ES2505471T3 - Power generation device - Google Patents

Abstract

A power generating device (1) comprising gears (3) speed multipliers that include a main shaft (2) capable of rotating driven by an external force; a rotation transmission mechanism (30) capable of receiving the rotation of the main shaft (2) to increase the speed of rotation of the main shaft (2), and a roller bearing (38, 39) capable of rotationally supporting an output shaft (35) capable of generating an operating torque of the rotation transmission mechanism (30); a generator (4) that includes a drive shaft (41) capable of being rotated when it receives the rotation of the output shaft (35) and configured to generate electricity in connection with the rotation of a rotating rotor along with the shaft (41 ) drive; an input rotor (5) disposed on the output shaft (35) to be able to rotate together with the output shaft (35); an output rotor (6) arranged on the drive shaft (41) to be able to rotate together with the drive shaft (41) and concentrically arranged on a radial interior or on a radial exterior of the input rotor (5); a unidirectional clutch (7) disposed between the input rotor (5) and the output rotor (6), the unidirectional clutch (7) being configured to connect the input rotor (5) with the output rotor (6) for rotate together with the input rotor (5) and the output rotor (6) when a rotation speed of the input rotor (5) exceeds the rotation speed of the output rotor (6), and the clutch (7 being configured) ) unidirectional to release a connection between the input rotor (5) and the output rotor (6) when the rotation speed of the input rotor (5) falls below the rotational speed of the output rotor (6); and a pair of roller bearings (8) disposed between the input rotor (5) and the output rotor (6) and configured to support the input rotor (5) and the output rotor (6) so that the rotor (5) input and output rotor (6) rotate in relation to each other; wherein the unidirectional clutch (7) includes an outer peripheral surface (71a) of an inner ring (71), an inner peripheral surface (72a) of an outer ring (72), and a roller (73) disposed on each of the various wedge-shaped spaces (S) formed between the outer peripheral surface (71a) of the inner ring (71) and the inner peripheral surface (72a) of the outer ring (72), in which the unidirectional clutch (7) It is configured to connect the input rotor (5) with the output rotor (6) to rotate together with the input rotor (5) and the output rotor (6) by engaging the roller (73) with the surface ( 71a) outer peripheral of the inner ring (71) and the inner peripheral surface (72a) of the outer ring (72), in which the unidirectional clutch (7) is configured to release the connection between the input rotor (5) and the output rotor (6) to release the roller gear (73) with the peripheral surface (71a) outer ca of the inner ring (71) and the inner peripheral surface (72a) of the outer ring (72), in which the unidirectional clutch (7) includes an annular cage configured to contain the various rollers at a certain distance along the circumferential direction, characterized in that the pairs of roller bearings (8) are arranged on the respective axial sides of the unidirectional clutch (7) so that each of the pairs of roller bearings (8) is disposed adjacent to the clutch ( 7) unidirectional and an axial end (81b1) of each of the pairs of roller bearings (8) is able to be in contact with a corresponding face of the axial end faces of an annular clutch cage (74) (7) unidirectional, and because the roller bearing pairs (8) are a pair of cylindrical roller bearings (8), each of which includes several cylindrical rollers (83) and a portion (81b) with which terminal faces of the plurality of cylindrical rollers (83) in axial direction can be placed in sliding contact, and the axial end faces of the annular cage (74) of the unidirectional clutch (7) can be placed in contact with the portion (81b) of the pair of cylindrical roller bearings (8).

Description

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DESCRIPTION

Power generation device

Background of the invention

1. Field of the invention

The present invention relates to a power generation device in which the speed of rotation of a main shaft is increased by an external force by gears multiplying the speed to drive the generator.

2. Description of the related technique

The speed multiplier gears are used in a wind power generating device so that the force of the wind is received by blades to rotate the main axis that is connected to the blades and increase the speed of rotation of the axis main to drive the generator. As shown in FIG. 16, the speed multiplier gears 202 include a planetary gear mechanism 203 that receives the rotation of a main shaft 200 to increase the speed. A high speed gear mechanism 204 that receives the rotation at which the speed is increased by the planetary gear mechanism 203 and also increases the rotation speed, and an output shaft 205 that generates an operating torque of the mechanism 204 of high speed gears.

The planetary gear mechanism 203 is constructed such that, when an input shaft 203a coupled to the main shaft 200 rotates to be able to rotate together, a planetary support 203b also rotates and, therefore, a solar gear 203d rotates at increased speed by means of of a planetary gear 203c, and the rotation is transmitted to a low speed shaft 204a of the high speed gear mechanism 204. The high speed gear mechanism 204 is constructed to rotate an intermediate shaft 204d at an increased speed by means of the low speed gear 204b and a first intermediate gear 204c when the low speed shaft 204a rotates and also rotates the shaft 205 output at increased speed by means of a second intermediate gear 204e and a high speed gear 204f. As respective bearings for rotating support of the low speed shaft 204a, intermediate shaft 204d and output shaft 205 of speed multiplier gears 202, roller bearings 206 to 211 are frequently used (see, for example, the Japanese Patent Application Publication No. 2007-232186 (JP 2007-232186 A)).

Likewise, a wind power generation device is known that receives a force from the wind on blades to rotate the main shaft that is connected to the blades and increases the speed of rotation of the main shaft to drive the generator. Speed multiplier gears to increase the rotation of the main shaft include, as shown in FIG. 16, for example, a planetary gear mechanism 203 that increases the rotational speed received from a main shaft 200, a high speed gear mechanism 204 that further increases the rotational speed received from the planetary gear mechanism 203, and an output shaft 205 that generates an operating torque of the high speed gear mechanism 204. The output shaft 205 is coupled to a drive shaft of the generator (not shown) in order to transmit the transmission energy.

The planetary gear mechanism 203 is constructed such that, when the rotation of the main shaft 200 is transmitted to the input shaft 203a the planetary support 203b rotates and, therefore, rotates the solar gear 203d at the increased speed by means of the gear 203c planetary, and the rotation is transmitted to the low speed shaft 204a of the high speed gear mechanism 204. Likewise, the high speed gear mechanism 204 is constructed to rotate the intermediate gear 204d at an increased speed by means of the low speed gear 204b and the first intermediate gear 204c when the rotation is transmitted from the planetary gear mechanism 203 to the low speed shaft 204a and also rotate the output shaft 205 at increased speed by means of the second intermediate gear 204e and the high speed gear 204f.

As respective bearings for rotating rotation of the low speed shaft 204a, intermediate shaft 204d and output shaft 205 of speed multiplier gears 202, roller bearings 206 to 211 are frequently used (see, for example, the JP 2007-232186A). Likewise, in the prior art a power generation device is known which comprises all the features of the characterizing part of claim 1 (see, for example, German Patent Application Publication No. 10 2009 004991 (DE 10 2009 004991 A1)).

Summary of the invention

In the wind power generation device, "smearing" adhesions (a phenomenon in which the seizing of the surface layer) is generated on the rolling contact surface of a roller or a rolling surface of a Rotating wheel on the roller bearing that supports the output shaft that rotates at high speed and therefore the life of the roller bearing can be reduced. The objective of the present invention

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it consists in providing a power generating device that can prevent the retention in the roller bearing that supports the output shaft of the speed accelerating gears.

The inventor of the present application has studied with great attention the mechanism of retention generation. As a result, the inventor has discovered that when the speed of rotation of the main shaft rapidly decreases by decreasing the force of the wind, the speed of rotation of the generator drive shaft exceeds the speed of rotation of the output shaft by the inertia of the generator rotor that has a considerable weight and, therefore, the so-called loss of torque (loss of load) occurs, the radial load that is applied to the roller bearing that supports the output shaft is reduced because of the loss of the torque, the drag friction drag between the roller and the cage containing the roller exceeds exceeds the drag friction drag between the roller of the roller bearing and the rotating wheel and, thus, delays the roller rotation The inventor has also discovered that, when the speed of rotation of the main axis increases rapidly by increasing the intensity of the wind from the state described above, the inertia torque derived from the increased rotation speed is added to increase the radial load that is applied to the roller bearing that supports the output shaft and, therefore, the roller slides on the contact surface with the rotating wheel in a state in which a high load is applied to the roller at the time in which the temperature of the contact surface rises and, in this way, the retention is generated. The inventor put into practice the invention of the present application based on these findings.

Aspects of the present invention relate to a power generation device. The power generating device includes: speed multiplier gears that include a main shaft that rotates by an external force, a rotation transmission mechanism that receives the rotation of the main shaft to increase the speed of rotation of the main shaft, and a roller bearing that rotatably supports an output shaft that generates an operating torque of the rotation transmission mechanism; a generator that includes a drive shaft that is rotated by receiving the rotation of the output shaft and that is configured to generate electricity in connection with the rotation of a rotating rotor along with the drive shaft; an input rotor arranged on the output shaft to be able to rotate together with the output shaft; an output rotor arranged on the drive shaft to be able to rotate together with the drive shaft and which is concentrically arranged on a radial interior or on a radial exterior of the input rotor; and a unidirectional clutch disposed between the input rotor and the output rotor, the unidirectional clutch being configured to connect the input rotor with the output rotor to rotate together with the input rotor and the output rotor when a rotation speed of the input rotor exceeds a rotation speed of the output rotor, and a unidirectional clutch configured to release a connection between the input rotor and the output rotor when the rotation speed of the input rotor falls below the rotation speed of the output rotor.

According to the power generation device constructed as set forth, the unidirectional clutch can connect the input rotor to the output rotor to rotate together when the rotation speed of the input rotor exceeds the rotation speed of the output rotor and releases the connection between the input rotor and the output rotor when the rotation speed of the input rotor falls below the rotation speed of the output rotor. That is, even when the rotation speed of the output shaft rapidly falls when a decrease in external force occurs through the main shaft, it is possible to prevent the rotation of the generator rotor by inertia from being transmitted to the output shaft through the drive shaft Therefore, the reduction of the radial load that is applied to the roller bearing that supports the output shaft and the delay of the rotation of the roller in association with the reduction of the radial load can be prevented. Therefore, when the speed of rotation of the main shaft rapidly increases due to the change in the external force derived from the state described in the previous lines, and a high load is applied on the roller, the roller hardly slides on the surface of contact with the rotating wheel and, therefore, the generation of adhesions on the roller bearing can be effectively prevented.

The power generating device may include a roller bearing disposed between the input rotor and the output rotor and be configured to support the input rotor and the output rotor so that the input rotor and the output rotor rotate between yes. The unidirectional clutch can include an outer peripheral surface of an inner ring, an inner peripheral surface of an outer ring, and a roller disposed in each of the wedge-shaped spaces formed between the outer peripheral surface of the inner ring and the peripheral surface internal of the outer ring. The unidirectional clutch can be configured to connect the input rotor with the output rotor to rotate together with the input rotor and with the output rotor by engaging the roller with the outer peripheral surface of the inner ring and with the inner peripheral surface of the outer ring, and the unidirectional clutch can be configured to release the connection between the input rotor and the output rotor by releasing the roller gear with the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring. In this case, due to the existence of a separation between the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring when the unidirectional clutch roller gear release occurs with the outer peripheral surface of the inner ring and the surface internal peripheral of the outer ring, the relative relative displacement of the input rotor and the output rotor in the radial direction by the rolling bearing can be prevented. Therefore, the knocking of the input rotor and the output rotor in the radial direction during the operation of the power generating device can be prevented.

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The unidirectional clutch may include an annular cage configured to contain the different rollers with the separation determined along a circumferential direction, a pair of roller bearings may be disposed between the input rotor and the output rotor, and the pairs of rolling bearings may be arranged on the respective axial sides of the unidirectional clutch so that each of the pairs of rolling bearings is positioned adjacent to the unidirectional clutch and an axial end of each of the pairs of roller bearings can be positioned in contact with a corresponding face of the axial end faces of the unidirectional clutch annular cage. In this case, the axial end faces of the unidirectional clutch cage are in contact with the axial ends of a pair of the bearing bearings and, therefore, the displacement of the cage towards the axial sides can be restricted.

The pairs of rolling bearings can be a pair of cylindrical roller bearings that include several cylindrical rollers and a portion with which the end faces of the various cylindrical rollers in the axial direction are placed in sliding contact, and the axial end faces of the Ring cage can be placed in contact with the portion of the pair of cylindrical roller bearings. In this case, the inner annular rib of the rolling bearing can be used as a member that restricts the axial displacement of the cage, and, therefore, the structure of the roller bearing can be simplified.

The inner peripheral surface of the outer ring of the unidirectional clutch can be a cylindrical surface, the cylindrical roller bearing can include a bearing surface of an outer ring of the cylindrical roller bearing in which the cylindrical roller bearing rolls, the output rotor it can be arranged on a radial outside of the input rotor, and the inner peripheral surface of the outer ring of the unidirectional clutch and the bearing surface can be formed on an inner peripheral surface of the output rotor. In this case, the output rotor can be used as an outer ring that has the inner peripheral surface of the outer ring of the unidirectional clutch and the outer ring that has the rolling surface of the outer ring of the respective cylindrical roller bearing and, therefore, the structure of the entire wind device can be simplified.

The output rotor can be removably attached to the drive shaft and be arranged so that it can move in the axial direction with respect to the input rotor. In this case, the output rotor can be removed from the input rotor when the output rotor is removed from the drive shaft and moved in the axial direction with respect to the input rotor. Therefore, the outer ring of the unidirectional clutch and the outer ring of the cylindrical roller bearing can be removed at the same time and, therefore, the maintenance tasks of the unidirectional clutch and the cylindrical roller bearing can be easily carried out. In this case, there is no need to move the generator and, therefore, maintenance tasks can be easily carried out.

According to the power generating device of the present invention, adhesions can be effectively prevented from generating adhesions in the roller bearing that supports the output shaft of the speed multiplier gears.

In the power generating device, when the generator is burned it becomes difficult for the drive shaft to rotate, the transmission torque from the output shaft to the drive shaft becomes excessively high, and the speed multiplier gears receive a overload and, therefore, there is a possibility that speed multiplier gears will be damaged.

The present invention provides an energy generating device that can effectively prevent adhesions in the roller bearing that supports the output shaft of the speed multiplier gears and reduces the load applied to the speed multiplier gears in the case. that the transmission torque from the output shaft to the generator drive shaft is excessively high.

In the power generation device described in the preceding lines, the unidirectional clutch may be provided with a torque limiter configured to release the connection between the input rotor and the output rotor when the transmission torque from the input rotor to The output rotor exceeds an upper limit.

According to the power generation device, which is constructed as described in the previous lines, the unidirectional clutch can connect the input rotor with the output rotor to be able to rotate together when the rotation speed of the input rotor exceeds the Rotation speed of the output rotor and release the connection between the input rotor and the output rotor when the rotation speed of the input rotor falls below the rotation speed of the output rotor. That is, even when the rotation speed of the output shaft quickly falls when a decrease in the external force occurs through the main shaft, it is possible to prevent the rotation of the generator rotor by inertia from being transmitted to the output shaft through the drive shaft Accordingly, the reduction of the radial load applied to the roller bearing that supports the output shaft and the rotation delay of the roller in association with the reduction of the radial load can be prevented. Therefore, when the speed of rotation of the main shaft rapidly increases due to the change of the external force due to the state described above, and a high load is applied on the roller, the roller hardly slides on the surface of contact with the rotating wheel and, therefore, the generation of adhesions on the roller bearing can be effectively prevented.

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Likewise, the unidirectional clutch is provided with a torque limiter and, therefore, when the drive shaft is difficult to rotate because the generator has burned, the transmission torque from the input rotor arranged on the shaft side of output to the output rotor arranged on the drive shaft side exceeds the upper limit (the input rotor is connected to the output rotor to remain in a locked state), the torque limiter can release the connection between the input rotor and The output rotor. Consequently, the load applied to the speed multiplier gears can be reduced, and the speed multiplier gears can be prevented from being damaged. Also, because the unidirectional clutch is provided with the torque limiter, a simplification and a reduction in the size of the structure can be carried out in comparison with an assumption in which the unidirectional clutch and the torque limiter are arranged by separated.

The unidirectional clutch may include an inner peripheral surface of an outer ring disposed on a rotor between an input rotor and the output rotor, an outer peripheral surface of an internal ring disposed on another rotor between the input rotor and the output rotor and configured to form several wedge-shaped spaces in circumferential direction with the inner peripheral surface of the outer ring, and a roller disposed in each of the various wedge-shaped spaces; The unidirectional clutch can be configured to connect the input rotor with the output rotor to rotate together with the input rotor and the output rotor by engaging the roller with the outer peripheral surface of the inner ring and the outer peripheral surface of the ring external, the unidirectional clutch can be configured to release the connection between the input rotor and the output rotor, releasing the roller engagement with the outer peripheral surface of the inner ring and the outer peripheral surface of the outer ring; the torque limiter may be provided with a housing recess that is formed on the outer peripheral surface of the inner ring and that houses the roller separated from the wedge-shaped space, when the transmission torque exceeds the upper limit, to release the gear of the roller with the outer peripheral surface of the inner ring and with the inner peripheral surface of the outer ring.

According to the exposed structure, when the transmission torque from the input rotor to the output rotor exceeds an upper limit, the roller that is separated from the wedge-shaped space is housed in the housing recess, and released the engagement of the roller with the outer peripheral surface of the inner ring and with the inner peripheral surface of the outer ring. Therefore, the connection from the input rotor to the output rotor can be properly released.

The outer peripheral surface of the inner ring may be arranged in the inlet rotor, and the torque limiter may be provided with a means of separation prevention that prevents the roller arranged in the housing recess from being separated from the housing recess by the centrifugal force due to the rotation of the input rotor. When the inlet rotor rotates in a state in which the roller is housed in the housing recess, and the roller exits the housing recess by centrifugal force, there is a possibility that the gearing of the roller will occur again with the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring. However, the torque limiter of the present invention includes a means of preventing separation that prevents the roller from separating from the housing recess and, therefore, such problems can be solved.

The separation prevention means may be constructed such that a restriction section that restricts the movement of the roller housed in the housing recess over the radial exterior protrudes along an edge of the accommodation recess in the circumferential direction. According to said structure, if the roller is separated from the housing recess to the radial exterior by a centrifugal force due to the rotation of the input rotor, the control section becomes an obstacle that prevents separation. Therefore, the engagement of the roller with the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring can be properly prevented again.

A receptacle configured to accommodate the roller may be disposed between the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring. A cage configured to maintain the rollers with a determined clearance along the circumferential direction and an elastic member configured to press the roller disposed within the receptacle towards a wedge-shaped space narrowing direction, may be disposed between the peripheral surface outer of the inner ring and the inner peripheral surface of the outer ring; and the housing recess may be formed so that it has a depth so that the roller is located in a radial interior with respect to the elastic member. According to the exposed structure, when the roller separates from the cage receptacle to enter the housing recess, the elastic member extends to be located on the radial outside of the roller. Therefore, if the roller is separated from the housing recess to the radial outside by the centrifugal force in association with the rotation of the inlet rotor, the elastic member becomes an obstacle and separation can be prevented.

The elastic member may be provided with a locking member that blocks at least a portion of the housing recess that houses the roller. According to the exposed structure, when the elastic member is disposed on the radial outside of the roller entering the housing recess as described above, the blocking member can block at least a part of the housing recess and prevent Firmly separating the roller.

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In accordance with the power generating device of the present invention, adhesions can be effectively prevented in the roller bearing that supports the output shaft of the speed multiplier gears, and the load applied to the gears can be reduced. speed multiplier gears in case the transmission torque from the output shaft to the generator drive shaft is excessively high. Also, in accordance with the unidirectional clutch of the present invention, when the transmission torque from the input shaft to the generator output shaft becomes excessively high, the connection between the input rotor and the output rotor can, of preferably, it can be released and, likewise, the separation of the housing recess roller can be prevented by centrifugal force due to the rotation of the input rotor and the engagement of the roller with the outer peripheral surface of the inner ring and the peripheral surface internal of the outer ring.

In the wind power generation device, adhesions are generated (a phenomenon in which the seizing of the surface layer is generated) on the rolling contact surface of a roller or a rolling surface of a rotating wheel in the bearing of rollers that support the output shaft that rotates at high speed and, therefore, the life of the roller bearing can be reduced. The present invention provides a power generating device that can effectively prevent adhesions from being generated in the roller bearing that supports the output shaft of the speed multiplier gears.

The power generating device may include a mass of inertia arranged to be able to rotate together with the output rotor.

According to the power generation device that is constructed as described above, the unidirectional clutch can connect the input rotor with the output rotor to be able to rotate together when the rotation speed of the input rotor exceeds the speed of rotation of the output rotor and release the connection between the input rotor and the output rotor when the rotation speed of the input rotor falls below the rotation speed of the output rotor. That is, even when the rotation speed of the output shaft quickly falls below a decrease in external force through the main shaft, it is possible to prevent the rotation of the generator rotor by inertia from being transmitted to the output shaft through of the drive shaft. Accordingly, the reduction of the radial load applied to the roller bearing that supports the output shaft and the delay of the rotation of the roller in association with the reduction of the radial load can be prevented. Therefore, when the speed of rotation of the main shaft rapidly increases due to the change of the external force from the state described above, and a high load is applied on the roller, the roller hardly slides on the surface of contact with the rotating wheel and, therefore, can effectively prevent adhesions from being generated on the roller bearing.

Likewise, the output rotor is provided with the mass of inertia to be able to rotate together, and therefore, the moment of inertia of the output rotor can be increased. Consequently, the unidirectional clutch releases the connection between the input rotor and the output rotor and, when the output rotor rotates at a reduced speed due to the inertia of the rotor, angular acceleration due to deceleration is poor. Therefore, the rotation speed of the output rotor can be prevented from being rapidly reduced. That is, even when the speed of rotation of the main shaft rapidly falls below a decrease in external force, the generator rotor does not rapidly reduce the rotation speed in association with the output rotor, but instead continues to rotate by inertia and therefore, the average rotation speed of the rotor can be increased. Therefore, the efficiency of generator power generation can be improved.

The power generating device may include a roller bearing disposed between the input rotor and the output rotor and be configured to support the input rotor and the output rotor so that the input rotor and the output rotor rotate between yes. The unidirectional clutch can include, an outer peripheral surface of an inner ring, an inner peripheral surface of an outer ring and a roller disposed in each of the various wedge-shaped spaces formed between the outer peripheral surface of the inner ring and the surface internal peripheral of the outer ring. The unidirectional clutch can be configured to connect the input rotor with the output rotor to rotate together with the input rotor and the output rotor by engaging the roller with the outer peripheral surface of the inner ring and the inner peripheral surface of the ring external. The unidirectional clutch can be configured to release the connection between the input rotor and the output rotor by releasing the roller gear with the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring. In this case, due to the existence of a separation between the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring, when the unidirectional clutch roller gear is released with the outer peripheral surface of the inner ring and the peripheral surface internal of the outer ring, the relative relative displacement of the input rotor and the output rotor in the radial direction can be prevented by the roller bearing. Therefore, the knocking of the input rotor and the output rotor in the radial direction during the operation of the power generating device can be prevented.

The unidirectional clutch may include an annular cage configured to maintain the various rollers at the determined clearance along a circumferential direction, and a pair of roller bearings may be disposed between the input rotor and the output rotor. The pair of roller bearings may be arranged on the respective axial sides of the unidirectional clutch so that the pair of roller bearings is disposed adjacent to the unidirectional clutch and an axial end of each bearing of the pair of roller bearings

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can be placed in contact with a corresponding face of the axial end faces of the unidirectional clutch ring cage. In this case, the axial end faces of the unidirectional clutch cage are in contact with the axial ends of a pair of roller bearings and, therefore, the displacement of the cage towards the axial sides can be restricted.

The pair of roller bearings may be a pair of cylindrical roller bearings that include several cylindrical rollers and a portion with which the end faces of the various cylindrical rollers in the axial direction are placed in sliding contact, and the axial end faces of the annular cage, can be placed in contact with the portion of the pair of cylindrical roller bearings. In this case, the rib of the inner ring of the roller bearing can be used as a member that restricts the axial displacement of the cage and, therefore, the structure of the roller bearing can be simplified.

The inner peripheral surface of the outer ring of the unidirectional clutch can be a cylindrical surface, the cylindrical ring bearing can include a bearing surface of an outer ring of the cylindrical roller bearing where the cylindrical roller bearing rolls, the output rotor can be disposed on a radial exterior of the input rotor and the inner peripheral surface of the outer ring of the unidirectional clutch and the bearing surface may be formed on an inner peripheral surface of the output rotor. In this case, the output rotor can be used as an outer ring that has the inner peripheral surface of the outer ring of the unidirectional clutch and the outer ring that has the rolling surface of the outer ring of the respective cylindrical roller bearing and, therefore, the structure of the entire wind device can be simplified.

The output rotor may be removably attached to the drive shaft and be arranged to be able to move in an axial direction with respect to the input rotor. In this case, the output rotor can be removed from the drive shaft and moved in an axial direction with respect to the input rotor. Therefore, the outer ring of the unidirectional clutch and the outer ring of the cylindrical roller bearing can be removed at the same time and, therefore, the maintenance tasks of the unidirectional clutch and the cylindrical roller bearing can be easily carried out. In this case, it is not necessary to move the generator and therefore maintenance tasks can be carried out more easily.

The power generating device may include: an electromagnetic clutch configured to connect the output rotor with the mass of inertia so that the output rotor and the mass of inertia rotate together during energization and to release the connection between the output rotor and the mass of inertia when energization does not occur; a detection means configured to detect the rotation speed of the output rotor; and a control means configured to control the arrangement of the magnetic clutch in a state without energization at the beginning of the rotation of the output rotor and to control the energization of the magnetic clutch when the detection means detects that the output rotor reaches a speed of rotation determined after the start of the rotation of the output rotor. In this case, the electromagnetic clutch is not energized and the connection between the output rotor and the mass of inertia is released until the output rotor reaches the speed of rotation determined at the beginning of the rotation and, therefore, can be reduced the operating torque to rotate the output rotor at the determined rotation speed. Accordingly, the time required to rotate the rotor at the determined rotation speed through the output rotor and the drive shaft can be reduced and, therefore, the efficiency of generator power generation can be further improved. . When the detection means detects that the output rotor reaches the determined rotation speed after the start of the rotation of the output rotor, the electromagnetic clutch is energized, and the output rotor and the mass of inertia are connected to be able to rotate together and, therefore, the moment of inertia of the output rotor can be increased. Therefore, when the unidirectional clutch releases the connection between the input rotor and the output rotor, the generator rotor does not rapidly reduce the rotational speed in association with the output rotor, but instead continues to rotate by inertia and therefore , the average rotation speed of the rotor can be increased. Therefore, the generator power generation efficiency can be further improved.

The power generating device may include a viscous fluid coupling arranged between the output rotor and the mass of inertia. The viscous fluid coupling may include: i) a viscous fluid that transmits an operating torque of the output rotor over the mass of inertia by viscous drag during low speed rotation of the output rotor, and ii) a clutch mechanism centrifuge that transmits the operating torque of the output rotor over the mass of inertia through the use of centrifugal force in association with the high-speed rotation of the output rotor during high-speed rotation of the output rotor. In this case, when the output rotor rotates at low speed at the beginning of the rotation, the operating torque of the output rotor is transmitted to the mass of inertia by the viscous drag of the viscous fluid and, therefore, the mass of inertia increases the speed with an angular acceleration less than the angular acceleration of the output rotor. In other words, the inertia torque by the mass of inertia applied to the output rotor at the start of the rotation of the output rotor can be reduced and, therefore, the operating torque required to increase the speed can be reduced. Rotation of the output rotor at the determined rotation speed. Therefore, the time required to increase the rotation speed of the rotor can be reduced to the rotation speed determined through the output rotor and the drive shaft and, therefore, the efficiency of generator power generation can result improved Likewise, when the output rotor reaches the rotation speed determined at high speed, the operating torque of the output rotor is transmitted to the ground.

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of inertia through the centrifugal clutch mechanism. Therefore, the output rotor and the mass of inertia are connected to be able to rotate together and, therefore, the moment of inertia of the output rotor can be increased. Therefore, when the unidirectional clutch releases the connection between the input rotor and the output rotor, the generator rotor does not rapidly decrease the rotational speed in association with the output rotor, but instead continues to rotate by inertia and therefore , the average rotation speed of the rotor can be increased, and the efficiency of generator power generation can be further improved.

In accordance with the power generating device of the present invention, the adhesion in the roller bearing that supports the output of the speed multiplier gears can be effectively prevented.

Brief description of the drawings

The features, advantages, and technical and industrial significance of the invention will be described in the subsequent detailed description of exemplary embodiments of the invention with reference to the accompanying drawings, in which the same numbers indicate the same elements, and in which:

FIG. 1 is a schematic side view showing a power generating device according to first and second embodiments of the present invention;

FIG. 2 is a cross-sectional view showing a roller bearing of gears multiplying the speed of the power generating device shown in FIG. one;

FIG. 3 is a cross-sectional view showing a connection part between an output shaft of the speed multiplier gears and the drive shaft of a generator of the power generation device according to the first embodiment and shown in FIG. one;

FIG. 4 is a cross-sectional view showing a unidirectional clutch of the power generation device according to the first and third embodiments;

FIG. 5 is a cross-sectional view showing a connection part between an output shaft of the speed multiplier gears and a drive shaft of a generator of the power generator device according to the second embodiment and shown in FIG. one;

FIG. 6 is a cross-sectional view showing a unidirectional clutch of the power generating device according to the second embodiment and shown in FIG. one;

FIG. 7 is a cross-sectional vita showing a part of the unidirectional clutch on an enlarged scale according to the second embodiment;

FIG. 8 is a cross-sectional view showing on a scale of enlarged size a part of the unidirectional clutch according to the second embodiment in a state in which a roller is housed in a housing recess;

FIG. 9 is a schematic side view showing a power generation device according to the third embodiment of the present invention;

FIG. 10 is a cross-sectional view showing a connection part between an output shaft of the speed multiplier gears and a drive shaft of a generator of the power generation device according to the third embodiment and shown in FIG. 9;

FIG. 11 is a graph showing a rotational fluctuation of an output rotor of the power generation device according to the third embodiment;

FIG. 12 is a graph showing rotational fluctuations of the output shaft shown in FIG. 10 and a generator rotor;

FIG. 13 is a cross-sectional view showing a connection part between an output shaft of the speed multiplier gears and a drive shaft of a generator of a wind power generation device according to a fourth embodiment of the present invention;

FIG. 14 is a cross-sectional view showing a connection part between an output shaft of the speed multiplier gears and a drive shaft of a generator of a wind power generation device according to a fifth embodiment of the present invention;

FIG. 15 is a graph showing rotational fluctuations of an output rotor and of a mass of inertia of the wind power generating device of FIG. 14; Y

FIG. 16 is a cross-sectional view showing the speed multiplier gears.

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Detailed description of embodiments

In the following, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a schematic side view showing a power generation device according to first and second embodiments of the present invention. The power generation device of the present embodiment is a wind power generation device 1. The wind power generation device 1 includes a main shaft 2 that rotates when it receives wind force (external force), gears 3 speed multipliers that are coupled to the main axis 2, and a generator 4 that is coupled to the gears 3 speed multipliers. The rotation speed of the main axis 2 is increased by the gears 3 speed multipliers, and the generator 4 is driven by the rotational power with increasing speed.

On the terminal tip of the main axis 2, blades (not shown), for example, are coupled to be able to rotate together, and the blades are constructed to receive the force of the wind to rotate together with the main axis 2. The generator 4 incorporates a drive shaft 41 that receives the rotational power of increased speed by means of gears 3 multipliers of the speed to rotate, and a rotor 42 that is installed in the generator 4 and a stator (not shown). The rotor 42 is coupled to the drive shaft 41 to be able to rotate together, and the electricity is generated in connection with the rotation of the drive shaft 41 and the drive of the rotor 42.

The gears 3 speed multipliers include a gear mechanism 30 (rotation transmission mechanism) that receives the rotation of the main axis 2 to increase the speed of the rotation. The gear mechanism 30 includes a planetary gear mechanism 31 and a mechanism 32 that receives the rotation whose speed is increased by the planetary gear mechanism 31 and that further increases the speed of the rotation. The planetary gear mechanism 31 has an internal gear gear 31a (annular gear), several planetary gears 31b that are held by a planetary support (not shown) that is coupled to the main shaft 2 to be able to rotate together, and a solar gear 31c that gears with the planetary gears 31b. Therefore, when the planetary support rotates together with the main shaft 2, the solar gear 31c rotates by means of the planetary gears 31b and the rotation is transmitted to a low speed shaft 33 of the high speed gear mechanism 32.

The high speed gear mechanism 32 includes a low speed shaft 33 incorporating a low speed gear 33a, an intermediate gear 34 incorporating a first intermediate gear 34a and a second intermediate gear 34b, and an output shaft 35 incorporating a high speed 35a gear. The low speed shaft 33 is constituted by a large rotary shaft whose diameter is approximately 1 m and which is concentrically arranged with the main axis 2. Both ends of the low speed shaft 33 in the axial direction are supported by roller bearings 36a and 36b for rotation. The intermediate shaft 34 is disposed on the low speed shaft 33. Both ends of the intermediate shaft 34 in the axial direction are supported by roller bearings 37a and 37b for rotation. The first intermediate gear 34a disposed on the intermediate shaft 34 meshes with the low speed gear 33a, and the second intermediate gear 34b meshes with the high speed gear 35a. The output shaft 35 is disposed on the intermediate shaft 34 and is adapted to generate the operating torque. The sides of one end 35b and another end 35c (exit end) of the output shaft 35 in the axial direction are respectively supported by the roller bearings 38 and 39 for rotation.

According to the exposed structure, the rotation of the main shaft 2 is increased in three stages with a transmission ratio of the planetary gear mechanism 31, a transmission ratio between the low speed gear 33a and the first intermediate gear 34a, and a transmission ratio between the second intermediate gear 34b and the high speed gear 35a. The operating torque is generated from the output end 35c of the output shaft 35. Therefore, the rotation speed of the main axis 2 is increased in three stages by the gears 3 speed multipliers and is adapted to the drive of the generator 4.

FIG. 2 is a cross-sectional view showing the roller bearing 38 that supports one end 35b of the output shaft 35. In FIG. 2, the roller bearing 38 is constituted by a cylindrical roller bearing and includes an inner ring 38a that is coupled and fixed on the output shaft 35, an outer ring 38b that is fixed to a housing (not shown), several rollers 38c cylindrical which are located between the inner ring 38a and the outer ring 38b to be able to roll, and an annular cage 38d that maintains the respective cylindrical rollers 38c at a certain distance along the circumferential direction. The inner ring 38a, the outer ring 38b and the cylindrical roller 38c are made, for example, of bearing steel. The cage 38d is manufactured, for example, in a copper alloy.

The inner ring 38a has a rolling surface 38a1 of the inner ring that is formed in an axial center of the outer periphery. The outer ring 38b is concentrically arranged with the inner ring 38a and has a rolling surface 38b1 of the outer ring that is formed in an axial center of the inner periphery and a pair of external ribs 38b2 that are formed on the axial sides of the surface 38b1 rolling of the outer ring. The rolling surface 38b1 of the outer ring is arranged opposite the surface

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38a1 rolling of the inner ring. The outer ribs 38b2 of the outer ring are shaped so that they protrude at both ends of the inner periphery of the outer ring 38b in the axial direction to an inner side in the radial direction. An end face of the cylindrical roller 38c is placed in sliding contact with the ribs 38b2 of the outer ring.

The cylindrical roller 38c is located between the rolling surface 38a1 of the inner ring of the inner ring 38a and the rolling surface 38b1 of the outer ring of the outer ring 38b for rolling. The cage 38d has a pair of annular sections 38d1 that are located separately in the axial direction and several column sections 38d2 that are located at regular intervals along the circumferential direction of the annular sections 38d1 to connect both annular sections 38d1. Receptacles 38d3 are respectively formed between the pair of annular sections 38d1 and adjacent column sections 38d2, and the respective cylindrical rollers 38c are located within the receptacles 38d3.

As shown in FIG. 1, the wind power generating device 1 also includes an input rotor 5 which is arranged to be able to rotate together with the output shaft 35 of the speed multiplier gears 3, and an output rotor 6 that is arranged to be able to rotate together with the drive shaft 41 of the generator 4, a unidirectional clutch 7 that is disposed between the input rotor 5 and the output rotor 6, and a pair of roller bearings 8 which are arranged on the axial sides of the clutch 7 unidirectional The unidirectional clutch 7 and the roller bearings 8 are constructed to transmit the rotation of the output shaft 35 to the drive shaft 41 by means of the input rotor 5 and the output rotor 6. At this point, the wind power generating device 1 of the present embodiment is constructed such that the roller bearings 8 are arranged on the axial sides of the unidirectional clutch 7, however, a roller bearing 8 may be arranged only on one axial side of the unidirectional clutch 7.

First, the first embodiment will be described. FIG. 3 is a cross-sectional view showing a connection part between the output shaft 35 of the gears 3 speed multipliers and the drive shaft 41 of the generator 4. In FIG. 3, the inlet rotor 5 is concentrically arranged with the output shaft 35 and has a flange section 51, a large diameter section 52, and a small diameter section 53, in this order, from an axial end (left end of FIG. 3) to another axial end (right end of FIG. 3). The flange section 51 is shaped to extend to a radial exterior beyond the outer peripheral surface of the large diameter section 52 and is removably fixed at the outlet end 35c of the output shaft 35. Specifically, the flange section 51 is fastened on a flange section 35c1 that is formed at the outlet end 35c in a stop arrangement against the flange section 35c1 with a bolt and a nut (not shown). A gap S1 is formed between the terminal face of the small diameter section 53 and the terminal face of a flange section 41a of the drive shaft 41.

The output rotor 6 is concentrically arranged on a radial exterior of the input rotor 5 and has a cylindrical section 61 and a flange section 62 that is formed at another axial end (right end of FIG. 3) of the cylindrical section 61 . The flange section 62 is shaped so that it extends to a radial exterior beyond the outer peripheral surface of the cylindrical section 61 and is removably fixed within one end of the drive shaft 41. Specifically, the flange section 62 is fastened on a flange section 41a that is formed at one end of the drive shaft 41 in a stop arrangement against the flange section 41a with a bolt and a nut (not shown).

An inner peripheral surface of the cylindrical section 61 is formed in a cylindrical surface. An annular sealing member 10 for sealing an annular space between the cylindrical section 61 and the small diameter section 53 of the inlet rotor 5 is disposed in the space between the inner peripheral surface of the cylindrical section 61 and one end axial (left end of FIG. 3) and the outer peripheral surface of the large diameter section 52 of the inlet rotor 5. A gap S2 is disposed between the terminal face of the cylindrical section 61 on a terminal side and a terminal face of the flange section 51 of the inlet rotor 5 facing the end face of the cylindrical section 61. Accordingly, the output rotor 6 can move to both axial sides with respect to the input rotor 5 in a state in which the output rotor 6 is separated from the drive shaft 41.

FIG. 4 is a cross-sectional view showing the unidirectional clutch 7. In FIG. 3 and in FIG. 4, the unidirectional clutch 7 includes an inner ring 71, an outer ring 72 and several rollers 73 that are disposed between an outer peripheral surface 71a of the inner ring 71 and an inner peripheral surface 72a of the outer ring 72. The inner ring 71 is coupled and fixed on the axial center of the small diameter section 53 of the inlet rotor 5 and constituted to rotate together with the small diameter section 53. A zone B disposed at the axial center of the cylindrical section 61 of the output rotor 6 is arranged as an outer ring 72 of the unidirectional clutch 7. Thus, the inner peripheral surface 72a is formed on an inner peripheral surface of the cylindrical section 61 in the zone B. The rollers 73 are formed adopting a cylindrical profile, and eight rollers are arranged in the circumferential section of the present embodiment .

The unidirectional clutch 7 also includes an annular cage 74 that contains the respective rollers 73 at regular intervals along the circumferential section and several elastic members 75 that elastically press the respective rollers 73 in one direction. The cage 74 has a pair of annular sections 74a

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facing each other arranged in axial direction and several column sections 74b extending between both annular directions 74a in the axial direction and which are arranged at regular intervals in the circumferential direction to connect both annular sections 74a. Several receptacles 74c are formed between both annular sections 74a and adjacent column sections 74b, and the respective rollers 73 are housed separately within the receptacles 74c. The elastic members 75 are formed with a helical compression spring and are housed separately within the respective receptacles 74c of the cage 74 to be installed in the column sections 74b.

In FIG. 4, flat cam surfaces 71a1 in the same number as the rollers 73 (eight) are formed on the outer peripheral surface 71a of the inner ring 71. The inner peripheral surface 72a of the outer ring 72 is shaped by adopting a cylindrical configuration. Several (eight) wedge-shaped spaces S are formed in the circumferential direction between the cam surfaces 71a1 of the ring and the inner ring 71 and the cylindrical surface of the outer ring 72. The rollers 73 are arranged at regular intervals within the respective wedge-shaped spaces S, and the elastic members 75 press the rollers 73 in the direction in which the wedge-shaped spaces S narrow. The outer peripheral surface of a roller 73 is shaped as a contact surface 73a that is in contact with a cam surface 71a1 of the inner ring 71 and a cylindrical surface of the outer ring 72, and the contact surface 73a is a straight surface in a width direction (axial direction). The unidirectional clutch 7 is located in an environment in which a grease lubricant made with ester-based oil and a urea-based thickener and practically not affected by temperature changes, is disposed between the inner ring 71 and the outer ring 72.

In the unidirectional clutch 7 which is constructed as described above, in the event that the input rotor 5 rotates with an increase in speed and, therefore, that the rotation speed of the input rotor 5 exceeds that of the output rotor 6, the inner ring 71 performs the relative rotation with the outer ring and 72 in one direction (the opposite direction to the clockwise hands of FIG. 4). In this case, the roller 73 moves slightly in the direction in which the wedge-shaped space S is narrowed by the pushing force of the elastic member 75, the contact surface 73a of the roller 73 is placed in contact with the surface 71a outer peripheral of the inner ring 71 and the inner peripheral surface 72a of the outer ring 72 (that is, the roller 73 is pressed towards the inner ring 71 and the outer ring 72), and the unidirectional clutch 7 is arranged in a state in which that the roller 73 fits between the inner ring 71 and the outer ring 72. Accordingly, the inner ring 71 and the outer ring 72 can rotate together in one direction and connect the input rotor 5 with the output rotor 6 to be able to rotate together.

In the event that the rotation speed of the input rotor 5 is constant after increasing and the same as that of the output rotor 6, the roller 73 remains engaged between the inner ring 71 and the outer ring 72. Therefore, the unidirectional clutch 7 maintains the corrotation of the inner ring 71 and the outer ring 72 in one direction, and the input rotor 5 and the output rotor 6 continue to rotate together.

On the other hand, in the event that the input rotor 5 rotates at a reduced speed and, therefore, the rotation speed of the input rotor 5 falls below that of the output rotor 6, the inner ring 71 leads to perform the relative rotation with respect to the outer ring 72 in another direction (clockwise direction of FIG. 4). In this case, the roller 73 moves slightly in the direction in which the wedge-shaped space S widens against the pushing force of the elastic member 75 and, therefore, the engagement of the roller 73 with the ring 71 is released. internal and outer ring 72. Therefore, the gear of the roller 73 is released and, therefore, the connection between the input rotor 5 and the output rotor 6 is released.

In FIG. 3, a pair of roller bearings 8 are respectively arranged between the small diameter section 53 of the input rotor 5 and the cylindrical section 61 of the output rotor 6 and support the input rotor 5 and the output rotor 6 for rotation mutual The roller bearings 8 are arranged on the axial sides of the unidirectional clutch 7 adjacent to each other so that the axial ends of the roller bearings 8 can be placed in contact with the axial end faces of the cage 74 of the unidirectional clutch 7 of the axial end.

The roller bearing 8 is provided with an inner ring 81, an outer ring 82 and a cylindrical roller bearing that includes several cylindrical rollers 83 that are located between the inner ring 81 and the outer ring 82 for rolling. The inner ring 81 has a rolling surface 81a of the inner ring that is formed on an inner periphery and a rib 81b of the inner ring that is formed on the axial sides of the inner race surface 81a so that they protrude through a radial exterior. Terminal faces of the cylindrical roller 83 are located respectively in sliding contact with an inner surface of the rib 81b of the inner ring. Likewise, the outer surface 81b1 of the rib 81b of the inner ring adjacent to the unidirectional clutch 7 is shaped as a contact surface that is in contact with an inner surface of the annular section 74a which is an axial terminal face of the cage 74 of unidirectional clutch 7.

The zones A and C of the axial end faces of the cylindrical section 61 of the exit rotor 6 are arranged as the outer ring 82 of the roller bearing 8. A rolling surface 82a of the outer ring of the outer ring 82 is formed on respective inner peripheral surfaces of zones A and C. The cylindrical roller 83 is located between the rolling surface 82a of the outer ring and the rolling surface 81a of the ring internal to be able to roll.

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According to the wind power generation device 1 described in the previous lines, the unidirectional clutch 7 is arranged between the input rotor 5 which rotates together with the output shaft 35 of the gears 3 speed multipliers and the rotor 6 output rotating together with the drive shaft 41 of the generator 4, can release the connection between the input rotor 5 and the output rotor 6 when the rotation speed of the input rotor 5 falls below that of the rotor 6 of exit. That is, when the rotation speed of the output shaft 35 quickly falls below a decrease in wind force through the main axis 2, it can be prevented that the rotation of the rotor 42 of the generator 4 by inertia is transmitted to the axis 35 output via drive shaft 41. Accordingly, the reduction of the radial load applied to the roller bearing 38 that supports the output shaft 35 and the delay of the rotation of the cylindrical roller 38c in association with the reduction of the radial load can be prevented. Therefore, when the speed of rotation of the main axis 2 rapidly increases due to the change of the force of the wind and a high load is applied on the cylindrical roller 38c starting from the aforementioned state, the cylindrical roller 38c hardly slides on the surface of contact with the load ring 38a and, therefore, the adhesions of the roller bearing 38 can be effectively prevented.

Likewise, by preventing the rotation of the rotor 42 of the generator 4 from being transmitted by inertia to the output shaft 35, the loads applied to the bearings 36a, 36b, 37a, 37b, 38, 39 of rollers and others of the rollers can be reduced gears 3 speed multipliers. Consequently, the reduction of the size of all gears 31b and 31c of the planetary gear mechanism 31, of the axes 33 to 35 of the high speed gear mechanism 32, and of the bearings 36a, 36b, 37a, 37b can be achieved , 38 and 39 of rollers and, therefore, the weight of gears 3 speed multipliers can be reduced with the consequent reduction in cost. Likewise, releasing the connection between the input rotor 5 and the output rotor 6, the rotor 42 of the generator 4 continues to rotate inertia without rapid slowdown and, therefore, the average rotational speed of the rotor can be increased

42. Consequently, the efficiency of generator 4 power generation can be improved.

Between the input rotor 5 and the output rotor 6, the roller bearing 8 which supports the rotors is arranged to be able to rotate each other. Thus, by releasing the gear of the roller 73, the inner ring 71 and the outer ring 72 of the unidirectional clutch 7, when the separation between the roller 73 and the inner and outer rings 71 and 72 occurs in the S-shaped separation of wedge, the roller bearing 8 can prevent the input rotor 5 and the output rotor 6 from moving mutually in the radial direction. Therefore, tapping in the radial direction can be prevented during the operation of the wind power generating device 1.

Because a pair of roller bearings 8 is disposed on the axial sides of the unidirectional clutch 7 adjacent to each other, since the axial end faces of the cage 74 of the unidirectional clutch 7 are formed to be able to contact the axial ends of the bearings 8 of rollers, the movement of the cage 74 towards the axial sides can be restricted. In particular, because the axial end face of the cage 74 of the unidirectional clutch 7 (outer surface of the annular section 74a is in contact with the rib 81b of the inner ring of the roller bearing 8, the rib 81b of the inner ring of the Roller bearing 8 can also be used as a member that restricts the axial displacement of the cage 74. Accordingly, the structure of the roller bearing 8 can be simplified.

Likewise, because the inner peripheral surface 72a of the outer ring of the unidirectional clutch 7 and the rolling surface 82a of the outer ring of the roller bearing 8 are formed in the inner peripheral surface of the output rotor 6, the output rotor 6 It can be used as the outer ring 72 of the unidirectional clutch 7 and the outer ring 82 of the roller bearing 8. Accordingly, the entire structure of the wind power generating device 1 can be simplified. Because the output rotor 6 is removably attached to the drive shaft 41 of the generator 4 and is removably arranged in the axial direction with respect to the input rotor 5, the output rotor 6 can be removed from the rotor 5 input when the output rotor 6 is removed from the drive shaft 41 and moved in the axial direction with respect to the input rotor 5. Accordingly, the outer ring 72 of the unidirectional clutch 7 and the outer ring 82 of the roller bearing 8 can be removed at the same time and, therefore, the maintenance tasks of the unidirectional clutch 7 and the bearing 8 can be easily carried out. of rollers. In this case, it is not necessary to move the generator 4 and, therefore, maintenance tasks can easily be carried out.

The present invention is not limited to the first embodiment described above and can be suitably modified when put into practice. For example, in the first embodiment, the input rotor and the output rotor are respectively arranged on the output shaft and on the drive shaft as separate members. However, the input rotor and the output rotor can be integrally formed with, respectively, the output shaft and the drive shaft. The output rotor is arranged on the radial outside of the input rotor; however, the output rotor may be arranged on the radial inside of the input rotor. In this case, the unidirectional clutch may be formed with the cam surface disposed on the inner peripheral surface of the outer ring and the inner peripheral surface of the inner ring may be shaped as a cylindrical surface. Likewise, in this case, the inner peripheral surface of the outer ring can be formed on the inner peripheral surface of the output rotor and the output rotor can be used as an internal ring.

Likewise, the output rotor is formed as an outer ring of the unidirectional clutch and an outer ring of the roller bearing; however, these outer rings may be arranged on the output rotor as

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separate members The roller bearing that is disposed between the input rotor and the output rotor is constructed as a cylindrical roller bearing in order to move the output rotor in the axial direction; however, the roller bearing may be constructed as a ball bearing in the event that the output rotor is not displaced in the axial direction.

The unidirectional clutch cage is in contact with the inner ring of the roller bearing; however, the outer ring of the roller bearing can be arranged on the output rotor as a separate member, and the outer ring can be placed in contact with the unidirectional clutch cage. The power generation device of the present embodiment is exemplified in a case of using the wind force as an external force; however, the power generating device of the present embodiment may be applicable to the power generating device that generates electricity by using a different external force, such as hydraulic power or thermal energy.

Next, the structure of the power generation device of the second embodiment with respect to the unidirectional clutch will be described. Descriptions of the structure that overlap the first embodiment will not be repeated. FIG. 5 is a cross-sectional view showing a connection part between the output shaft 35 of the gears 3 speed multipliers and the drive shaft 41 of the generator 4. In FIG. 5, the rotor 5 is concentrically arranged with the output shaft 35 and has a flange section 51, a large diameter flange 52a, a medium diameter section 52b and a small diameter section 52c, in this order, from one end axial (left end of FIG. 5) to another axial end (right end of FIG. 5).

The flange section 51 is shaped so that it extends to a radial exterior beyond the outer peripheral surface of the large diameter section 52a and so that it can be removably fixed at the outlet end 35c of the output shaft 35 . Specifically, the flange section 51 is fixed to the flange section 35c1 which is formed at the outlet end 35c of the output shaft 35 in a stop arrangement against the flange section 35c1 with a bolt and nut arrangement (no shown). A gap S1 is formed between the terminal face of the small diameter section 52c and the terminal face of the flange section 41a of the drive shaft 41.

The output rotor 6 is concentrically arranged on the radial section of the input rotor 5 and has a cylindrical section 61 and a flange section 62 that is formed at another axial end (right end of FIG. 5) of the cylindrical section 61 . The flange section 62 is shaped so that it extends to a radial exterior beyond the outer peripheral surface of the cylindrical section 61 and so that it is removably fixed at one end (left end of FIG. 5) of the shaft 41 drive. Specifically, the flange section 62 is fixed on a flange section 41a that is formed at one end of the drive shaft 41 in a stop arrangement against the flange section 41a with a bolt and nut arrangement (not shown).

An inner peripheral surface of the cylindrical section 61 is formed in a cylindrical surface. An annular sealing member 10 for sealing an annular space between the cylindrical section 61 and the middle diameter section 52b and the small diameter section 52c of the inlet rotor 5 is disposed between the space between the inner peripheral surface of the cylindrical section 61 at an axial end (left end of FIG. 5) and the outer peripheral surface of the large diameter section 52a of the inlet rotor 5. A gap S2 is formed between the terminal face of the cylindrical section 61 on a terminal side and a terminal face of the flange section 51 of the inlet rotor 5 facing the end face of the cylindrical section 61. Accordingly, the output rotor 6 can be moved to both axial sides with respect to the input rotor 5 in a state in which the output rotor 6 is separated from the drive shaft 41.

FIG. 6 is a cross-sectional view showing the unidirectional clutch 7, and FIG. 7 is a cross-sectional view showing a part of the unidirectional clutch 7 on an enlarged scale. In FIGS. 5 to 7, the unidirectional clutch 7 includes an inner ring 71, an outer ring 72 and several rollers 73 that are disposed between an outer peripheral surface 71a of the inner ring 71 and an inner peripheral surface 72a of the outer ring 72. The inner ring 71 is fitted and fixed on the left side of the small diameter section 52c of the inlet rotor 5 and constructed to rotate together with the small diameter section 52c in the direction of an arrow A of FIG. 6. A zone B in the axial center of the cylindrical section 61 of the output rotor 6 is fixed as the outer ring 72 of the unidirectional clutch 7. Therefore, the inner peripheral surface 72a is formed on an inner peripheral surface of the cylindrical section 61 of the zone B. The rollers 73 are formed adopting a circular cylindrical configuration and six rollers are arranged in the circumferential direction in the present embodiment .

In FIG. 6, the flat cam surfaces 71a1 having the same number of rollers 73 (six) are formed on the outer peripheral surface 71a of the inner ring 71. The inner peripheral surface 72a of the outer ring 72 is shaped as a cylindrical surface. Several (six) wedge-shaped spaces S are formed in the circumferential direction between the cam surfaces 71a1 of the inner ring 71 and the cylindrical surface 72a of the outer ring 72. The rollers 73 are arranged uniformly spaced in the respective spaces S wedge-shaped, and the elastic members 75 press the rollers 73 in the direction in which the

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Wedge-shaped S spaces narrow (narrowing direction). The outer peripheral surface of a roller 73 is shaped as a contact surface that is in contact with a cam surface 71a1 of the inner ring 71 and a cylindrical surface 72a of the outer ring 72. The unidirectional clutch 7 surrounded by a lubricating grease made with ester-based oil and a urea-based thickener so that it is not affected by temperature changes between the inner ring 71 and the outer ring 72.

In the unidirectional clutch 7 having the structure described above, in the event that the input rotor 5 rotates at a higher speed and therefore the rotation speed of the input rotor 5 exceeds that of the output rotor 6, the Internal ring 71 performs a rotation with respect to the outer ring 72 in one direction (the direction of arrow A (clockwise direction) of FIG. 6). In this case, the roller 73 moves slightly in the direction in which the wedge-shaped space S narrows due to the pushing force of the elastic member 75, the outer peripheral surface of the roller 73 is placed in contact with the surface 71a outer peripheral (cam surface 71al) of the inner ring 71 and the inner peripheral surface 72a of the outer ring 72 (i.e., the roller 73 is pressed towards the inner ring 71 and towards the outer ring 72), and the roller 73 is it places the gear between the inner ring 71 and the outer ring 72. Accordingly, the inner ring 71 and the outer ring 72 rotate together in the direction of the arrow A, and the input rotor 5 and the output rotor 6 are connected to be able to rotate together.

In the event that the rotational speed of the input rotor 5 is constant after its increase and that the speed is the same as that of the output rotor 6, the roller 73 is maintained in a gear state between the inner ring 71 and the outer ring 72 Therefore, the inner ring 71 and the outer ring 72 maintain the rotation in the direction of the arrow A, and the input rotor 5 and the output rotor 6 continue to rotate together.

On the other hand, in the event that the input rotor 5 rotates at a reduced speed and therefore the rotation speed of the input rotor 5 falls below that of the output rotor 6, the inner ring 71 performs a rotation with respect to the outer ring 72 in another direction (opposite direction of arrow A (clockwise direction) of FIG. 6). In this case, the roller 73 moves slightly in the direction in which the wedge-shaped space S widens against the pushing force of the elastic member 75, and therefore the engagement state of the outer peripheral surface of the roller 73 with inner ring 71 and with outer ring 72. Consequently, the connection between the input rotor 5 and the output rotor 6 is released.

The wind power generation device 1 which is the power generation device of the second embodiment produces an effect similar to the wind power generation device 1 of the first embodiment.

The unidirectional clutch 7 of the present embodiment is provided with a torque limiter 9. The torque limiter 9 is adapted to release the connection between the input rotor 5 and the output rotor 6 in the event that the operating torque transmitted from the input rotor 5 to the output rotor 6 exceeds a value specific (upper limit). As described above, the unidirectional clutch 7 is constructed such that the inlet rotor 5 rotates in the direction of the arrow A at a higher speed, and therefore the roller 73 engages between the cam surface 71a1 and the surface 72a internal peripheral of the outer ring 72 and cause the output rotor 6 to rotate together in the direction of the arrow A. However, when the generator 4 burns and it is difficult for the drive shaft 41 to rotate, the output rotor 6 which is coupled to the drive shaft 41 is also difficult to rotate, and the operating torque transmitted from the input rotor 5 to the output rotor 6 is excessively high. In this way, the gears 3 speed multipliers located between the output shaft 35 that is coupled to the input rotor 5 and the main shaft 2 receive an overload, and there is a possibility that the gears and bearings of the gears 3 Speed multipliers are damaged.

The torque limiter 9 of the present embodiment is intended to solve the drawbacks described above and has a housing recess 91 formed on the outer peripheral surface 71a of the inner ring 71 and can accommodate the roller 73 as shown in FIG. 6 and in FIG. 7. The housing recess 91 is formed in a corresponding position between the cam surfaces 71a1 immediately next to each other in the circumferential direction. Therefore, a total of six housing recesses 91 are formed in the present embodiment. The roller 73 that is in contact with the cam surface 71a1 that is disposed adjacently in the direction of the arrow A is adapted to fall and be housed inside the housing recess 91 when the roller 73 passes over a section 71a2 surface terminal 71a1 of cam.

As shown in FIG. 7, a lower section 91a of the housing recess 91 is formed on an arcuate surface having approximately the same radius as that of the roller 73. Some side wall sections 91b1 and 91b2 that are formed in circumferential directions of the lower section 91a are shaped in parallel with each other and on inclined surfaces with respect to an imaginary line Y in the radial direction passing through a center O of the unidirectional clutch shaft 7 and a center of curvature of the lower section 91a so that the radial exterior of the side wall section is located in the direction of the arrow A. Therefore, the side wall section 91b1 arranged in the vicinity of the roller 73 that is not housed within the housing recess 91 and that is located between the surface 71a1 of cam and the inner peripheral surface 72a of the outer ring 72 is shaped to offer a considerable length, and the section on

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Side wall 91b2 disposed on a distant side of the roller 73 is shaped to have a reduced length. Likewise, it is provided that an angle between the cam surface 71a1 and a surface of the side wall section 91b has an angle of 90 ° or greater (for example, approximately 90 ° to 120 °).

The housing recess 91 is formed with a depth in which the entire roller 73 can be accommodated. Therefore, the roller 73 that is housed in the housing recess 91 is located in a radial interior with respect to the elastic member 75. The elastic member 75 is provided with a cover member 93. The cover member 93 is shaped, as shown in FIG. 7, adopting a square bottom tube profile to surround a circumferential end face (end face disposed on one side of the roller 73), a radial outer surface, a radial inner surface, and axial side surfaces of the elastic member 75. A section 93a covering a circumferential end face is in contact with the roller 73. A section 93b covering the radial outer surface of the elastic member 75 is formed by adopting an arcuate profile along the inner peripheral surface 72a of the outer ring 72 . A coating of fluorocarbon or molybdenum disulfide polymers is applied to section 93b so that section 93b slides smoothly when in contact with the inner peripheral surface 72a of the outer ring 72 and, therefore, reduces the drag of friction.

When the operating torque transmitted from the input rotor 5 to the output rotor 6 exceeds the upper limit, the roller 73 passes over the terminal section 71a2 from the cam surface 71a1, falls into the housing recess 91, as shown in FIG. 8, and is separated from the wedge-shaped space S between the cam surface 71a1 and the inner peripheral surface 72a of the outer ring 72. Therefore, the connection between the input rotor 5 and the output rotor 6 is completely released, and the transmission of the operating torque between both rotors is severed. In this way, the input rotor 5 rotates almost free of charge, the load applied to the gears 3 speed multipliers can be reduced, and the gears 3 speed multipliers can be prevented from being damaged.

The input rotor 5 continues to rotate at greater speed by means of gears 3 speed multipliers as long as the main shaft 2 rotates after the roller 71 is housed in the housing recess 91. However, when the roller 73 is separated from the radial outward housing recess 91 by a centrifugal force due to the rotation of the inlet rotor 5 and is again engaged between the cam surface 71a1 and the inner peripheral surface 72a of the external ring 72, the input rotor 5 connects with the output rotor 6 to be locked, and the gears 3 speed multipliers receive an intense load. In order to prevent said problem, the torque limiter 9 of the present embodiment is provided with a means of separation prevention (separation prevention device) that prevents the separation of the roller 73 from the housing recess 91 .

In particular, the separation prevention means is constructed such that a side wall section 91b2 (that is, a control section that is an edge in the circumferential direction) of the housing recess 91 protrudes from the radial outside of the roller 73. That is, if the roller 73 travels radially outward (one direction of a hollow arrow B along the imaginary line Y) by centrifugal force, the side wall section 91b2 of the housing recess 91 becomes in an obstacle to the displacement of the roller 73, and the separation of the roller 73 from the housing recess 91 can be prevented. Because the inertial force opposite the direction of the arrow A is transmitted to the roller 73 of the rotation of the input rotor 5 in the direction of arrow A, the roller 73 is more difficultly separated from the housing recess 91.

Also, the separation prevention means is also constructed with an elastic member 75 and with the cover member 93. That is, when the roller 73 disposed on the cam surface 71a1 falls into the housing recess 91, the elastic member 75 extends into the receptacle 74c, the roller 73 is located in the radial interior of the elastic member 75 and within the member 93, and at least part of the housing recess 91 is blocked by the cover member 93. Therefore, if the roller 73 travels radially outward by the centrifugal force due to the rotation of the inlet rotor 5, the elastic member 75 and the cover member 93 become obstacles to the movement of the roller 73, and it can be properly prevent the separation of the roller 73 from the housing recess 91. In particular, the separation of the roller 73 from the housing recess 91 can be prevented without major problems by arranging the cover member 93 on the elastic member 75.

In FIG. 5, a pair of roller bearings 8 is respectively disposed between the middle diameter section 52b of the inlet rotor 5 and the cylindrical section 61 of the outlet rotor 6 and between a body 53 of the intermediate ring which is coupled to section 52c of small diameter of the inlet rotor 5 to be able to rotate together with the cylindrical section 61. The pair of roller bearings 8 mutually supports the input rotor 5 and the output rotor 6. The roller bearing 8 is disposed adjacently on the axial sides of the unidirectional clutch 7 so that the axial ends of the roller bearing 8 are in contact with the axial end faces of the cage 74 of the unidirectional clutch 7.

The present invention is not limited to the second embodiment described above and can be suitably modified when put into practice. For example, in the second embodiment, the output rotor is formed as the outer ring of the unidirectional clutch and the outer ring of the roller bearing; however, these outer rings may be arranged on the output rotor as members

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separated. On the other hand, the inlet rotor can be formed as an internal ring of the unidirectional clutch and as an internal ring of the roller bearing. The roller bearing that is disposed between the input rotor and the output rotor is constructed as a cylindrical roller and the output rotor is constructed as a cylindrical roller bearing in order to move the output rotor in the axial direction; however, the roller bearing may be constructed as a ball bearing in the event that the output rotor is not displaced in the axial direction.

The housing recess of the torque limiter may not necessarily be formed at a depth to which the entire roller can be accommodated but may be formed at a depth greater than at least the radius of the roller. When the housing recess is shaped deeper than the radius of the roller, the control section may be shaped without protruding from the inner peripheral surface of the outer ring. The unidirectional clutch cage is in contact with the inner ring of the roller bearing; however, the outer ring of the roller bearing can be arranged on the output rotor as a separate member, and the outer ring can be placed in contact with the unidirectional clutch cage. Likewise, the present embodiment exemplifies the wind power generation device that uses wind force as an external force; however, the present invention can be applied to the power generating device that generates electricity by using a distant external force, such as hydraulic power or thermal energy. The unidirectional clutch of the present invention can also be implemented in applications other than that of the power generating device.

An example of a unidirectional clutch according to the present invention is arranged between the input rotor and the output rotor which is concentrically arranged on the radial rotor of the input rotor, connects the input rotor with the output rotor to be able to rotate together in a state in which the rotation speed of the input rotor exceeds that of the output rotor, and releases the connection between the input rotor and the output rotor in a state where the rotation speed of the input rotor falls below that of the output rotor. A unidirectional clutch includes the inner peripheral surface of the outer ring, the outer peripheral surface of the inner ring, the roller and the torque limiter. The inner peripheral surface of the outer ring is disposed on the side of the output rotor. The outer peripheral surface of the inner ring is disposed on the side of the inlet rotor and constitutes several wedge-shaped spaces in the circumferential direction with the inner peripheral surface of the outer ring. The roller is arranged in each of the various wedge-shaped spaces, connecting the input rotor with the output rotor to be able to rotate together by its engagement with the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring, and release the connection by undoing the gear. The torque limiter includes the housing recess that is formed on the outer peripheral surface of the inner ring, and which houses the roller separated from the wedge-shaped space when the transmission torque from the input rotor to the output rotor exceeds the upper limit and, thus, releases the gear of the roller with the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring. The torque limiter is provided with a means of separation prevention that prevents the roller disposed in the housing recess from being separated from the housing recess by the centrifugal force in association with the rotation of the input rotor.

The unidirectional clutch includes the torque limiter and, therefore, when the transmission torque from the input rotor to the output rotor exceeds the upper limit (the input rotor is connected to the output rotor to be arranged in a locked state) , the torque limiter releases the connection between the input rotor and the output rotor. When the input rotor rotates in a state in which the roller is housed in the housing recess, the roller exits the housing recess by centrifugal force, there is a possibility that the engagement of the roller with the surface occurs again. outer peripheral of inner ring (that is, outer peripheral surface of inner ring) and inner peripheral surface of outer ring (that is, inner peripheral surface of outer ring). However, the torque limiter which constitutes an example of the present invention includes the means of separation prevention that prevents the roller from separating from the housing recess and, therefore, said problems can be solved.

The separation prevention means may be constructed such that the control section that controls the movement of the roller that is housed in the housing recess over the radial exterior protrudes along the edge of the accommodation recess in the circumferential direction. According to said structure, if the roller is separated from the housing recess by centrifugal force due to the rotation of the input rotor, the control section becomes an obstacle to prevent separation. Therefore, the engagement of the roller with the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring can be properly prevented again.

The cage that has a receptacle that can accommodate the roller and maintains the circumferential separation of several rollers and the elastic member that incorporates a compression spring that presses the roller disposed in the receptacle towards the narrowing direction of the wedge-shaped space is arranged between the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring. The separation prevention means can be constructed by forming the housing recess at a depth where the roller can be located in the radial interior with respect to the elastic member. According to the exposed structure, when the roller separates from the cage receptacle to enter the housing recess, the elastic member extends to be located on the radial outside of the roller. Therefore, if the roller is separated from the recess

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Radial outwardly by centrifugal force in association with the rotation of the inlet rotor, the elastic member becomes an obstacle and separation can be prevented.

The elastic member may be provided with a locking member that blocks at least a portion of the housing recess that houses the roller. According to the exposed structure, when the elastic member is disposed on the radial outside of the roller entering the housing recess as described above, the blocking member that is fixed to the elastic member can block at least a part of the housing recess and prevent the separation of the roller without problems.

In the following lines, a third embodiment of a fifth embodiment of the present invention will be described in detail, with reference to the attached drawings. FIG. 9 is a schematic side view showing a wind power generation device according to the third embodiment of the present invention.

In FIG. 9, the wind power generating device 1 also includes an input rotor 5 which is arranged to be able to rotate together with the output shaft 35 of the speed multiplier gears 3, an output rotor 6 which is arranged to be able to rotate together with the drive shaft 41 of the generator 4, a unidirectional clutch 7 which is disposed between the input rotor 5 and the output rotor 6, a pair of roller bearings 8 which is disposed on axial sides of the unidirectional clutch 7, and a mass 9 of inertia that is arranged to be able to rotate together with the output rotor 6. The unidirectional clutch 7 and roller bearings 8 are constructed to transmit the rotation of the output shaft 35 on the drive shaft 41 through the input rotor 5 and the output rotor 6. At this point, the wind power generating device 1 of the present embodiment is constructed such that the roller bearings 8 are arranged on the axial sides of the unidirectional clutch 7; however, a roller bearing 8 may be arranged only on an axial side of the unidirectional clutch 7.

FIG. 10 is the same as that of FIG. 3, except for the mass of inertia 9. FIG. 4 also shows the unidirectional clutch 7 according to the third embodiment.

In FIG. 9 and in FIG. 10, the inertia mass 9 is formed by adopting a cylindrical profile and is fitted and fixed on the cylindrical section 61 of the output rotor 6. The mass of inertia 9 is designed so that an angular acceleration ω point (dot) through the acceleration of the output rotor 6 which is calculated by the equation below (1) is smaller than an angular acceleration ω point (dot ) b due to the deceleration of the output rotor 6 in a real use environment.

ω dota = T / I (I)

in which T is a torque for the generation of electrical energy, and I is the moment of inertia of the generator rotor and the mass of inertia. In other words, the mass of inertia 9 is designed so that the moment of inertia I of the output rotor 6 and the rotor 42 of the generator 4 is greater in order to reduce the angular acceleration ω point a of the previous equation (1) so that it is greater than the angular acceleration ω point b in the actual use environment. When the actual measured values of the rotation speed ω b of the output rotor 6 are plotted on a graph, the values show a waveform that varies up and down with little amplitude, as shown in FIG. 11. Therefore, when the slope of line D, which is drawn to pass slightly above the amplitude peaks, is established as angular acceleration ω point b in the actual use environment, it can be designed preferentially the mass of inertia 9.

FIG. 12 is a graph showing the rotational fluctuations of the output shaft of gears 3 speed multipliers and rotor 42 of generator 4. As shown in FIG. 12, if the wind force decreases and the rotation speed of the output shaft 35 rapidly decreases, the rotor 42 does not rapidly decrease the rotation speed in association with the output rotor 6 by means of the drive shaft 41 but continues to rotate with a gradual deceleration due to inertia. Therefore, in the event that the wind force fluctuates rapidly, the rotational fluctuations of the rotor 42 can be reduced.

The wind power generation device 1 which is constructed in accordance with the foregoing, produces an effect similar to the wind power generation device 1 of the first and second embodiments.

Likewise, the output rotor 6 is provided with the mass of inertia 9 to be able to rotate together and, therefore, the moment of inertia I of the output rotor 6 can be increased. Consequently, the unidirectional clutch 7 releases the connection between the input rotor 5 and the output rotor 6, and when the output rotor 6 rotates at increased speed due to the inertia of the rotor 42, the angular acceleration ω point a through the slowdown is low. Therefore, the rotation speed of the output rotor 6 can be prevented from rapidly decreasing. That is, even if the wind force decreases and the speed of rotation of the main shaft 2 decreases rapidly, the rotor 42 of the generator 4 continues to rotate inertia with the output rotor 6 and, therefore, the speed of average rotation of the rotor 42. Accordingly, the energy generation efficiency of the generator 4 can be further improved.

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FIG. 13 is a cross-sectional view showing a connection part of the output shaft of the speed multiplier gears and a drive shaft of a generator of a wind power generation device according to a fourth embodiment of the present invention In FIG. 13, the wind power generating device 1 of the present embodiment includes an electromagnetic clutch 11 that connects the output rotor 6 with the inertia mass 9 to be able to rotate together during energization and releases the connection in a non-energizing mode , a detection means 12 (detection device) that detects the rotation speed of the output rotor 6 and a control means 13 (control device) that controls the energization of the electromagnetic clutch 11.

The electromagnetic clutch 11 includes a clutch housing 14 that is disposed between the cylindrical section 61 of the output rotor 6 and the mass of inertia 9, a multi-disc clutch 15 that is disposed between the clutch housing 14 and the cylindrical section 61, a electromagnet 16 which is arranged on one axial side of the multi-disc clutch 15 and a thrust member 17 that is disposed on the other axial side of the multi-plate clutch 15. The clutch housing 14 has a cylindrical body 14a of the housing that is fitted and fixed in the cylindrical section 61 and an annular section 14b extending from an axial end of the body 14a of the housing to a radial interior.

The multi-disc clutch 15 is constructed so that several external clutch discs 15a and several internal clutch discs 15b are alternately arranged in the axial direction. The external clutch discs 15a are mounted on the inner periphery of the body 14a of the housing by means of a groove adjustment so that they can move in the axial direction. Likewise, the internal discs 15b of the clutch are mounted on the outer periphery of the cylindrical section 61 of the output rotor 6 by means of the groove adjustment so that it can move in the axial direction.

The electromagnet 16 is constructed with a U-shaped yoke 16a in cross section and a coil 16b that is held within the yoke 16a. The yoke 16a is fixed to the outer periphery of a cylindrical support member 19 which is fixed to the gearbox housing 3 speed multipliers. The support member 19 is provided with a roller bearing 20 that supports the inertia mass 9 for rotation. The roller bearing 20 is shaped like a ball bearing that includes an inner ring 20a that is adjusted and fixed on the support member 19, an outer ring 20b that is adjusted and fixed within the mass of inertia 9, and several balls (rolling elements) 20c that are located between the inner ring 20a and the outer ring 20b to be able to roll. The roller bearing 20 is shaped like a ball bearing that uses a ball as a bearing element; however, the roller bearing 20 may be shaped as a roller bearing that uses a roller as a bearing element.

The pushing member 17 is formed with a magnetic substance and mounted on a right terminal side of FIG. 13 on the inner periphery of the body 14a of the housing by means of a groove adjustment to be able to move in the axial direction. Likewise, the pushing member 17 is pressed towards the flange section 62 of the outlet rotor 6 by the pressing force of an elastic member (not shown) and held in a non-pushing position shown in FIG. 13 by the stop arrangement against a stop ring 18 fixed on the inner periphery of the body 14a of the housing.

According to the exposed structure, when the coil 16b of the electromagnet 16 is not energized, the pushing member 17 is held in the non-pushing position by the pushing force of the elastic member. Therefore, the external clutch discs 15a and the internal clutch discs 15b are not in mutual intimate contact, or the multi-disc clutch 15 is in a DISABLED state and, therefore, the connection between the output rotor 6 and the mass of inertia 9. When the coil 16b of the electromagnet 16 is energized, the thrust member 17 is attracted to the electromagnet 16 against the thrust force of the elastic member and, therefore, the thrust member 17 pushes the outer discs 15a of the Clutch and internal clutch discs 15b towards the side of the annular section 14b of the clutch housing 14. Accordingly, the external clutch discs 15a and the internal clutch discs 15b are placed in intimate mutual contact, or the multi-disc clutch 15 is in the ON state and, therefore, the output rotor 6 and the mass of inertia 9 are connected to rotate together.

The detection means 12 detects the rotation speed of the drive shaft 41 of the generator 4 which rotates together with the output rotor 6 in this embodiment in order to detect the rotation speed of the output rotor 6. Specifically, the detection means 12 is constructed with a sensor that is disposed in the vicinity of the drive shaft 41 that protrudes from the right side of the rotor drawing 42 of the generator 4 shown in FIG. 9 and detects the rotation speed of the drive shaft 41. The detection means 12 can detect the rotational speed of the rotor 42, the output shaft 35 and the gears 3 speed multipliers, or the output rotor 6 itself, other than the drive shaft 41. Also, the detection means 12 can use a sensor that detects the speed of rotation of the drive shaft 41 or of the rotor that is incorporated in the generator 4 in order to control the transmission of the generator 4.

The control means 13 controls the energization of the coil 16b of the electromagnet 16 when the output rotor 6 begins to rotate. In particular, the control means 13 controls that the coil 16b is not energized in order to release the connection between the output rotor 6 and the mass of inertia 9 at the start of the rotation of the output rotor 6. When the detection means 12 detects that the output rotor 6 reaches a certain rotation speed (for example,

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From 300 to 500 rpm after the start of the output rotor 6, the control means 13 controls the energization of the coil 16b in order to connect the output rotor 6 with the mass of inertia 9 to be able to rotate together. Other structures of the present embodiment are the same as that of the third embodiment and, therefore, the description is not repeated.

According to the wind power generation device 1 constructed as described above, the electromagnetic clutch 11 is not energized and the connection between the output rotor 6 and the inertia mass 9 is released until the rotor 6 of output reaches the speed of rotation determined at the beginning of the rotation and, therefore, the required operating torque to rotate the output rotor 6 at the determined rotation speed can be reduced. Accordingly, the time required to rotate the rotor 42 can be reduced at the speed of rotation determined by means of the output rotor 6 and the drive shaft 41 and, therefore, the efficiency of the generation of generator power 4. When the detection means 12 detects that the output rotor 6 reaches the determined rotation speed after the start of the rotation of the output rotor 6, the electromagnetic clutch 11 is energized, and the output rotor 6 and the mass of inertia 9 are connected to be able to rotate together and, therefore, the moment of inertia of the output rotor 6 can be increased. Therefore, when the unidirectional clutch 7 releases the connection between the input rotor 5 and the output rotor 6, the rotor 42 of the generator 4 does not rapidly decrease the rotation speed in association with the output rotor 6 but instead continues to rotate by inertia and, therefore, the average rotation speed of the rotor 42 can be increased. Consequently, the energy generation efficiency of the generator 4 can be further increased.

FIG. 14 is a cross-sectional view showing a connection part between an output shaft of the speed multiplier gears and a drive shaft of a generator in a wind power generation device according to a fifth embodiment of The present invention. In FIG. 14 the wind power generating device 1 of the present embodiment includes a viscous fluid coupling 22 as an alternative to the electromagnetic clutch 11 of the fourth embodiment. The viscous fluid coupling 22 is disposed between the cylindrical section 61 and the outlet rotor 6 and the inertia mass 9, and includes a clutch housing 23, several external clutch discs 24a, several internal clutch discs 24b, a member 25 thrust and a ball 26.

The clutch housing 23 has a cylindrical body 23a of the housing that is fitted and fixed in the cylindrical section 61 and an annular section 23b extending from an axial end of the body 23a of the housing to a radial interior. Another axial side of the body 23a of the housing is covered by a cover member 26 which is formed by an annular plate. Sealing members 28a and 28b are respectively arranged in the gap between the annular section 23b of the clutch housing 23 and the cylindrical section 61 and the separation between the body 23a of the housing and the cover member 27. An annular tight space is formed between a body 23a of the housing and the cylindrical section 61.

A viscous fluid, such as silicone oil, fills the tight space and the external clutch discs 24a and the internal clutch discs 24b are alternately arranged in the axial direction. The external clutch discs 24a are mounted on the inner periphery of the body 23a of the housing by means of a groove adjustment to be able to move in the axial direction. Likewise, the internal disks 24b of the clutch are mounted on the outer periphery of the cylindrical section 61 of the output rotor 6 by means of the groove adjustment so that they can move in the axial direction.

The pushing member 25 is mounted on a right side of FIG. 14 on the inner periphery of the body 23a of the housing by means of the groove adjustment to be able to move in the axial direction. A lateral surface of the thrust member 25 formed with an inclined surface 25a that is inclined so that the thickness of the thrust member 25 in the axial direction gradually increases towards the radial outside. Accordingly, a wedge-shaped space K is formed between the inclined surface 25a of the thrust member 25 and the cover member 27 to narrow radially outward. Several balls 26 are housed in the wedge-shaped space K in the circumferential direction. The pushing member 25 is always pushed to the side of the flange section 62 of the exit rotor 6 by the pushing force of the elastic member (not shown) and held in a non-pushing position shown in FIG. 14 by the stop arrangement against the ball 26. In the present embodiment, the centrifugal clutch mechanism 29 is constructed with the external clutch discs 24a, the internal clutch discs 24b, the thrust member 25, and the ball 26.

According to the exposed structure, when the output rotor 6 rotates at low speed during the onset of rotation, the centrifugal force applied to the ball 26 of the viscous fluid coupling 22 is small. Therefore, as shown in FIG. 14, the ball 26 is located in the radial interior of the wedge-shaped space K, and the pushing member 25 is held in the non-pushing position by the pushing force of the elastic member. Therefore, the external clutch discs 24a and the internal clutch discs 24b are not in intimate mutual contact, or the centrifugal clutch mechanism 29 is in a DEACTIVATED state and, therefore, the operating torque of the output rotor 6 it is transmitted to the mass of inertia 9 by the viscous entrainment of the viscous fluid.

In FIG. 14, when the output rotor 6 reaches a certain rotation speed to rotate at high speed, the centrifugal force applied to the ball 26 of the viscous fluid coupling 22 increases. Therefore, ball 26 is

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shifts radially out of the wedge-shaped space K along the inclined surface 25a of the thrust member 25 by centrifugal force. In this case, the pushing member 25 is pushed towards the side of the annular section 23b of the clutch housing 23 by the ball 26 and, therefore, the pushing member 25 pushes the outer clutch disks 24a and the disks 24b internal clutch to the side of the annular section 23b against the pushing force of the elastic member. Accordingly, the external clutch discs 24a and the internal clutch discs 24b are placed in intimate mutual contact, or the mechanism 29 of the centrifugal clutch is in an ON state and, therefore, the operating torque of the output rotor 6 it is transmitted to the mass of inertia 9 by means of the centrifugal mechanism 29 of the clutch.

FIG. 15 is a graph showing the rotational fluctuations of the output rotor 6 and the mass of inertia 9 of the present embodiment. As shown in FIG. 15, when the output rotor 6 rotates at low speed during the onset of rotation, or when the operating torque of the output rotor 6 is transmitted to the mass of inertia 9 by the viscous entrainment of the viscous fluid, the mass of inertia 9 increases the speed with a lower angular acceleration (the slope of a dashed line shown in FIG. 15) than the angular acceleration of the output rotor 6 (the slope of a continuous line shown in FIG. 15). Likewise, when the output rotor 6 reaches the determined rotation speed ωc to rotate at high speed, or when the operating torque of the output rotor 6 is transmitted to the mass of inertia 9 through the centrifugal mechanism 29 of the clutch , the mass of inertia 9 rotates together with the output rotor 6 with the same rotation speed ωc. Other structures of the present embodiment are the same as those of the third and fourth embodiments and, therefore, the description is not repeated.

According to the wind power generation device 1 constructed as described above when the output rotor 6 rotates at low speed at the beginning of the rotation, the operating torque of the output rotor 6 is transmitted to the ground. of inertia 9 by the viscous entrainment of the viscous fluid and, therefore, the mass of inertia 9 increases the speed with an angular acceleration less than the angular acceleration of the output rotor 6. In other words, the inertia torque due to the mass of inertia 9 that is applied to the output rotor 6 at the start of the rotation of the output rotor 6 can be reduced and, therefore, the required operating torque can be reduced to increase the rotation speed of the output rotor 6 to the determined rotation speed. Accordingly, the time required to increase the rotational speed of the torque 42 to the rotational speed determined by means of the output rotor 6 and by the drive shaft 41 can be reduced, and therefore, the efficiency of Generator 4 power generation. Likewise, when the output rotor 6 reaches the rotation speed determined to rotate at high speed, the operating torque of the output rotor 6 is transmitted to the mass of inertia 9 by means of the 29 centrifugal clutch mechanism. Consequently, the output rotor 6 and the mass of inertia 9 are connected to be able to rotate together and, therefore, the moment of inertia of the output rotor 6 can be increased. Thus, the unidirectional clutch 7 releases the connection between the input rotor 5 and the output rotor 6, the rotor 42 of the generator 4 does not rapidly decrease the rotation speed in association with the output rotor 6 but instead continues to rotate by inertia and, therefore, the average rotation speed of the rotor 42 can be increased, and the efficiency of the generator power generator 4 can be further improved.

The present invention is not limited to the above-described embodiments described above and can be suitably modified when put into practice. For example, in the present embodiment, the input rotor and the output rotor are respectively arranged on the output shaft and on the drive shaft as separate members; however, the input rotor and the output rotor can be integrally formed, respectively, with the output shaft and the drive shaft. The output rotor is arranged on the radial outside of the input rotor; however, the output rotor may be arranged on the radial inside of the input rotor. In this case, the unidirectional clutch can be formed with the inner peripheral surface of the outer ring as a cam surface, and the outer peripheral surface of the inner ring can be shaped as a cylindrical surface. Likewise, in this case, the outer peripheral surface of the inner ring can be formed on the outer peripheral surface of the output rotor, and the output rotor can be used as an internal ring.

Also, the output rotor is formed as an outer ring of the unidirectional clutch and as an outer ring of the roller bearing; however, these outer rings may be arranged on the output rotor as separate members. The roller bearing that is disposed between the input rotor and the output rotor is constructed as a cylindrical roller bearing in order to move the output rotor in the axial direction; however, the roller bearing may be constructed as a ball bearing in case the output rotor is not displaced in the axial direction.

The unidirectional clutch cage is in contact with the inner ring of the roller bearing; however, the outer ring of the roller bearing can be arranged on the output rotor as a separate member and the outer ring can be placed in contact with the unidirectional clutch cage. The power generation device of the present embodiment is exemplified in a case of using the wind force as an external force; The power generating device of the present embodiment can be applicable to the power generating device that generates electricity by using a distant external force, such as hydraulic power or thermal energy.

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In the third embodiment, the mass of inertia is arranged on the output rotor as a separate member; however, the mass of inertia can be integrally formed with the output rotor. Likewise, when the output rotor is disposed within the radial interior of the input rotor, the mass of inertia may be arranged at the axial end of the output rotor so as not to interfere with the unidirectional clutch or the roller bearing.

Claims (12)

5 10 fifteen twenty 25 30 35 40 Four. Five fifty E12183632 09-19-2014 1.-A power generation device (1) comprising gears (3) speed multipliers that include a main shaft (2) capable of rotating driven by an external force; a rotation transmission mechanism (30) capable of receiving the rotation of the main shaft (2) to increase the speed of rotation of the main shaft (2), and a roller bearing (38, 39) capable of rotationally supporting an output shaft (35) capable of generating an operating torque of the rotation transmission mechanism (30); a generator (4) that includes a drive shaft (41) capable of being rotated when it receives the rotation of the output shaft (35) and configured to generate electricity in connection with the rotation of a rotating rotor along with the shaft (41) drive; an input rotor (5) disposed on the output shaft (35) to be able to rotate together with the output shaft (35); an output rotor (6) arranged on the drive shaft (41) to be able to rotate together with the drive shaft (41) and concentrically arranged on a radial interior or on a radial exterior of the input rotor (5); a unidirectional clutch (7) disposed between the input rotor (5) and the output rotor (6), the clutch being (7) unidirectional configured to connect the input rotor (5) with the output rotor (6) to rotate together with the input rotor (5) and the output rotor (6) when a rotation speed of the rotor (5) ) input exceeds the rotation speed of the output rotor (6), and the unidirectional clutch (7) being configured to release a connection between the input rotor (5) and the output rotor (6) when the rotation speed of the input rotor (5) falls below the rotational speed of the output rotor (6); and a pair of roller bearings (8) disposed between the input rotor (5) and the output rotor (6) and configured to support the input rotor (5) and the output rotor (6) so that the rotor (5) input and output rotor (6) rotate in relation to each other; wherein the unidirectional clutch (7) includes an outer peripheral surface (71a) of an inner ring (71), an inner peripheral surface (72a) of an outer ring (72), and a roller (73) disposed on each of the various wedge-shaped spaces (S) formed between the outer peripheral surface (71a) of the inner ring (71) and the inner peripheral surface (72a) of the outer ring (72), wherein the unidirectional clutch (7) is configured to connect the input rotor (5) with the output rotor (6) to rotate together with the input rotor (5) and the output rotor (6) through the engagement of the roller (73) with the outer peripheral surface (71a) of the inner ring (71) and the inner peripheral surface (72a) of the outer ring (72), wherein the unidirectional clutch (7) is configured to release the connection between the input rotor (5) and the output rotor (6) to release the roller gear (73) with the outer peripheral surface (71a) of the ring (71) internal and the inner peripheral surface (72a) of the outer ring (72), in which the unidirectional clutch (7) includes an annular cage configured to contain the various rollers at a certain distance along the circumferential direction, characterized because the pairs of roller bearings (8) are arranged on the respective axial sides of the unidirectional clutch (7) so that each of the pairs of roller bearings (8) is disposed adjacent to the unidirectional clutch (7) and one end (81b1) axial of each of the pairs of roller bearings (8) is able to be in contact with a corresponding face of the axial end faces of an annular cage (74) of the unidirectional clutch (7), and because The pairs of roller bearings (8) are a pair of cylindrical roller bearings (8), each of which includes several cylindrical rollers (83) and a portion (81b) with which terminal faces can be placed in sliding contact of the plurality of cylindrical rollers (83) in axial direction, and The axial end faces of the unidirectional clutch ring cage (74) can be placed in contact with the portion (81b) of the cylindrical roller bearing pair (8). 2. The power generation device (1) according to claim 1, wherein the inner peripheral surface (72a) of the outer ring (72) of the unidirectional clutch (7) is a cylindrical surface, the cylindrical roller bearing (8) includes a bearing surface (82a) of an outer bearing ring (82) (82). 8) cylindrical roller where the cylindrical roller bearing (8) rolls, the output rotor (6) is arranged on a radial exterior of the input rotor (5), and the inner peripheral surface (72a) of the outer ring (72) of the unidirectional clutch (7) and the bearing surface (82a) are formed on an inner peripheral surface of the output rotor (6). 3. The power generation device (1) according to claim 2, wherein 22 5 10 fifteen twenty 25 30 35 40 Four. Five E12183632 09-19-2014 The output rotor (6) is removably fixed on the drive shaft (41) and arranged to be able to move in the axial direction with respect to the input rotor (5). 4. The power generation device (1) according to any one of claims 1 to 3, wherein The unidirectional clutch (7) is provided with a torque limiter (9) configured to release the connection between the input rotor (5) and the output rotor (6) when the transmission torque from the input rotor (5) to the rotor (6) Output exceeds an upper limit. 5. The power generation device according to claim 4, wherein the torque limiter (9) is provided with a housing recess (91) that is formed on the outer peripheral surface (71a) of the inner ring (71) and that is adapted to accommodate the roller (73) separated from the space (S ) wedge-shaped, when the transmission torque exceeds the upper limit, to release the roller gear (73) with the outer peripheral surface (71a) of the inner ring (71) and the inner peripheral surface (72a) of the ring ( 72) external. 6. The power generation device according to claim 5, wherein the outer peripheral surface (71a) of the inner ring (71) is arranged in the input rotor (5), and the torque limiter (9) is provided with a means of preventing separation that prevents the roller (73) arranged in the housing recess (91) from being separated from the housing recess (91) by the centrifugal force due to the Rotation of the input rotor (5). 7. The power generation device according to claim 6, wherein The separation prevention means is constructed in such a way that a restriction section restricting the movement of the roller (73) housed in the recess (91) of the housing on the radial exterior (B) protrudes along a recess edge (91) of accommodation in the circumferential direction. 8. The power generation device according to claim 6 or 7, wherein a receptacle (74c) configured to accommodate the roller (73) is disposed between the outer peripheral surface (71a) of the inner ring (71) and the inner peripheral surface (72a) of the outer ring (72), a cage (74) configured to keep the rollers (73) at a certain distance along the circumferential direction and an elastic member (75) configured to push the roller (73) disposed within the receptacle (74c) towards a direction of wedge-shaped space (S) are arranged between the outer peripheral surface (71a) of the inner ring (71) and the inner peripheral surface (72a) of the outer ring (72), and The housing recess (91) is formed with a depth at which the roller (73) is located in a radial interior with respect to the elastic member (75). 9. The power generation device according to claim 8, wherein the elastic member (75) is provided with a blocking member capable of blocking at least a part of the recess (91) of housing that can accommodate the roller (73). 10. The power generation device according to any one of claims 1 to 9, further comprising: a mass (9) of inertia arranged to be able to rotate together with the output rotor (6). 11. The power generation device according to claim 10, further comprising: an electromagnetic clutch (11) configured to connect the output rotor (6) with the mass of inertia (9) so that the output rotor (6) and the mass of inertia (9) rotate together during energization and to release the connection between the output rotor (6) and the mass of inertia (9) when it does not occur the energization; a detection means (12) configured to detect the rotation speed of the output rotor (6); Y a control means (13) configured to control the arrangement of the electromagnetic clutch (11) in a non-energized state at the start of the rotation of the output rotor (6) and to control the energization of the electromagnetic clutch (11) when the medium ( 12) Detection detects that the output rotor (6) reaches a certain rotation speed after the start of the rotation of the output rotor (6). 12. The power generation device according to claim 10, further comprising: 2. 3 E12183632 09-19-2014 a coupling (22) of viscous fluid disposed between the output rotor (6) and the mass of inertia (9), The viscous fluid coupling (22) includes: i) a viscous fluid that transmits an operating torque of the output rotor (6) to the mass of inertia (9) by the viscous drag in the course of low speed rotation of the output rotor (6), and ii) a centrifugal clutch mechanism (29) capable of 5 transmit the operating torque of the output rotor (6) to the mass of inertia (9) by using the centrifugal force in association with the high-speed rotation of the output rotor (6) during high-speed rotation of the rotor (6) output. 24