JP2003314446A - High-speed fluid device - Google Patents

Abstract

(57) [Summary] [PROBLEMS] A high-speed fluid device incorporating a high-speed fluid machine such as a turbomachine, a supercharger, a blower, or the like. A low-speed side shaft provided with an outer ring at one end.
A high-speed shaft rotatably supported eccentrically with respect to the low-speed shaft and the outer ring; and at least one guide roller 37a, rotatably supported between the outer ring 32 and the high-speed shaft 17. 37b and at least one movable roller 38, a friction roller type speed increasing device utilizing a wedge action, a drive shaft 61 connected to an electric motor 60 connected to a low speed side shaft, and a high speed And a high-speed fluid machine 51 driven by the side shaft.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a high speed fluid device for flowing a fluid at a high speed, for example, a high speed fluid device incorporating a high speed fluid machine such as a turbomachine, a supercharger, or a blower.

[0002]

2. Description of the Related Art Conventionally, as a high-speed fluid device, for example, JP-A-4-203421 and JP-A-11-2945.
The supercharger for a vehicle engine disclosed in Japanese Patent Publication No. 48 is a centrifugal type, in which power is directly belt-transmitted from a drive shaft of the engine, speed is increased by a speed increaser, and the impeller is rotationally driven. Has become.

The one disclosed in Japanese Patent Laid-Open No. 4-203421 uses a planetary gear mechanism as a speed increaser in order to obtain a high speed increasing ratio. However, at rotational speeds ranging from tens of thousands rpm to 100,000 rpm or more, there is a great problem in service life as well as gear vibration and noise.

In Japanese Patent Laid-Open No. 11-294548, a system using a planetary roller of a friction roller mechanism is used. However, by tightening the planetary roller and the sun shaft with a flexible outer ring, it is necessary for a traction drive. It has a structure to obtain pressing force. Therefore, slippage occurs at high rotation and high torque, and the driving force cannot be transmitted to the impeller. In order to prevent this, it is necessary to tighten the planetary roller with the outer ring with even greater force.However, in a low rotation and low torque state, the planetary roller is pressed with an excessive pressing force, resulting in reduced efficiency. I will end up. At the same time, since a large pressing force always works, there is a problem in terms of life.

[0005]

Further, as described above, in the system in which power is directly obtained from the drive shaft of the engine by belt transmission, the mounting position of the supercharger is necessarily attached to the crankshaft of the engine. It will be limited to the same plane as the pulley.

On the other hand, the engine room is very crowded due to the recent high performance of the engine, the electrification of automobiles, the securing of collision safety of the vehicle body, etc., and the installation position of the supercharger has a high degree of freedom. Absent.

From the supercharger side, optimization of the distance to the engine intake port, the mounting position of the intercooler and the distance to the intercooler is desired.

However, the installation position of the supercharger is limited due to the above-mentioned reasons, and optimization is difficult.

In the method of extracting power from the engine crankshaft, the turbine speed of the supercharger is proportional to the engine speed. As a result, if the supercharger is designed so as to obtain a sufficient supercharging effect even when the engine is at low speed, there is a drawback that the supply air amount and the boost pressure are too excessive at high engine speed. As a method of eliminating this drawback, a method of providing a continuously variable transmission or an electromagnetic clutch on the input pulley portion of the speed increaser has been proposed, but such a method complicates the system and increases the weight and volume. However, there is a problem that the cost increases.

The object of the present invention has been made in view of the above-mentioned circumstances, and it is possible to perform quiet and smooth power transmission, obtain high transmission efficiency, and have high mountability and controllability. It is to provide a small-sized, lightweight, inexpensive high-speed fluid device.

[0011]

In order to achieve the above object, a high speed fluid device according to the present invention includes a low speed side shaft rotatably supported by a housing and an outer ring provided at one end thereof, and the low speed side shaft and A high-speed side shaft eccentric to the outer ring and rotatably supported by the housing, and at least one guide roller and at least one guide roller rotatably supported between the outer ring and the high-speed side shaft. A friction roller type speed increaser utilizing a wedge action composed of a movable roller, an electric motor having a drive shaft connected to the low speed side shaft, and a high speed connected to the high speed side shaft and driven by the high speed side shaft. Fluid machinery,
It is characterized by consisting of.

As described above, according to the present invention, the impeller of the high speed fluid machine is configured to be driven by the friction roller type speed increaser utilizing the wedge action. Since it is a drive, it can transmit power quietly and smoothly even at high speeds, so there is no problem of vibration or noise. Further, since the pressing force required for the traction drive is a mechanism obtained by a wedge action and an appropriate pressing force proportional to the transmission torque is always obtained, slippage does not occur. At the same time, high efficiency can be obtained from a low rotation and low torque region to a high rotation and high torque region. Also,
Since the electric motor is built in, there is no limitation on the mounting position in the engine room, and it is possible to mount at the optimum position.

In the high speed fluid device of the present invention, the high speed fluid machine may be a blower.

In the high speed fluid device of the present invention, the blower as the high speed fluid machine may be a centrifugal high speed fluid machine, a positive displacement fluid machine, or an axial flow fluid machine.

In the high speed fluid system of the present invention, the centrifugal fluid machine preferably comprises an impeller.

In the high speed fluid device of the present invention, the positive displacement fluid machine may be a roots type positive displacement fluid machine.

In the high-speed fluid machine of the present invention, the axial flow type fluid machine may be a Risholm type axial flow type fluid machine.

In the high-speed fluid device of the present invention, when the high-speed fluid machine is used as a centrifugal fluid machine and the present invention is applied to a centrifugal supercharger, the efficiency is high and the motor can be downsized. Since the feeder itself is also small, it has the advantage that it is easy to install and the drive power of the motor is small.

When the high-speed fluid device of the present invention is used, for example, in an engine supercharger, the optimum rotational speed can always be obtained by controlling the motor. It is possible to avoid an excessive amount and boost pressure, and it is possible to always perform optimum supercharging without installing another means such as a continuously variable transmission.

Conventionally, tens of thousands rpm to 100,000 rp
Since there is no gearbox capable of increasing the rotational speed to reach m or more, such a method of driving with an electric motor has not been obtained.

Further, the high-speed fluid device of the present invention can be used not only in the engine supercharger but also in, for example, a fuel cell vehicle.
It can also be applied to a blower for feeding hydrogen as a fuel, a blower for blowing away water and water vapor generated by the reaction of hydrogen and oxygen, and the like.

The traction drive type transmission is
Since it is quiet and smooth, it has been developed for various industrial uses, and in recent years, attempts have been made to apply it to personal use such as automobiles and bicycles, and it has attracted attention as a next-generation power transmission system.

Unlike the gear transmission, the traction drive type transmission strongly presses at least two rotating bodies having smooth surfaces, and a lubricating oil film (for example, an EHL oil film) is interposed between them to transmit power. It is a mechanism for transmission, and its basic formula is expressed by a simple friction formula Ft = μ · Fc (Ft: traction force). Where Fc
Is called pressing force, and various methods have been developed to generate this.

As one of the traction drive type transmissions, there is a friction roller type transmission utilizing a wedge action (hereinafter referred to as a wedge roller type transmission in this specification). The wedge roller type transmission is around the tip of the high speed side shaft and is eccentric to the high speed side shaft,
A rotatably provided outer ring exists between the driven-side cylindrical surface that is the outer peripheral surface of the high-speed side shaft and the drive-side cylindrical surface that is the inner peripheral surface of the outer ring, and has a radial width of a circle. A transmission provided in at least one guide roller and at least one movable roller, each outer peripheral surface of which is a cylindrical surface for power transmission, disposed in an annular space that is not uniform in the circumferential direction. . The movable roller is a roller that generates a pressing force by a wedge action, and is a roller that moves in the radial direction and the circumferential direction.

[0025]

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, a high speed fluid device using a wedge roller type transmission according to an embodiment of the present invention will be described with reference to the drawings.

First, the internal structure of the wedge roller type transmission common to the respective embodiments will be described in detail, and then the first embodiment and the second embodiment will be described.

FIG. 1 is a sectional view of an engine supercharger incorporating a wedge roller type transmission as a high speed fluid device according to an embodiment of the present invention. 2 is a sectional view of the wedge roller type transmission having a one-way clutch function taken along the line bb of FIG. 1, FIG. 3 is a diagram for explaining the operation of the wedge roller type transmission, and FIG. FIG. 3 is a cross-sectional view of a wedge roller type transmission that can transmit torque when rotating in opposite directions.

In the present embodiment, the wedge roller type transmission A acts as a speed increasing gear with the low speed side shaft 3 (outer ring side) as the input side and the high speed side shaft 17 as the output side.
However, the present device can also be applied to a speed reducer having a low speed side shaft (outer ring side) as an output side.

Further, as shown in FIG. 2, the wedge roller type transmission A has a one-way clutch function which transmits torque during forward rotation but does not transmit torque during reverse rotation. As shown in FIG. 4, torque may be transmitted during both forward and reverse rotations.

In the wedge roller type transmission A according to the embodiment of the present invention, in FIGS. 1 and 2, a housing 2 which is a partition plate is fixed to a substantially cylindrical housing 1. A low speed side shaft 3 is rotatably supported by the housing 1, and at the end of the low speed side shaft 3 in the housing 1,
A disc-shaped member 4 is provided, and an outer ring 32 is attached to the outer edge portion of the disc-shaped member 4.

A high speed side shaft 17 is eccentrically (offset) with respect to the low speed side shaft 3 and the outer ring 32 and is rotatably provided in the housing 2 which is a partition plate.

As shown in FIG. 2, a large diameter guide roller 37a is provided between the outer ring 32 and the high speed side shaft 17.
A guide roller 37b having a small diameter and a movable roller 38 that moves when torque is transmitted are interposed.

As shown in FIG. 3, the support shaft 39b for rotatably supporting the movable roller 38 is constructed so as to be movable between the high speed side shaft 17 and the outer ring 32 in the direction of biting into the "wedge". Further, it is urged by an elastic material 47 (see FIG. 2) such as a compression spring installed in the cylinder hole 46 in a direction to bite into the “wedge”.

Thus, as shown in FIG. 3, during normal rotation, the movable roller 38 has the high speed side shaft 17 and the outer ring 32.
It moves in a direction that bites into the "wedge" between and, and generates a pressing force Fc. Traction force is generated by this Fc, and torque can be transmitted.

On the other hand, during reverse rotation, the movable roller 38 is
Move in the direction away from the "wedge" and press force Fc =
It becomes 0, the outer ring 32 spins, and torque cannot be transmitted to the high speed side shaft 17.

As shown in FIG. 2, between the inner peripheral surface of the outer ring 32 and the outer peripheral surface of the distal end portion of the high speed side shaft 17, there is provided an annular space 36 having a radial width which is different in the circumferential direction. .

The wedge roller type transmission A is constructed by installing two guide rollers 37a and 37b and one movable roller 38 in such an annular space 36.
In the figure, the movable roller 38 is partially cut away and is shown. In order to install each of these rollers 37a, 37b, 38, three support shafts 39a,
39a and 39b are provided. These three support shafts 39
Two support shafts 39a, 39 of a, 39a, 39b
a is the housing 2 and the connecting plate 14 at both ends thereof.
It is press-fitted and fixed in the fitting holes 40, 40 formed in 1. Therefore, the two support shafts 39a, 39a are not displaced in the annular space 36 in the circumferential direction or the diametrical direction. On the other hand, the above three support shafts 39a, 39a, 39b
Of the remaining one of the supporting shafts 3 located on the upper left side of FIG.
9b supports both ends of the outer ring 32 with respect to the housing 2 and the connecting plate 14 so as to be slightly displaceable in the circumferential direction and the diametrical direction. For this reason, a support hole 41 having an inner diameter larger than the outer diameter of the support shaft 39b is formed in a portion of the housing 2 and the connecting plate 14 aligned with both ends of the one support shaft 39b. Both ends of the support shaft 39b are loosely engaged with the respective support holes 41.

Then, each support shaft 39 supported as described above.
The guide rollers 37a, 37b and the movable roller 38 are rotatably supported by bearings such as radial needle bearings 42, 42 (the bearings of the movable roller are not shown) around the intermediate portions of a, 39a, 39b. is doing. In order to connect and fix the connecting plate 14 to the housing 2, the protrusions 27, 27 projectingly provided on one surface of the connecting plate 14 have the guide rollers in the circumferential direction of the connecting plate 14. It exists between 37a, 37b and the movable rollers 38. In other words, the protrusions 27, 27 and the guide rollers 37a are provided in the annular space 36.
37b or movable rollers 38 are alternately present in the circumferential direction of the annular space 36. Further, the outer peripheral surface of each of the guide rollers 37a and 37b or the movable roller 38 and the circumferential side surface of each of the protrusions 27 and 27 do not interfere (rub) with each other.

In this way, the support shafts 39a, 39a are
The guide rollers 37a, 3a rotatably supported between the housing 2 and the connecting plate 14 by a and 39b.
7b and the outer peripheral surface of the movable roller 38, the power transmission cylindrical surfaces 43a, 43a, 43b are driven side cylindrical surfaces 44 which are the outer peripheral surfaces of the tip of the high speed side shaft 17, respectively.
And the drive side cylindrical surface 45 which is the inner peripheral surface of the outer ring 32. As described above, each of the guide rollers 37
The radial widths of the annular space 36 in which the a and 37b and the movable roller 38 are installed are different in the circumferential direction. As described above, the guide rollers 37a and 37b are equal in width to the annular space 36 in the circumferential direction.
Also, the outer diameter of the movable roller 38 is different. That is, of the guide rollers 37a, 37b and the movable roller 38, the movable roller 38 and the guide roller 37b located on the side where the tip of the high-speed side shaft 17 is eccentric with respect to the outer ring 32 (upper side in FIG. 2). The outer diameter is the same as each other and is relatively small. On the other hand, the outer diameter of the guide roller 37a located on the opposite side (lower side in FIG. 2) of the outer ring 32 to which the tip of the high-speed shaft 17 is eccentric is set to the movable roller 38 and the guide roller 37b. Larger than the outer diameter of. Then, the power transmission cylindrical surfaces 43a, 43a, 43b which are the outer peripheral surfaces of the guide rollers 37a, 37b and the movable roller 38.
Are brought into contact with the driven-side and driving-side cylindrical surfaces 44 and 45, respectively.

Of the guide rollers 37a, 37b and the movable roller 38, the guide rollers 37a, 37 are used.
Both ends of the support shafts 39a, 39a supporting b are fixed to the housing 2 and the connecting plate 14 (in the annular space 36) as described above. On the other hand, the support shaft 39b that supports the movable roller 38 does not move relative to the housing 2 and the connecting plate 14 (the annular space 3) as described above.
In (6), a slight displacement in the circumferential direction and the diametrical direction is possible. Therefore, the movable roller 38 also
Within the annular space 36, some displacement is possible in the circumferential direction and the diametrical direction. Then, the housing 2 and the connecting plate 1
A support shaft 39 that supports the movable roller 38 by an elastic material 47 such as a compression spring installed in the cylinder hole 46 of No. 4
b is elastically lightly pressed to move the movable roller 38 rotatably supported by these support shafts 39b toward the narrow portion of the annular space 36.

When the rotary shaft is rotationally driven by the wedge roller type transmission configured as described above, the driving force is input to the low speed side shaft 3 to rotate the outer ring 32 clockwise in FIG. The rotation of the outer ring 32 is transmitted to the high speed side shaft 17 via the guide rollers 37a and 37b and the movable roller 38, and the high speed side shaft 17
Is rotated counterclockwise in FIG. Power transmission between the outer ring 32 and the guide rollers 37a, 37b and the movable roller 38, and the guide rollers 37a, 37
Power transmission between the high speed side shaft 17 and the movable roller 38b is performed by friction transmission, so that noise and vibration generated during power transmission are low.

The movable roller 38 is composed of the outer ring 32.
The width of the annular space 36 is narrowed by a force corresponding to the magnitude of the torque transmitted from the high speed side shaft 17 to the high speed side shaft 17 (see FIG. 2).
The upper middle part of the) tends to cut into. Therefore, the contact portion between the driving side cylindrical surface 45 which is the inner peripheral surface of the outer ring 32 and the power transmission cylindrical surface 43a, 43a and 43b which is the outer peripheral surface of the guide rollers 37a and 37b and the movable roller 38, and , These power transmitting cylindrical surfaces 43a, 43
The surface pressure of the abutting portion between a and 43b and the driven side cylindrical surface 44 which is the outer peripheral surface of the high speed side shaft 17 becomes higher as the torque increases. Conversely, when this torque is small, the surface pressure of each of the contact portions is low. Therefore, the surface pressure of each of these contact portions is set to an appropriate value according to the torque to be transmitted, and the torque can be efficiently transmitted.

That is, when the outer ring 32 rotates clockwise in FIG. 2 and the high speed side shaft 17 also rotates counterclockwise, the movable roller 38 moves the outer ring 32.
From the driving side cylindrical surface 45 which is the inner peripheral surface of the above and the driven side cylindrical surface 44 which is the outer peripheral surface of the high speed side shaft 17, a force in the same direction as the pressing force by the elastic material 47 is received and the annular space 36 2 tends to move toward the narrow part, that is, toward the center of the upper part of FIG.

As a result, the power transmission cylindrical surface 43b, which is the outer peripheral surface of the movable roller 38, is replaced by the drive side cylindrical surface 45.
And the driven side cylindrical surface 44 are strongly pressed. And
This power transmission cylindrical surface 43b and the driven side cylindrical surface 44
The contact pressure of the inner diameter side contact portion 48, which is the contact portion with the drive force, and the outer diameter side contact portion 49, which is the contact portion between the power transmission cylindrical surface 43b and the drive side cylindrical surface 45, are high. Become. In this way, both the inner diameter side and outer diameter side contact portions 4 of the movable roller 38 are
When the abutting pressure of 8, 49 is increased, the high-speed side shaft 17 and the outer ring 32, which are pressed by the power transmission cylindrical surface 43b that is the outer peripheral surface of the movable roller 38, have a diameter due to elastic deformation and assembly clearance. Slightly displaced in the direction. As a result, the contact pressures of the inner diameter side and outer diameter side contact portions 48 and 49 with respect to the guide rollers 37a and 37b are increased. Then, both of these inner diameter side and outer diameter side contact portions 48,
Based on the frictional engagement at 49, the rotational force of the outer ring 32 can be transmitted to the high speed side shaft 17 via the guide rollers 37a and 37b and the movable roller 38.

As described above, the force for moving the movable roller 38 toward the narrow portion of the annular space 36 is large as the rotational driving force transmitted from the outer ring 32 to the high speed side shaft 17. It changes according to the size. And
As this force increases, both the inner diameter side and outer diameter side contact portions 4
The contact pressure of Nos. 8 and 49 becomes high. Therefore, based on such an action, the contact pressure corresponding to the transmitted rotational driving force is automatically selected, and the transmission efficiency of the wedge roller type transmission A can be secured.

In the case of the example shown in FIG. 2, the wedge roller type transmission A has a one-way clutch function,
When the rotation speed of the high-speed side shaft 17 becomes higher than the rotation speed of the outer ring 32, that is, the rotation speed of the outer ring 32 multiplied by the speed increasing ratio of the wedge roller type transmission A, The connection of this wedge roller type transmission A is disconnected. That is, in this case, the movable roller 38
However, against the elasticity of the elastic material 47, the annular space 36
Is displaced to the wider side (lower left side in FIG. 2). As a result,
The contact pressure between the inner diameter side and outer diameter side contact portions 48, 49 is reduced or lost, and the rotation of the outer ring 32 is not transmitted to the high speed side shaft 17.

Next, a wedge roller type transmission shown in FIG. 4, which is capable of transmitting torque when rotating in both forward and reverse directions, will be described.

FIG. 4 shows the high speed side shaft 17 (see FIG. 1).
Shows a structure which can be rotationally driven in both directions of a clock and a counterclockwise. Therefore, the structure of this example is implemented in combination with the high-speed fluid machine X (see FIG. 1) whose rotational direction is freely convertible. In the combination of the structure of this example, one guide roller 37 and two movable rollers 38a and 38b are conveniently used as the three rollers forming the wedge roller type transmission A. . Of these, the roller installed in the widest part of the annular space 36 is a guide roller 37 whose diameter is relatively large and whose installation position does not change. On the other hand, a pair of rollers provided with the narrowest portion of the annular space 36 sandwiched therebetween are movable rollers 38a each having a relatively small diameter and capable of slight displacement in the circumferential direction and the diametrical direction. , 38b. Then, the support shafts 39b, 39 supporting the movable rollers 38a, 38b, respectively.
b is elastically pressed toward the narrowest part of the annular space 36.

In the case of the structure of the present example configured as described above, when the outer ring 32 rotates clockwise in FIG. 4, the movable row 38a on the left side in FIG. I will cut into the part that became. On the other hand, the outer ring 3
When 2 rotates in the counterclockwise direction in FIG. 4, the movable roller 38b on the right side in FIG. 4 bites into the narrowed portion of the annular space 36. Further, in the case of this example, support shafts 39b and 39b supporting the movable rollers 38a and 38b, respectively.
In order to support both ends of the annular space 36, the lengths of the support holes 41a formed in the housing 2 and the connecting plate 14 in the circumferential direction of the annular space 36 are regulated. Specifically, of the support holes 41a, 41a, the annular space 36 is
The position of the end on the wide side (lower side in FIG. 4) is closer to the position where the width of the annular space 36 is narrower than that in the case shown in FIG. The movable rollers 38a, 38b are prevented from retreating excessively to the wider side of the annular space 36.

In the case of the present embodiment configured as described above, even if the outer ring 32 rotates in either the clockwise or counterclockwise direction, any movable roller 38a (38b) causes the width of the annular space 36 to change. Of the movable roller 38
Inner diameter side and outer diameter side contact portions 48, 4 related to a (38b)
Increase the contact pressure of 9. On the other hand, the movable roller 38b is displaced in the direction of retracting from the narrow portion of the annular space 36.
With respect to (38a) as well, the retreat amount is limited. As a result, with respect to both the movable rollers 38a, 38b and the guide roller 37, the contact pressures of the contact portions 48, 49 on the inner diameter side and the outer diameter side are sufficiently increased, and from the outer ring 32 to the high speed side shaft 17, Motion can be transmitted efficiently. As described above, except that the power can be transmitted from the rotating outer ring 32 to the high-speed side shaft 17 in both the clockwise and counterclockwise directions, the same parts as those described above with reference to FIG. Omit it.

(First Embodiment) Next, the first embodiment will be described. FIG. 1 is a cross-sectional view of an engine supercharger incorporating a wedge roller type transmission as a high speed fluid device according to a first embodiment of the present invention. FIG. 2 shows b of FIG.
FIG. 4 is a cross-sectional view of a wedge roller type transmission having a one-way clutch function along line b, FIG. 3 is a diagram for explaining the operation of the wedge roller type transmission, and FIG. It is a sectional view of a transmission wedge roller type transmission. FIG. 5 is an enlarged cross-sectional view of an example in which two angular ball bearings are frontally combined.

The hole 23 of the partition plate (housing) 2 has two holes.
One set of angular contact ball bearings 24 and 25 in which individual pieces are combined in front
And a seal member 29 is provided by the preload member 26.
It is firmly fixed with. The preload member 26 presses the outer rings of the bearings 24 and 25 in the axial direction to apply preload so as to eliminate the inner clearance of the bearing.

No bearing is provided on the high-speed fluid machine X side. This is because if the high-speed side shaft 17 is supported by two bearings that are distant from each other, it becomes impossible to slightly swing in the angular direction.

As described above, in the present embodiment, the bearing support of the high-speed side shaft 17 is made up of only one set of two angular ball bearings 24, 25 that are assembled in front.

On the side of the wedge roller type transmission A, as shown in FIG. 5, two angular contact ball bearings (24, 25) are combined in front so that the angular rigidity of the high speed side shaft 17 can be reduced and the high speed side can be reduced. The side shaft 17 can be slightly swung in the angular direction, and processing errors, assembling errors, and minute movements can be absorbed.

The high speed side shaft 17 is not only supported by these two angular ball bearings (24, 25), but also the rollers 37a, 3 on the wedge roller type transmission A side.
It is also supported by 7b and 38, and is substantially supported at two points. Therefore, the high-speed side shaft 17 is firmly supported on the side of the high-speed fluid machine X without causing a defect such as a missile movement.

Therefore, according to the present invention, it is possible to satisfy the requirements on the wedge roller type transmission A side and the requirements on the high speed fluid machine X side, which are conventionally incompatible.

Further, in the present embodiment, as shown in FIG. 1, a supercharger 50 is used as the high speed fluid machine X, and the impeller 5 of the supercharger 50 is provided at one end of the high speed side shaft 17.
1 is attached. Since the wedge roller type speed increaser A is a traction drive and can perform quiet and smooth power transmission even at high speed rotation, there is no problem of vibration or noise. Furthermore, the pressing force required for the traction drive is
Since it is a mechanism obtained by a wedge action and an appropriate pressing force proportional to the transmission torque is always obtained, no slippage occurs. At the same time, high efficiency can be obtained from a low rotation and low torque region to a high rotation and high torque region.

Further, at the other end of the high speed side shaft 17,
The drive shaft 61 of the electric motor 60 is integrally connected.
Thus, as a drive source of the wedge roller type speed increaser A,
Since the electric motor 60 is used, there is no limitation on the mounting position in the engine room, and the mounting can be performed at the optimum position.

Further, by controlling the electric motor 60, it is possible to always obtain the optimum rotation speed, so that it is possible to avoid an excessive supply air amount or boost pressure of the supercharger at the time of high engine rotation, Optimal supercharging can always be performed without installing any other means such as a continuously variable transmission.

Conventionally, tens of thousands rpm to 100,000 rp
Since there is no gearbox capable of increasing the rotational speed to reach m or more, such a method of driving with an electric motor has not been obtained.

Further, in the present embodiment, not only in the engine supercharger, but also in, for example, a fuel cell vehicle, a blower for feeding hydrogen as fuel, water and steam generated by the reaction of hydrogen and oxygen, It can also be applied to blowers for blowing off.

In this embodiment, a centrifugal high-speed fluid machine including an impeller is used as an example of a blower that constitutes the high-speed fluid machine. A flow type high speed fluid machine may be used.

When the centrifugal supercharger 50 is a high-speed fluid machine as in this embodiment, the efficiency is high and the electric motor 60 can be downsized, and the centrifugal supercharger itself is also small. It has the advantage of being easy to install and reducing the drive power of the motor.

(Second Embodiment) FIG. 6 shows a second embodiment of the present invention.
It is a sectional view of a wedge roller type gearbox of an embodiment. A sectional view of the wedge roller type transmission taken along the line bb is shown in FIG.
Since it is equivalent to FIG. Moreover, the same components as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

In this embodiment, the partition plate (housing)
No bearing is provided in the hole 23 of No. 2, and two sets of two angular ball bearings 24 and 25, which are frontally combined, are provided on the high speed side shaft 1.
It is provided at the other end of 7.

Also in this case, as shown in FIG. 5, since two angular ball bearings (24, 25) are combined in front, the angular rigidity of the high speed side shaft 17 can be reduced,
The high-speed side shaft 17 can be slightly swung in the angular direction, and processing errors, assembling errors, and minute movements can be absorbed. The high-speed side shaft 17 is not only supported by these two angular ball bearings (24, 25), but also the rollers 37a, 38 on the wedge roller type transmission A side.
It is also supported by b and 38 (see FIG. 2), and is substantially supported at two points. Therefore, the high-speed side shaft 17 is firmly supported on the side of the high-speed fluid machine X without causing a defect such as a missile movement.

Further, in the present embodiment, the supercharger 50 is used as the high speed fluid machine X, the impeller 51 of the supercharger 50 is attached to one end of the high speed side shaft 17, and the high speed side shaft 17 The drive shaft 61 of the electric motor 60 is integrally connected to the other end of the. The configuration, action, and effect in that case are the same as those in the above-described first embodiment.

Further, in the present embodiment, not only the supercharger of the engine but also, for example, a fuel cell vehicle, a blower for feeding hydrogen as a fuel, water and steam generated by the reaction of hydrogen and oxygen It can also be applied to blowers for blowing off.

(Third Embodiment) FIG. 7 shows a third embodiment of the present invention.
FIG. 3 is a cross-sectional view of the wedge roller type transmission according to the embodiment. A cross-sectional view of the wedge roller type transmission taken along the line bb is the same as FIGS. Moreover, the same components as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

In the present embodiment, a single double-row angular contact ball bearing 30 combined in front is used instead of a set of two angular contact ball bearings 24, 25 combined in front.

Also in this case, since the front combination is used, the action point distance can be made smaller than that in the rear combination. Therefore, the angular rigidity of the high-speed side shaft 17 can be reduced, the high-speed side shaft 17 can be slightly swung in the angular direction, and processing errors, assembling errors, and minute movements can be absorbed. Also, the high speed side shaft 17
Is a double-row angular contact ball bearing 3 combined with this front
Not only is it supported by 0, but it is also supported by rollers 37a, 37b, 38 (see FIG. 2) on the side of the wedge roller type transmission A, and is supported at substantially two points. Therefore,
The high-speed side shaft 6 is firmly supported on the high-speed fluid machine X side without causing a defect such as a missile movement.

Further, in the present embodiment, the supercharger 50 is used as the high speed fluid machine X, and the impeller 51 of the supercharger 50 is attached to one end of the high speed side shaft 17, and further the high speed side shaft 17 is provided. The drive shaft 61 of the electric motor 60 is integrally connected to the other end of the. The configuration, action, and effect in that case are the same as those in the above-described first embodiment.

Further, in the present embodiment, not only the engine supercharger but also, for example, a fuel cell vehicle or the like, a blower for feeding hydrogen as fuel, water and steam generated by the reaction of hydrogen and oxygen It can also be applied to blowers for blowing off.

(Fourth Embodiment) FIG. 8 shows a fourth embodiment of the present invention.
FIG. 3 is a cross-sectional view of the wedge roller type transmission according to the embodiment. A cross-sectional view of the wedge roller type transmission taken along the line bb is the same as FIGS. Moreover, the same components as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

In the present embodiment, a deep groove ball bearing 31 is used in place of the set of two angular contact ball bearings 24 and 25 that are frontally combined.

In this case, since angular rigidity is not provided, it can be applied if the rotation speed condition is not so high.

Further, in the present embodiment, the supercharger 50 is used as the high speed fluid machine X, the impeller 51 of the supercharger 50 is attached to one end of the high speed side shaft 17, and the high speed side shaft 17 The drive shaft 61 of the electric motor 60 is integrally connected to the other end of the. The configuration, action, and effect in that case are the same as those in the above-described first embodiment.

Further, in the present embodiment, not only in the engine supercharger, but also in, for example, a fuel cell vehicle, a blower for feeding hydrogen as fuel, water and steam generated by the reaction of hydrogen and oxygen It can also be applied to blowers for blowing off.

The present invention is not limited to the above-mentioned embodiments, but can be variously modified.

[0081]

As described above, according to the present invention,
A friction roller type speed increaser that uses a wedge action is configured to drive a high-speed fluid machine.The wedge roller type speed increaser is a traction drive, and it is possible to perform quiet and smooth power transmission even at high speeds. Therefore, there is no problem of vibration and noise. Further, since the pressing force required for the traction drive is a mechanism obtained by a wedge action and an appropriate pressing force proportional to the transmission torque is always obtained, slippage does not occur. At the same time, high efficiency can be obtained from a low rotation and low torque region to a high rotation and high torque region.

Further, since the electric motor is used as the drive source of the wedge roller type speed increaser, even when the electric motor is used in the engine room, for example, the mounting position in the engine room is not limited, and it is optimal. It can be mounted at any position.

Further, according to the present invention, since quiet and smooth power transmission can be performed even at high speed rotation, there is no problem of vibration or noise. Further, since the pressing force required for the traction drive is a mechanism obtained by a wedge action and an appropriate pressing force proportional to the transmission torque is always obtained, slippage does not occur. At the same time, high efficiency can be obtained from a low rotation and low torque region to a high rotation and high torque region.

Further, according to the present invention, since the electric motor is used as the drive source, the mounting position is not limited even when used in the engine room, for example, and the mounting can be carried out at the optimum position. Becomes

Further, by controlling the motor, it is possible to always obtain the optimum number of revolutions, so that it is possible to avoid an excessive supply air amount and boost pressure of the supercharger at the time of high engine revolution, and to continuously step. Optimal supercharging can always be performed without installing another means such as a transmission.

Conventionally, tens of thousands rpm to 100,000 rp
Since there is no gearbox capable of increasing the rotational speed to reach m or more, such a method of driving with an electric motor has not been obtained.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing an internal structure of a high-speed fluid device using a wedge roller type transmission according to a first embodiment of the present invention.

FIG. 2 is a sectional view taken along line bb of FIG.

FIG. 3 is a diagram illustrating an operation of a wedge roller type transmission.

FIG. 4 is a sectional view of a wedge roller type transmission according to the present invention capable of transmitting torque when rotating in both forward and reverse directions.

FIG. 5 is an enlarged cross-sectional view of an example in which two angular ball bearings are frontally combined.

FIG. 6 is a cross-sectional view of a wedge roller type transmission portion of a high speed fluid system according to a second embodiment of the present invention.

FIG. 7 is a sectional view of a wedge roller type transmission portion of a high speed fluid system according to a third embodiment of the present invention.

FIG. 8 is a sectional view of a wedge roller type transmission portion of a high speed fluid system according to a fourth embodiment of the present invention.

[Explanation of symbols]

1, 101 housing 2,102 housing (partition plate) 3,103 Low speed side shaft 4 Disc-shaped member 14 Connection plate 17,117 High speed side shaft 22 Thrust needle bearing 23, 123 holes 24, 25 angular contact ball bearing 26 Preload member 27 Projection 28 Volts 29 Seal member 30 Double Row Angular Contact Ball Bearing 31, 131a, 131b Deep groove ball bearings 32 outer ring (low speed side shaft) 33 retaining ring 34 Volts 36 annular space 37, 37a, 37b Guide roller 38, 38a, 38b Movable roller 39a, 39b Support shaft 40 fitting hole 41, 41a Support hole 42 radial needle bearing 43 Cylindrical surface for power transmission 44 Driven side cylindrical surface 45 Drive side cylindrical surface 46 Cylinder hole 47 Elastic material 48 Inner diameter side contact part 49 Outer diameter side contact part 50 supercharger 51 Impeller 60 electric motor 61 Drive shaft A wedge roller transmission (gearbox) X High-speed fluid machinery

─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. ⁷ Identification code FI theme code (reference) // F02B 39/04 F04B 35/00 101Z F term (reference) 3G005 EA04 EA05 EA06 EA19 EA20 GB45 GB73 GB78 3H022 AA02 AA03 BA03 BA07 CA06 DA11 DA20 3H076 AA16 BB21 BB40 BB41 BB43 CC07 CC15 3J051 AA01 BA03 BB08 BC03 BD02 BE04 ED04 FA10

Claims (8)

[Claims] 1. A low-speed side shaft rotatably supported by a housing and having an outer ring at one end, and a high-speed side shaft eccentric to the low-speed side shaft and the outer ring and rotatably supported by the housing. A friction roller type speed increaser utilizing a wedge action, which is rotatably supported between the outer ring and the high speed side shaft and is composed of at least one guide roller and at least one movable roller; Is a high speed fluid machine connected to the low speed side shaft, and a high speed fluid machine connected to the high speed side shaft and driven by the high speed side shaft. 2. The high-speed fluid machine according to claim 1, wherein the high-speed fluid machine is a blower. 3. The high-speed fluid device according to claim 2, wherein the blower is a centrifugal high-speed fluid machine. 4. The high speed fluid device according to claim 3, wherein the centrifugal fluid machine comprises an impeller. 5. The high-speed fluid device according to claim 2, wherein the blower is a positive displacement fluid machine. 6. The high-speed fluid device according to claim 5, wherein the positive displacement fluid machine is a roots type positive displacement fluid machine. 7. The high-speed fluid device according to claim 2, wherein the blower is an axial flow type fluid machine. 8. The high-speed fluid device according to claim 7, wherein the axial flow type fluid machine is a Lishorum type axial flow type fluid machine.