JPH08135752A - Power transmission device - Google Patents

Abstract

PURPOSE: To construct an overload torque limiter mechanism with torque variation absorbing function in the power transmission device of a compressor for automotive air conditioner. CONSTITUTION: In the normal operation of a compressor 4, a rotating force from an engine is transmitted to the rotating shaft of the compressor 4 through an elastic ring body 7 comprising a pulley 1, a rotor 2, a pin 6, and a rubber and hubs 11 and 9 so as to operate the compressor 4. In this case, the elastic ring body 7 absorbs torque variation. On the other hand, when the compressor is overloaded as in locked condition, the elastic ring body 7 deforms elastically, penetrates through a clearance in a holding member 13, and cuts off power transmission.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission device having a function of a torque limiter at the time of abnormality, and is suitable as a power transmission device for driving a compressor of a refrigeration cycle of an automobile air conditioner.

[0002]

2. Description of the Related Art Conventionally, as a power transmission device having the function of a torque limiter of this kind, the Japanese Utility Model Publication No. 6-14104.
In the device described in this publication, a drive-side rotating member that receives a rotational force from an automobile engine and a driven-side rotating member that is connected to a rotating shaft of a compressor are provided. An engaging mechanism that combines a drive lever made of a rigid body and an elastic member made of a leaf spring is interposed.

When a torque of a predetermined value or more is applied to the engagement mechanism due to a seizure failure of the compressor, the leaf spring is elastically deformed by the pressing force applied from the drive lever to the leaf spring, and the drive lever moves. By rotating about the rotation center provided at the intermediate position, the engagement state between the drive lever and the leaf spring is released, and the connection between the drive side rotation member and the driven side rotation member is cut off. I am trying to do it.

Thus, the power transmission from the engine to the compressor is shut off to prevent the engine power transmission system equipment from being damaged due to overload.

[0005]

However, in the above-mentioned conventional device, since the engaging mechanism using the leaf spring is used between the rotating members, the engaging mechanism itself absorbs the torque fluctuation of the compressor. Can not have the action of. Therefore, in order to absorb the torque fluctuation of the compressor, it is necessary to separately install a mechanism for absorbing the torque fluctuation, which causes a problem of high cost.

The present invention has been made in view of the above points,
An object of the present invention is to provide a power transmission device capable of exhibiting a torque limiter function at the time of overload by an engagement mechanism using a rubber elastic member having a torque fluctuation absorbing action.

[0007]

In order to achieve the above object, the present invention employs the following technical means. According to the first aspect of the invention, the drive side rotating member (1, 2) that rotates by receiving the rotational force from the rotary drive source and the driven side rotation connected to the rotating shaft (8) of the driven side device (4). Members (9, 11),
An elastic member (7, 70) made of rubber that is elastically deformable and arranged so as to connect the rotating members, and a holding member (13, 13) that holds the elastic member (7, 70).
0, 140), wherein the elastic member (7, 70) causes the holding member (13, 130, 140) to rotate when the rotational force is within a predetermined value.
Is integrally held by the two rotating members, and the rotating members are integrally connected to each other, and at the time of an overload in which the rotating force increases to a predetermined value or more,
Due to elastic deformation of the elastic member (7, 70) itself, the elastic member (7, 70) and the holding member (13, 130, 1).
40) is characterized in that the integral holding relationship with the rotating member is released to cut off the connection between the two rotating members.

According to a second aspect of the present invention, in the power transmission device according to the first aspect, the coupling mechanism is configured such that the elastic member (7) itself is elastic when the rotational force increases over a predetermined value. It is characterized in that the elastic member (7) is disengaged from the holding member (13) by the deformation so as to interrupt the connection between the both rotary members.

According to a third aspect of the present invention, in the power transmission device according to the second aspect, the elastic member (7) is formed in a ring shape, and the pin fixed to either one of the both rotary members. (6), the ring-shaped elastic member (7) is fitted and fixed to the pin (6), and the holding member (13) is a positive direction side of the rotation direction of the both rotary members and It is characterized by being configured as a cup-shaped member having a gap (A, B) on both sides in the negative direction.

According to a fourth aspect of the present invention, in the power transmission device according to the second or third aspect, the elastic member (7) is provided.
Is fixed to the drive side rotating member (1, 2),
The holding member (13) is the driven side rotation member (9, 1).
1) and is configured as a cup-shaped member having a gap (A, B) on both the positive direction side and the negative direction side of the rotation direction of the both rotary members, and the holding member (1
The gap (A, B) of 3) is characterized in that the gap (B) on the negative side is larger than the gap (A) on the positive side in the rotation direction. .

According to a fifth aspect of the present invention, in the power transmission device according to the second or third aspect, the elastic member (7) is provided.
Is fixed to the driven side rotation member (9, 11), the holding member (13) is fixed to the drive side rotation member (1, 2), and the rotation direction of both rotation members is positive. It is configured as a cup-shaped member having a gap (A, B) on both the direction side and the negative side, and the gap (A, B) of the holding member (13) is a positive direction of the rotation direction. It is characterized in that the gap (B) on the negative side is smaller than the gap (A) on the side.

According to a sixth aspect of the present invention, in the power transmission device according to any one of the third to fifth aspects, in the holding member (13) made of the cup-shaped member, the gaps (A, B) are provided. Among them, side walls (13e, 13f) having an arc shape are formed in a gap portion on the side where the elastic member (7) separates from the holding member (13) at the time of the overload. .

According to a seventh aspect of the invention, in the electromagnetic clutch according to the first aspect, the elastic member (70) includes the driven side rotating member (9, 11) and the drive side rotating member (1, 2). The holding member (130, 140) is concentric with the driven side rotating member (9, 11) and the drive side rotating member (1, 2). And the elastic member (7
0) is formed in a substantially cylindrical shape having a diameter different from that of the elastic member (70) and the holding members (130, 14).
0) and 0) are pressed against each other in the rotational direction to form the connecting mechanism, and the elastic member (70) is provided at the time of overload in which the rotational force increases to a predetermined value or more.
Elastically deforming the surface of the elastic member to the holding member (1
30, 140) slide, and the driven side rotation member (9,
11) and the drive side rotating member (1, 2) are configured to be disconnected from each other.

According to an eighth aspect of the present invention, in the electromagnetic clutch according to the seventh aspect, the driven side rotating member (9, 1).
1) and a substantially cylindrical first holding piece (130) arranged concentrically with the driving side rotating member (1, 2) and coupled to the driven side rotating member (9, 11); A substantially cylindrical second holding piece (which is coupled to the drive side rotating member (1, 2) and is concentrically arranged on the inner peripheral side of the first holding piece (130) with a predetermined gap therebetween. 140) and the holding member is constituted, and the substantially cylindrical elastic member (70) is locked in the rotational direction between the first holding piece (130) and the second holding piece. It is characterized by being crimped while being pressed.

According to a ninth aspect of the invention, in the electromagnetic clutch according to the eighth aspect, the first holding piece (130).
At least one of the second holding piece (140) and the locking shape portion (130A, 130B, 140A, 1) for increasing the locking force in the rotational direction with the elastic member (70).
40B) is formed, and the elastic member (70) also has locking shape parts (70A, 70) corresponding to the locking shape part.
B) is formed.

According to a tenth aspect of the present invention, in the electromagnetic clutch according to the ninth aspect, the engaging shape portions are a plurality of convex portions (130A, 1A) alternately and repeatedly formed in the rotational direction.
40A, 70A) and recesses (130B, 140B, 70)
It is characterized in that it is composed of B) and. Claim 1
In the invention described in claim 1, in the power transmission device according to any one of claims 1 to 10, the drive-side rotating member (1, 2) is configured to rotate by receiving a rotational force from an automobile engine. The driven device is a compressor (4) of a refrigeration cycle of an automobile air conditioner, and the compressor (4) is configured as a continuous variable capacity type without a clutch mechanism. Characterize.

The reference numerals in parentheses of the above means indicate the correspondence with the concrete means described in the embodiments described later.

[0018]

According to the invention described in claims 1 to 11, since it has the above-mentioned technical means, at the time of overload when the rotational force from the drive source rises to a predetermined value or more, the elastic member (7 , 70) elastic deformation of the elastic member (7, 7)
0) and the holding members (13, 130, 140) are released, the power transmission between the drive source and the driven-side device (4) is cut off, and the torque limiter at the time of overload. The function can be surely exhibited, whereby damage to various devices due to continuation of overload operation can be prevented.

Moreover, since the mechanism for exerting the torque limiter function is constituted by the combination of the elastic members (7, 70) made of rubber and the holding members (13, 130, 140), the impact absorption of rubber is absorbed. By utilizing the characteristics, it is possible to satisfactorily absorb the torque fluctuation of the driven side device such as the compressor. In addition to the above function and effect, in the invention according to claim 3, the elastic member (7) is formed in a ring shape, and the pin (6) is fixed to either one of the both rotating members. )
The ring-shaped elastic member (7) is fitted and fixed to the holding member (13), and the holding member (13) has a gap (A, B) on both the positive and negative sides of the rotating members. Since it is configured as a cup-shaped member, the elastic member (7) can be easily fixed to the pin (6) and the elastic member (7) and the holding member (13) can be easily assembled.

According to the sixth aspect of the invention, the elastic member (7) is held by the elastic member (7) during the overload in the both gaps (A, B) of the holding member (13) made of a cup-shaped member. Since the side wall portions (13e, 13f) having an arc shape are formed in the gap portion on the more detached side, the elastic member (7) is held by the side wall portions (13e, 13f) having the arc shape at the time of overload. It can be smoothly separated from the member (13), and the rubber surface of the elastic member can be prevented from being damaged.

Further, in the invention described in claims 7 to 10, a substantially cylindrical elastic member (concentric with the driven side rotating member (9, 11) and the driving side rotating member (1, 2)) is provided. 70) and a holding member (130, 14) also having a substantially cylindrical shape.
0), the substantially cylindrical elastic member (70) and the holding members (130, 140) are crimped while being locked in the rotational direction, so that the connecting mechanism is configured. According to the invention of Item 3, the armature (11, 1)
1A, 11B), the structure of the coupling mechanism can be simplified and the cost can be reduced as compared with the case where the pin (12) is fixed.

[0022]

Embodiments of the present invention will be described below with reference to the drawings. (First Embodiment) In FIGS. 1 and 2, reference numeral 1 denotes a driving pulley, which is rotated by receiving a rotational force from an automobile engine via a belt (not shown). This pulley 1 is a pulley portion 1a having a multiple V groove with which a multiple V belt is engaged.
Are integrally formed and are made of iron-based metal.

Reference numeral 2 denotes a drive-side rotor formed in a double ring shape having a U-shaped cross section, which is made of iron-based metal.
It is integrally joined to the pulley 1 by a joining means such as welding. A bearing 3 is arranged on the inner peripheral portion of the rotor 2, and the rotor 3 is rotatably supported by the bearing 3 on the cylindrical protrusion 5 a of the front housing 5 of the compressor 4.

Reference numeral 6 denotes a pin made of an iron-based metal, which is press-fitted and fixed in a hole 2b formed in a plurality of places (three places in this example) in the double ring-shaped connecting portion 2a of the rotor 2. An elastic ring body 7 made of rubber is fitted and fixed to the pin 6. The plurality of elastic ring bodies 7 and the pins 6 are arranged on the same circumference X centered on the center of the rotor 2 as shown in FIG.

As the material of the elastic ring body 7, rubber is used which exhibits excellent characteristics in terms of torque transmission and torque fluctuation absorption in the operating environment temperature range (-30 ° C to 120 °) of the automobile. Preferably, specifically,
Chlorinated butyl rubber, acrylonitrile butadiene rubber,
Rubber such as ethylene propylene rubber is preferred. 8 is a compressor 4
The rotary shaft 9 is a first hub, which is made of ferrous metal and is formed into a cylindrical shape having a flange portion 9a. The first hub 9 is screwed and fixed to the rotary shaft 8 with bolts 10 and the like.

That is, a screw hole 8a is formed in the central portion of the rotary shaft 8, and the rotary shaft 8 has a spline 8b on the outer peripheral portion thereof, and the inner peripheral surface of the first hub 9 is formed by the spline 8b. It has a non-rotating fit to the surface. Then, by screwing the threaded portion of the bolt 10 into the threaded hole 8a, the annular projection 9b on the inner peripheral portion of the first hub 9 is inserted between the tip of the rotary shaft 8 and the axial dimension adjusting shim 9c. It is designed to be sandwiched between. As a result, the first hub 9
And the rotary shaft 8 are integrally connected.

Reference numeral 11 denotes a second hub, which is formed of a ferrous metal into a ring-shaped plate shape and is integrally connected to the flange portion 9a of the first hub 9 at a plurality of locations by rivets 12. . Reference numeral 13 denotes a holding member for the elastic ring body 7, which is made of iron-based metal (for example, cold rolled steel plate SPCC) and has a cup-shaped cross section, and is integrally joined to the second hub 11 by a joining means such as welding. Has been done. In this holding member 13,
As shown in FIG. 2, holding pieces 13a and 13b extending on both inner and outer peripheral sides of the elastic ring body 7 are integrally formed by press working.

Then, the holding pieces 13a, 1 of the holding member 13
Between 3b, gaps A and B are set in both the positive direction and the negative direction with respect to the rotation direction R of the rotor 2, that is, the elastic ring body 7. The gap A in the positive direction of rotation is set smaller than the outer diameter of the elastic ring body 7 by a predetermined amount, while the gap B in the negative direction of rotation is set larger than the outer diameter of the elastic ring body 7 by a predetermined amount. . Therefore, the elastic ring body 7 can smoothly enter the negative direction gap B on the inlet side with respect to the rotation direction R, while the elastic ring body 7 cannot move in the rotational direction R on the positive direction gap A on the outlet side. Arrested,
Thereby, the elastic ring body 7 is integrally held by the holding member 13.

FIG. 3 shows an accessory drive system for an automobile engine. Reference numeral 14 is a crank pulley of the automobile engine. The rotation of the crank pulley 14 is passed through a belt 15 to a pulley 1 of a power transmission device for a compressor. It is designed to be transmitted to. Reference numeral 16 is a drive pulley of a water pump for circulating cooling water of an engine cooling device, 17 is a drive pulley of a battery charging generator (alternator), and 18 is a drive pulley of a hydraulic pump of a power steering device. ~ 18 is also the compressor drive pulley 1
At the same time, the belt 15 receives a rotational force and rotates.

Reference numerals 19, 20, and 21 are idle pulleys for applying a predetermined tension to the belt 15. Although a concrete structure of the compressor 4 is not shown in FIG. 1, the compressor 4 is generally known as a continuous variable capacity type, for example, a reciprocating type such as a swash plate type or a wobble type. The stroke of the dynamic piston is changed by changing the inclination angle of the swash plate of the piston drive mechanism to continuously change the compressor discharge capacity between 0% and 100%.

Such a continuously variable capacity type compressor 4
By using, the compressor 4 does not need to be equipped with an electromagnetic clutch for connecting and disconnecting power transmission. Next, the operation of the first embodiment having the above structure will be described. First, the normal operation of the compressor 4 will be described. The rotation of the crank pulley 14 of the automobile engine is transmitted to the pulley 1 by the belt 15 and the rotor 2 and the rotor 2 are integrated with the pulley 1.
The pin 6 and the elastic ring body 7 rotate.

Since the outer diameter of the elastic ring body 7 is larger than the gap A in the positive direction of the rotation of the cup-shaped holding member 13, it is held in the holding member 13. Therefore, since the elastic ring body 7 and the holding member 13 are integrally coupled in the rotation direction R, the pulley 1 is attached to the rotary shaft 8 of the compressor 4 via the first and second hubs 9 and 11. Is transmitted, and the compressor 4 operates.

Here, during normal operation of the compressor 4, since the elastic ring body 7 made of rubber absorbs the torsional vibration due to the operation of the compressor 4, the load torque of about 20 Nm is normally applied to the elastic ring body 7. However, at that time, the elastic ring body 7 causes only a small deformation at the above-mentioned load torque. The size of the gap A in the positive direction of rotation is set so that the elastic ring body 7 is held in the holding member 13 by this small deformation, so that the elastic ring body 7 is outside the holding member 13. Will not be released to. FIG.
(A) shows a small deformation state of the elastic ring body 7 in this load torque application state. The broken line shows the initial state before the load torque is applied to the elastic ring body 7.

Therefore, there is no problem in power transmission from the drive pulley 1 to the rotary shaft 8 of the compressor 4. Moreover, by interposing the elastic ring body 7 made of rubber in the power transmission system to the compressor 4, the torque fluctuation absorbing effect during normal operation of the compressor 4 can be satisfactorily exhibited. FIG. 5 shows a case I using a rubber elastic ring body 7 and a case II using a conventional leaf spring.
The torque fluctuation absorption effect is shown by comparing with. The horizontal axis of FIG. 5 is the rotation speed of the compressor 4, and the vertical axis is one-sided amplitude torque with respect to the average value of the load torque fluctuation width generated on the compressor rotation shaft (in other words, a torque of 1/2 of the load torque fluctuation width). ).

As can be seen from FIG. 5, in the case I according to the present invention, the peak of the torque shifts to a lower rotational speed range than that of the prior art II, and the peak value can be greatly reduced.
The effect of reducing the vibration of the compressor can be exhibited. On the other hand, when the compressor 4 has a seizure failure or the like and the rotating shaft 8 is locked, an excessive load torque is applied to the elastic ring body 7,
The elastic ring body 7 undergoes large deformation as shown in FIG. 4 (b), gradually slips out of the gap A of the holding member 13, and finally reaches the outside of the holding member 13 as shown in FIG. 4 (c). Then, the elastic ring body 7 and the holding member 13 are disconnected from each other, and the connection state between the elastic ring body 7 and the holding member 13 is blocked.

However, since the next holding member 13 is positioned at regular intervals (every 120 degrees of rotation angle in this example) in the rotation direction of the elastic ring body 7, the elastic ring body 7 is held next time. Move toward member 13. Since the gap B in the negative direction of rotation (inlet side) is set larger than the gap A in the positive direction of rotation (outlet side), the elastic ring body 7 can easily enter the holding member 13. become.

The movement of the elastic ring body 7 is continued until it is worn or damaged. Therefore, when the compressor 4 is temporarily locked due to a slight cause, the elastic ring body 7 and the holding member 13 can be automatically returned to the normal coupling state before the elastic ring body 7 is damaged, The machine 4 returns to the normal operation state. On the contrary, when the compressor 4 is continuously locked due to a serious failure such as seizure, the elastic ring body 7 is damaged, power transmission to the compressor 4 is completely cut off, and the torque limiter is completely cut off. Fulfill the function of.
Therefore, in the accessory drive system for the engine shown in FIG. 3, damage to the belt 15 and other accessory (1
It is possible to prevent the occurrence of serious failure such as inoperability of 6, 17, 18). (Second Embodiment) As shown in FIG. 6, among the holding pieces 13a, 13b of the holding member 13 of the elastic ring body 7, arcuate portions (corner R) 13c, 13d are provided on the side of the gap A in the positive direction of rotation. The side wall portions 13e and 13f having the are formed. Arc portions (corner R) 13c, 13d are provided on the side wall portions 13e, 13f.
By providing the elastic ring body 7 when the elastic ring body 7 slips out of the gap A, the elastic ring body 7 can move smoothly, and the side wall portions 13e and 13f can be elastically deformed outward from each other. Scratch is less likely to occur.

Since the side wall portions 13e and 13f can be elastically deformed outwardly, the degree of freedom in designing the dimension of the clearance A is increased. (Third Embodiment) As shown in FIGS. 7 and 8, a cup-shaped holding member 13 is fixed to a rotor 2 which is a driving side rotating member by a joining means such as welding, while a pin 6 is attached to a second hub 11. The pin 6 is press-fitted and fixed, and the elastic ring body 7 is fitted and fixed to the pin 6.

In the third embodiment, contrary to the first and second embodiments, the rotational force is transmitted from the cup-shaped holding member 13 to the elastic ring body 7. Therefore, in the holding member 13, contrary to the first and second embodiments, the gap A is formed on the negative side in the rotation direction R and the gap B is formed on the positive side in the rotation direction R. Even with such a configuration, the torque fluctuation absorption during normal operation and the torque limiter function during overload can be exhibited well.

9 and 10 show an example of a continuously variable displacement type compressor 4 which does not require a clutch for power transmission and disconnection, and 401 is a rotary shaft which rotates by receiving driving force from an engine. , Which corresponds to the rotary shaft 8 in FIG. The rotating shaft 401 is rotatably supported by the housing via bearings 402 and 403. The rotary shaft 401 has
A swash plate 404 is attached so that its inclination angle can be changed. That is, the rotation center position of the swash plate 404 is rotatable by the spherical support portion 405, and
By fitting the flat width portion 407 of the rotary shaft 401 into the groove 406 formed on the fourth side, the rotation of the rotary shaft 401 is transmitted to the swash plate 404.

Further, the swash plate 404 has a pin 408 and a groove 4
The pin 408 is fixed via the pin 06 and moves in the long groove 409 formed in the width across flats 407 of the rotary shaft 401, whereby the inclination angle of the swash plate 404 is changed. The swash plate 404 is connected to the piston 411 via the shoe 410, and the piston 411 is reciprocally slid in the cylinder 412 due to the swinging motion of the swash plate 404. In the suction process in which the working chamber 413 expands in volume as the piston 411 slides back and forth, the suction valve 414 opens and the refrigerant is sucked from the suction chamber 415 to the working chamber 413 side. On the other hand, in the compression process in which the volume of the working chamber 413 decreases as the piston 411 moves, the refrigerant is discharged to the discharge chamber 417 via the discharge valve 416. Inhalation chamber 4
Reference numeral 15 communicates with the suction port 418 via the suction passage in the compressor 4, and the low-temperature low-pressure refrigerant sucked from the evaporator of the refrigeration cycle (not shown) is supplied. On the other hand, the discharge chamber 417 communicates with the discharge port 419 through the discharge passage in the compressor 4, and the refrigerant is discharged from the discharge port 419 to the condenser side of the refrigeration cycle.

The discharge volume of this compressor 4 is the piston 41
The number of reciprocating strokes of 1 is variably controlled, so that it continuously changes. The amount of reciprocal stroll of the piston 411 is changed by changing the inclination angle of the swash plate 404. This change in the inclination angle is performed by interlocking the displacement of the swash plate 404 with the rotation center position while keeping the top dead center position on the right side in FIG. 9 constant.

In this example, the above control is performed by using the spool 420 to displace the spherical support portion 405 along the rotary shaft 401 in the horizontal direction in the drawing. The positional displacement of the spool 420 is performed by forming the spool 420 on the back surface and adjusting the pressure in the control pressure chamber 421. That is, the spool 42
One side of 0 is the suction chamber 415, and the suction pressure is always applied. On the other hand, the pressure regulated by the control valve 422 is supplied to the control pressure chamber 421, and the differential pressure between the pressure inside the control pressure chamber 421 and the pressure inside the suction chamber 415 is applied to the spool valve 420. . The pressure applied to the spool valve 420 and the piston 41
The tilt angle of the swash plate 404 is controlled to a position where it is balanced by the compression reaction force with 1.

The control valve 422 regulates the discharge pressure supplied from the discharge chamber 417 through the high-pressure introduction passage 423 and the low pressure (suction pressure) supplied from the low-pressure introduction passage 424 so that a constant control pressure is maintained. Control passage 4 from passage 425
21. In this example, an electric control type that switches and opens both the passages 423 and 424 by an electric signal is used.

As the control valve 422, it is also possible to use a structure in which a pressure responsive member such as a diaphragm is used and the control pressure is adjusted by a pure mechanical mechanism. Figure 9
Shows a state in which a predetermined pressure is supplied to the control pressure chamber 421 and the spool valve 420 is moved to the left side in the drawing by a predetermined amount. The discharge capacity of the compressor 4 is further reduced from the state shown in FIG. 9 in the state shown in FIG. In this state, the suction pressure is supplied to the control pressure chamber 421.
As a result, the spool valve 420 is displaced to the right side in the figure by the maximum amount due to the compression reaction force of the piston 411 and the like. As a result, the rotation center position of the swash plate 404 is also displaced to the right side in the drawing, and each swash plate 4
The tilt angle of 04 is also displaced in a direction approaching a right angle with respect to the rotation axis 401.

As is clear from FIG. 10, in this state,
The swing amount of the swash plate 404 is also small, and therefore, the reciprocating stroke of the piston 411 is minimized, and the compressor 4 is substantially
It is possible to set the discharge capacity of the above to zero. In addition, in each of the above-described embodiments, three elastic ring bodies 7 and three holding members 13 are provided, but this number is merely an example, and it goes without saying that the number may be increased or decreased as necessary.

Further, the plurality of holding members 13 can be integrally formed from a metal plate such as iron. Further, as the elastic member, a rubber elastic member having various shapes such as a rectangular shape and a disk shape can be used without using the illustrated ring body 7. In this case, the elastic member may be directly adhered and fixed to the driving-side or driven-side rotating member without using a pin.

In addition, the holding member 13 in the above embodiment is
The elastic ring body 7 is formed into a cup-like shape having holding pieces 13a and 13b on both inner and outer circumferences, but the shape is not limited to this. Only one of the inner and outer circumferences of the holding pieces 13a and 13b is formed. However, the functions of torque transmission and torque limiter can be exhibited. (Fourth Embodiment) FIGS. 11 to 14 show a fourth embodiment. A rotor 2 is formed in a cylindrical shape, and a pulley 1 is integrally joined to the outer peripheral surface of the cylinder by welding or the like. A substantially cylindrical first holding piece 130 is arranged concentrically with the pulley 1, the rotor 2, and the first hub 9. In this example, the first holding piece 130 is made of iron-based metal and is integrally molded with the second hub 11 by bending the outer peripheral side of the second hub 11 into an L shape by pressing.

The cylindrical shape of the first holding piece 130 is formed so as to extend parallel to the axial direction of the rotating shaft 8, and the cylindrical portion thereof has a plurality of convex portions alternately formed repeatedly in the rotating direction. A petal-shaped locking shape portion (see FIG. 11) including a portion 130A and a concave portion 130B is formed. On the inner peripheral side of the first holding piece 130, a second holding piece 140 having a substantially cylindrical shape is concentrically arranged with a predetermined interval. The second holding piece 190 is also formed by pressing an iron-based metal, and the cylindrical portion is composed of a plurality of convex portions 140A and concave portions 140B which are alternately and repeatedly formed in the rotational direction. A petal-shaped locking shape portion (see FIGS. 11 and 13) is formed.

Further, an outer peripheral bent portion 140C bent to the outer peripheral side is formed on one end side (the right side in FIG. 12) in the axial direction of the cylindrical portion of the second holding piece 140. As shown in FIG. 13, bulged portions 140D bulged toward the pulley 1 are integrally formed with the outer peripheral bent portion 140C at a plurality of locations (four locations in this example) where the rivets 120 are arranged, as shown in FIG. .

An insertion hole 140E for the rivet 120 is formed in the bulging portion 140D, and the insertion hole 140E is formed.
By inserting the rivet 120 into the
The holding piece 140 is integrally connected to the pulley 1 by the rivet 120. On the other hand, in this example, the elastic member 70 is the same as in FIG.
1. As shown in FIG. 14, it is formed of rubber into a substantially cylindrical shape, and the elastic member 70 also has the first and second holding pieces 13 formed therein.
A petal-shaped engaging shape portion corresponding to the engaging shape portions 0 and 140 is formed. That is, on the circumferential surface of the cylinder of the elastic member 70, a petal-shaped engagement shape portion including a plurality of convex portions 70A and concave portions 70B that are alternately and repeatedly formed in the rotation direction is formed.

The thickness of the elastic member 70 in the radial direction is set to be slightly larger than the distance between the first and second holding pieces 130 and 140, so that the elastic member 70 is set to the first and second holding pieces. It is inserted so as to be crimped between 130 and 140. In this fitted state, as shown in FIG. 11, the plurality of convex portions 70A and concave portions 70B of the elastic member 70, and the first and second concave portions 70A
Of the holding pieces 130, 140 of the plurality of convex portions 130A, 140
Since the A and the concave portions 130B and 140B are fitted and locked with each other, the elastic member 70 and the first and second holding pieces 13 are formed.
The locking force in the rotational direction between 0 and 140 can be increased.

In FIG. 11, for convenience, the elastic member 70 is used.
The part is hatched so that its shape is clearly shown. In addition, the second hub 11 that is integrally continuous with the first holding piece 130 and the outer circumferential bent portion 140C of the second holding piece 140 presses both ends of the elastic member 70 in the axial direction, and the elastic member 70. It is designed to prevent the axial movement of the.

With the above configuration, the first and second holding pieces 1
Between 30 and 140 (in other words, between the pulley 1 and the rotor 2 side and the hubs 9 and 11) can be integrally connected via the elastic member 70. As the assembling method in the fourth embodiment, the assembling body including the pulley 1, the rotor 2, the bearing 3, and the second holding piece 140 is first assembled in the front housing 5 of the compressor 4, and then the second assembly is carried out. Holding piece 140
The elastic member 70 is assembled on top. Next, this elastic member 70
Further, the assembly body including the first and second hubs 9 and 11 and the first holding piece 130 may be assembled to the rotary shaft 8 of the compressor 4, and finally the bolt 10 may be tightened.

Since the fourth embodiment is constructed as described above, during normal operation of the compressor 4, the rotation of the pulley 1 and the rotor 2 is controlled by the second holding piece 140, the elastic member 70, and the first member. It is transmitted to the hubs 11 and 9 via the holding piece 130,
The rotating shaft 8 of the compressor 4 can be rotated, and the elastic member 70 can serve to absorb the torque fluctuation of the compressor 4.

On the other hand, when the compressor 4 is locked, an excessive load torque is applied to the connecting mechanism composed of the first holding piece 130, the elastic member 70, and the second holding piece 140, so that the elastic member 70 is elastically deformed. The elastic member 70 and the outer peripheral surface of the second holding piece 140 that are raised and acted on by the driving force from the engine.
The locked state with the inner peripheral surface of is released. As a result, the outer peripheral surface of the second holding piece 140 slides on the inner peripheral surface of the elastic member 70, and the connection state between the second holding piece 140 and the elastic member 70 is cut off, so that the compressor is The power transmission to 4 is cut off.

Further, in the fourth embodiment, as clearly shown in FIG. 13, the outer peripheral bent portion 140C of the second holding piece 140 regulates the axial end portion of the elastic member 70, and the outer peripheral bent portion. Since the bulging portion 140D that bulges (projects) from 140C to the pulley 1 side is the fixing surface of the rivet 120, the axial end of the elastic member 70 can be separated from the fixing surface of the rivet 120.

Therefore, foreign matter (oil or the like) from the compressor 4 or the like can be prevented from adhering to the elastic member 70. (Fifth Embodiment) FIGS. 15 and 16 show a fifth embodiment, in which the first holding piece 130 integrally formed with the second hub 11 is opposed to the axial end of the elastic member 70. A plurality of (8 in this example) swelling portions 13 are provided in the circumferential direction
0C is integrally molded at equal intervals. This bulge 130
Since C bulges outward in the axial direction, a space portion 130D is formed inside the bulging portion 130C between the bulging portion 130C and the axial end portion of the elastic member 70.

When the bolt 10 is tightened when the device of the fifth embodiment is assembled, the elastic member 70 is compressed in the axial direction. This compression is necessary to absorb the dimensional tolerances of the assembled parts. However, if the elastic member 70 has a large compression allowance, the characteristics of the elastic member 70 are seen from both the torque fluctuation absorbing function and the torque limiter function. It may deviate from the required characteristics.

However, in the fifth embodiment, the bulging portion 13 is
Since the space portion 130D is formed by 0C, the compression margin volume of the elastic member 70 can be released into this space portion 130D, so that the elastic member 70 is not affected by the variation in the dimensional tolerance of the assembled parts. The characteristics of can be reliably set according to the intended design. (Sixth Embodiment) FIG. 17 shows a sixth embodiment in which the shape of the elastic member 70 in the above-mentioned fourth embodiment is modified. An escape groove 70C is provided at an intermediate position of the convex portion 70A of the elastic member 70. The convex portion 70A of the elastic member 70 is easily elastically deformed when the compressor 4 is overloaded, such as when the compressor 4 is locked.

By selecting the size and shape of the escape groove 70C, the operating torque when the torque transmission is interrupted can be easily adjusted, and the degree of freedom in design is increased. Incidentally, the above fourth to sixth
In the embodiment, the elastic member 70 is fitted between the first and second holding pieces 130 and 140 and pressure-bonded, but
The elastic member 70 may be pressure-bonded to only one of the first and second holding pieces 130 and 140 and adhered to the other. In this case, the convex portion 70A and the concave portion 70B are provided only on the surface of the elastic member 70 on which the elastic member 70 is to be pressed, and
Of 0, the surface to be bonded may have a circular shape with no irregularities. Similarly, of the first and second holding pieces 130 and 140, the holding piece on the side to be bonded may have a circular shape having no uneven portion.

[Brief description of drawings]

FIG. 1 is a sectional view of an essential part of a first embodiment of the present invention.

FIG. 2 is a front view of a first embodiment in which a main part of FIG. 1 is shown in a sectional view, and shows a state before being assembled to a compressor 4 by a bolt 10.

FIG. 3 is an accessory drive system diagram of an automobile engine to which the first embodiment is applied.

4 (a), (b) and (c) are enlarged views of a main part showing the operation behavior of the elastic ring body in the first embodiment.

FIG. 5 is a characteristic diagram showing a torque fluctuation absorbing effect according to the present invention.

FIG. 6 is a cross-sectional front view of essential parts showing a second embodiment of the present invention.

FIG. 7 is a cross-sectional view of essential parts of a third embodiment of the present invention.

8 is a front view of a third embodiment in which a section BB of FIG. 7 is shown in a sectional view, and shows a state before being assembled to the compressor 4 by the bolt 10. FIG.

FIG. 9 is a cross-sectional view showing an example of a continuously variable capacity type compressor having no clutch mechanism used in the present invention.

10 is a sectional view showing a small capacity setting state of the continuously variable capacity type compressor shown in FIG.

FIG. 11 is a front view of the fourth embodiment of the present invention.

12 is a cross-sectional view taken along the line AOA of FIG.

13A is a front view of a single second holding piece in the fourth embodiment, and FIG. 13B is a sectional view taken along line AAA of FIG. 13A.

FIG. 14 is a front view of a single elastic member according to a fourth embodiment.

FIG. 15 is a front view of the fifth embodiment of the present invention.

16 is a cross-sectional view taken along the line AA in FIG.

FIG. 17 is a front view of a single elastic member showing a sixth embodiment of the present invention.

[Explanation of symbols]

1, 2 ... Pulleys, rotors (rotating members on the driving side), 4 ... Compressors, 6 ... Pins, 7, 70 ... Elastic ring bodies (elastic members),
9, 11 ... First and second hubs (driven side rotating members), 1
3, 130, 140 ... Holding member, 13e, 13f ... Side wall portion.

─────────────────────────────────────────────────── ─── Continuation of the front page (51) Int.Cl. ⁶ Identification code Internal reference number FI Technical display location F16D 7/02 H (72) Inventor Kiyomi Okuda 1-1, Showa-cho, Kariya city, Aichi prefecture Nidec Incorporated (72) Inventor Junichi Toyama 1-1, Showa-cho, Kariya city, Aichi Nihon Denso Co., Ltd.

Claims (11)

[Claims] 1. A drive-side rotating member that receives a rotational force from a rotary drive source to rotate, a driven-side rotating member that is connected to a rotating shaft of a driven-side device, and a connection between the both rotating members. A rubber elastic member that is disposed and elastically deformable, and a connecting mechanism that includes a holding member that holds the elastic member are provided. When the rotating force is within a predetermined value,
When the elastic member is integrally held by the holding member and integrally connects the rotating members, the elastic member is elastically deformed by an elastic deformation of the elastic member itself at the time of an overload in which the rotational force increases to a predetermined value or more. The power transmission device is configured to release the integral holding relationship between the holding member and the holding member to cut off the connection between the both rotating members. 2. The connecting mechanism is configured such that, at the time of an overload in which the rotational force rises to a predetermined value or more, the elastic member separates from the holding member due to elastic deformation of the elastic member itself, and the elastic member is separated from the rotating member. The power transmission device according to claim 1, wherein the power transmission device is configured to cut off the connection of the two. 3. The elastic member is formed in a ring shape, and has a pin fixed to either one of the both rotary members, and the ring-shaped elastic member is fitted and fixed to this pin. The power transmission according to claim 2, wherein the holding member is configured as a cup-shaped member having a gap on both the positive direction side and the negative direction side of the rotation direction of the both rotary members. apparatus. 4. The elastic member is fixed to the drive-side rotating member, the holding member is fixed to the driven-side rotating member, and the positive and negative directions of rotation of the both rotating members are positive and negative. It is configured as a cup-shaped member having a gap on both sides, and the gap of the holding member is configured such that the gap on the negative side is larger than the gap on the positive side in the rotation direction. The power transmission device according to claim 2, wherein the power transmission device is provided. 5. The elastic member is fixed to the driven side rotating member, the holding member is fixed to the drive side rotating member, and the positive and negative directions of rotation of the both rotating members are positive and negative. It is configured as a cup-shaped member having a gap on both sides, and the gap of the holding member is configured such that the gap on the negative side is smaller than the gap on the positive side in the rotation direction. The power transmission device according to claim 2, wherein the power transmission device is provided. 6. In the holding member formed of the cup-shaped member, a side wall portion having an arc shape is formed in a gap portion of the both gaps on the side where the elastic member is separated from the holding member at the time of the overload. The power transmission device according to any one of claims 3 to 5, characterized in that: 7. The elastic member is formed in a substantially cylindrical shape concentrically arranged with the driven-side rotating member and the driving-side rotating member, and the holding member is provided with the driven-side rotating member and the driven-side rotating member. It is arranged concentrically with the drive-side rotating member and is formed into a substantially cylindrical shape having a diameter different from that of the elastic member. The substantially cylindrical elastic member and the holding member are crimped while being locked in the rotational direction. When the rotational force rises to a predetermined value or more, the elastic member is elastically deformed and the holding member slides on the elastic member surface so that the driven member is driven. The electromagnetic clutch according to claim 1, wherein the electromagnetic clutch is configured to cut off the connection between the side rotating member and the driving side rotating member. 8. A substantially cylindrical first holding piece arranged concentrically with the driven side rotating member and the driving side rotating member and coupled to the driven side rotating member, and the driving side rotating member. The holding member is composed of a second cylindrical holding piece that is coupled and is arranged concentrically on the inner peripheral side of the first holding piece with a predetermined gap therebetween. The cylindrical elastic member includes the first holding piece and the second holding piece.
The electromagnetic clutch according to claim 7, wherein the electromagnetic clutch is crimped while being locked in the rotational direction with the holding piece. 9. A locking shape portion is formed on at least one of the first holding piece and the second holding piece to enhance a locking force in a rotation direction with the elastic member, and 9. The electromagnetic clutch according to claim 8, wherein the elastic member also has a locking shape portion corresponding to the locking shape portion. 10. The electromagnetic clutch according to claim 9, wherein the locking shape portion is composed of a plurality of convex portions and concave portions that are alternately and repeatedly formed in the rotation direction. 11. The drive-side rotating member is configured to rotate by receiving a rotational force from an automobile engine, and the driven-side device is a compressor of a refrigeration cycle of an automobile air conditioner. The power transmission device according to claim 1, wherein the compressor is configured as a continuously variable capacity type without a clutch mechanism.