JP2008115939A - Power transmission mechanism of electromagnetic spring clutch type - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a power transmission mechanism of electromagnetic spring clutch type, which prevents an input-side rotor connected to an elastomer from makes a relative displacement axially with respect to an output-side rotor. <P>SOLUTION: An inner ring 38 constituting a hub 36 is provided with a plurality of engagement pieces 46, which are bent to be engaged respectively with the end faces 402 of an outer ring 40. The engagement pieces 46 engaged with the end faces 402 of the outer ring 40 elastically deform an elastic ring 39 so that the outer peripheral part 391 and the inner peripheral part 392 of the elastic ring 39 on the side of the outer ring 40 are displaced in the directions opposite to each other in the axial direction 181 of the rotary shaft 18. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to an electromagnetic spring clutch type power transmission mechanism that transmits a rotational driving force of a driving side rotating body to a driven side rotating body via a coil spring whose diameter is increased or decreased with the rotation of the driving side rotating body.

  This type of electromagnetic spring clutch type power transmission mechanism is disclosed in Patent Document 1, for example. When energization is performed on the exciting coil (solenoid), the armature is attracted to the input rotor (drive side rotating body), and the coil spring is wound (reduced diameter). The rotational driving force of the input rotor is transmitted to the hub (the driven-side rotating body) through the coiled coil spring. The hub includes a hub outer peripheral portion (input-side rotating body), a hub shaft portion (output-side rotating body), and a shock-absorbing elastic body connected to the hub outer peripheral portion and the hub shaft portion.

Since the hub outer peripheral portion is supported by the hub shaft portion via an elastic body, when vibration is applied from the outside, the hub outer peripheral portion tends to vibrate. In Patent Document 1, an elastic body stopper is provided on the spring cover and formed on the hub shaft so that the outer peripheral portion of the hub does not vibrate and strikes a peripheral member (spring cover or the like) to generate abnormal noise. An elastic body stopper is provided on the protrusion. The hub outer peripheral portion is between the spring cover side elastic body stopper and the protrusion side elastic body stopper.
JP 61-103017 A

  However, since the elastic stopper on the protruding part side is slightly separated from the outer periphery of the hub, the vibration of the outer peripheral part of the hub cannot be surely prevented, and the vibrating outer periphery of the hub hits the elastic body stop. Unable to prevent abnormal noise.

  An object of the present invention is to provide an electromagnetic spring clutch type power transmission mechanism in which an input-side rotator coupled to an elastic body is prevented from being displaced relative to an output-side rotator in the direction of a rotation axis.

  The present invention relates to a driving-side rotating body, an armature that is attracted to the driving-side rotating body by energizing a solenoid, and a state in which the driving-side rotating body rotates while the armature is attracted to the driving-side rotating body Then, the driven side rotation to which the rotational driving force of the driving side rotating body is transmitted via the coil spring whose diameter is enlarged or reduced with the rotation of the driving side rotating body and the coil spring whose diameter is increased or reduced An input-side rotating body that contacts the coil spring and obtains a rotational driving force from the driving-side rotating body, an output-side rotating body, the input-side rotating body, and the output The invention of claim 1 is directed to an electromagnetic spring clutch type power transmission mechanism that includes an elastic body that is coupled to a side rotating body and transmits a rotational driving force of the input side rotating body to the output side rotating body. The above At least one of the side rotator and the input side rotator includes preload applying means that rubs against the elastic body in the direction of the rotation axis of the driven side rotator and applies a preload. To do.

  Here, the pre-friction preload is a preload that causes elastic deformation in which a portion of the elastic body on the input side rotating body side and a portion of the elastic body on the output side rotating body side are displaced in opposite directions. Such a friction preload prevents displacement of the elastic body due to external vibration, and prevents the input-side rotating body from being displaced relative to the output-side rotating body in the direction of the rotation axis.

  In a preferred example, the preload applying means is an engaging piece formed on one of the output side rotating body and the input side rotating body, and the engaging piece elastically deforms the elastic body. In addition, it is engaged with the other corresponding to the one.

  The engaging piece formed on one of the output side rotating body and the input side rotating body elastically deforms the elastic body so as to rub against the elastic body and apply a preload. When the engaging piece is provided on the output side rotating body, the engagement target of the engaging piece is the input side rotating body, and when the engaging piece is provided on the input side rotating body, the engaging piece is engaged. The engagement target of the combined piece is the output side rotating body. Such an engagement relationship is simple in giving a preload by rubbing against the elastic body.

In a preferred example, the engagement piece is engaged with the other so as to be bent and elastically deform the elastic body.
When the engaging piece is not bent, the elastic body is in a natural state where it is not elastically deformed. When the engaging piece is bent, the elastic body is elastically deformed so as to be rubbed and given a preload. A configuration in which the elastic piece is elastically deformed by bending the engaging piece is a simple configuration in order to apply a preload to the elastic body.

  In a preferred example, the input-side rotator is a ring-shaped outer ring on the outer peripheral side of the output-side rotator, and the elastic body includes an inner periphery of the outer ring and an outer periphery of the output-side rotator. A ring-shaped rubber elastic ring interposed between the engagement piece, the engagement piece is provided on the outer peripheral side of the output-side rotation body, and the engagement piece is a radius of the output-side rotation body. The outer ring portion of the elastic ring is engaged with the end surface of the outer ring by bending from the inner side to the outer side in the direction, and the inner peripheral portion of the elastic ring on the output side rotating body side is the driven side. The rubbing preload is applied to the elastic ring so as to be relatively displaced in the direction of the rotation axis of the rotating body.

  When an impact ring torque is applied and the elastic ring breaks, the outer ring becomes free, but the engagement piece provided on the output side rotating body contributes to prevention of the outer ring from falling off.

In a preferred example, the output-side rotator has a cylindrical connecting cylinder part connected to the rubber elastic ring, and the engagement piece is integrally formed on an edge of the connecting cylinder part. .
The engaging piece is bent after forming the driven side rotating body, that is, after connecting the rubber elastic ring to the input side rotating body and the output side rotating body. When press-molding the output-side rotator, the engaging piece can be formed simultaneously with press-molding the output-side rotator.

  The present invention has an excellent effect that the input side rotating body connected to the elastic body can be prevented from being relatively displaced in the direction of the rotation axis with respect to the output side rotating body.

Hereinafter, a first embodiment in which the present invention is embodied in an electromagnetic spring clutch type power transmission mechanism used in a compressor will be described with reference to FIGS.
As shown in FIG. 1, a front housing 12 is connected to the front end of the cylinder block 11. A rear housing 13 is connected to the rear end of the cylinder block 11. The cylinder block 11, the front housing 12, and the rear housing 13 constitute an entire housing of the variable displacement compressor 10.

  A rotary shaft 18 is rotatably supported via radial bearings 19 and 20 on the front housing 12 and the cylinder block 11 forming the control pressure chamber 121. The rotating shaft 18 that protrudes outside from the control pressure chamber 121 obtains a rotational driving force from the vehicle engine E that is an external driving source via an electromagnetic spring clutch type power transmission mechanism 29.

  A rotary support 21 is fixed to the rotary shaft 18, and a swash plate 22 is supported so as to be slidable and tiltable in the axial direction of the rotary shaft 18. A guide pin 23 provided on the swash plate 22 is slidably fitted in a guide hole 211 formed in the rotary support 21. The swash plate 22 can be tilted in the direction of the rotation axis 181 of the rotation shaft 18 and can rotate integrally with the rotation shaft 18 by the linkage of the guide hole 211 and the guide pin 23. The tilt of the swash plate 22 is guided by the slide guide relationship between the guide hole 211 and the guide pin 23 and the slide support action of the rotary shaft 18.

  If the diameter center part of the swash plate 22 moves to the rotation support body 21 side, the inclination angle of the swash plate 22 increases. The maximum inclination angle of the swash plate 22 is regulated by the contact between the rotary support 21 and the swash plate 22. The swash plate 22 shown by the solid line in FIG. 1 is in the maximum tilt state, and the swash plate 22 shown by the chain line is in the minimum tilt state.

  Pistons 24 are accommodated in a plurality of cylinder bores 111 (only one is shown in the figure) penetrating the cylinder block 11. The rotational movement of the swash plate 22 is converted into the back-and-forth reciprocating movement of the piston 24 via the shoe 25, and the piston 24 reciprocates in the cylinder bore 111.

  A suction chamber 131 and a discharge chamber 132 are defined in the rear housing 13. The refrigerant in the suction chamber 131 which is the suction pressure region flows into the cylinder bore 111 by pushing the suction valve 15 away from the suction port 14 by the backward movement of the piston 24 (movement from the right side to the left side in FIG. 1). The gaseous refrigerant flowing into the cylinder bore 111 is discharged from the discharge port 16 to the discharge chamber 132 which is a discharge pressure region by pushing the discharge valve 17 away from the discharge port 16 by the forward movement of the piston 24 (movement from the left side to the right side in FIG. 1). Is done. The refrigerant discharged to the discharge chamber 132 returns to the suction chamber 131 via an external refrigerant circuit (not shown).

  An electromagnetic capacity control valve 26 is assembled to the rear housing 13. The capacity control valve 26 is interposed on a supply passage 27 that connects the discharge chamber 132 and the control pressure chamber 121. The valve opening degree of the capacity control valve 26 is adjusted according to the pressure of the suction chamber 131 and the duty ratio of energization to the solenoid (not shown) of the capacity control valve 26. When the valve hole of the capacity control valve 26 is closed, the refrigerant in the discharge chamber 132 is not sent to the control pressure chamber 121.

  The control pressure chamber 121 communicates with the suction chamber 131 via the discharge passage 28, and the refrigerant in the control pressure chamber 121 flows out to the suction chamber 131 via the discharge passage 28. As the valve opening of the capacity control valve 26 increases, the amount of refrigerant flowing from the discharge chamber 132 into the control pressure chamber 121 via the supply passage 27 increases, and the pressure in the control pressure chamber 121 increases. Therefore, the inclination angle of the swash plate 22 is reduced, and the discharge capacity is reduced. When the valve opening degree of the capacity control valve 26 decreases, the amount of refrigerant flowing from the discharge chamber 132 into the control pressure chamber 121 via the supply passage 27 decreases, and the pressure in the control pressure chamber 121 decreases. As a result, the inclination angle of the swash plate 22 increases and the discharge capacity increases.

Next, the configuration of the electromagnetic spring clutch type power transmission mechanism 29 will be described.
As shown in FIG. 1, a support cylinder portion 122 is integrally formed at the front end of the front housing 12, and a magnetic rotor 30 is rotatably supported on the outer periphery of the support cylinder portion 122 via a radial bearing 31. Has been. The rotor 30 serving as a drive-side rotator includes an annular base 301 connected to a radial bearing 31, an adsorption disk 302 perpendicular to the rotation shaft 18, a cylindrical belt winding portion 303, and a cylindrical transmission. Part 304. The rotor 30 obtains a rotational driving force from the vehicle engine E via a belt (not shown) wound around the belt winding portion 303. When the engine E is operating, the rotor 30 is supported by the support cylinder portion. Rotate around 122.

  A bobbin 33 is fixed to the front end of the front housing 12, and a solenoid 34 is accommodated in the bobbin 33. An accommodation groove 32 is formed between the base portion 301 and the belt winding portion 303, and a bobbin 33 and a solenoid 34 enter the accommodation groove 32.

  A spacer 35 is fitted to a portion of the rotating shaft 18 in the support cylinder portion 122, and a hub 36 is fixed to a tip portion of the rotating shaft 18. A hub 36 as a driven side rotating body includes a disk-shaped base 37 screwed to the tip of the rotary shaft 18, an inner ring 38 fixed to the front surface of the base 37 by a pin 47, and an outer periphery of the inner ring 38. An annular rubber elastic ring 39 connected and an outer ring 40 connected to the outer periphery of the elastic ring 39 are provided. The outer ring 40 as the input side rotating body is located at a position facing the suction disk 302 of the rotor 30. A coil spring 41 is disposed between the outer ring 40 and the transmission portion 304 of the rotor 30 so as to surround the outer ring 40. A latching recess 401 is formed on the outer periphery of the outer ring 40, and one end 411 of the coil spring 41 is latched on the latching recess 401.

  As shown in FIG. 2A, a ring-shaped armature 42 is disposed between the suction disk 302 of the rotor 30 and the outer ring 40. A disc spring 43 is interposed between the inner peripheral side of the armature 42 and the outer peripheral side of the base 37 of the rotor 30. The disc spring 43 biases the armature 42 from the suction disk 302 side to the inner ring 38 side. The armature 42 is located away from the outer ring 40. When the solenoid 34 is energized, the armature 42 is attracted to the suction disk 302 against the spring force of the disc spring 43, and the armature 42 rotates together with the rotor 30.

  A latching recess 421 is formed on the outer peripheral side of the armature 42, and the other end 412 of the coil spring 41 is latched on the latching recess 421. The winding direction of the coil spring 41 is a direction in which the front end 182 of the rotating shaft 18 is wound counterclockwise as viewed from the direction of the rotating axis 181 as it goes from the outer ring 40 side to the armature 42 side.

  When the armature 42 is not rotating, the coil spring 41 is not in contact with the inner peripheral surface 305 of the cylindrical transmission portion 304 as shown in FIG. When the solenoid 34 is energized and the armature 42 is attracted to the suction disk 302 as shown in FIG. 2A, the armature 42 rotates and the end of the coil spring 41 that is latched by the latching recess 421. The portion 412 is biased in the direction opposite to the winding direction of the coil spring 41. As a result, the coil diameter of the coil spring 41 is increased by the rotation of the suction disk 302. Due to this diameter expansion, the outer periphery of the coil spring 41 is pressed against the inner peripheral surface 305 of the transmission portion 304. Accordingly, the rotor 30, the coil spring 41, and the outer ring 40 are firmly coupled, and the rotational driving force of the rotor 30 is transmitted to the hub 36 via the coil spring 41. The rotational driving force transmitted to the hub 36 is transmitted directly from the base 37 to the rotary shaft 18 and from the base 37 via the spacer 35 to the rotary shaft 18.

  The inner ring 38 as an output side rotating body is connected to a disc portion 44 joined to the base 37, a cylindrical connecting tube portion 45 that is continuous with the outer periphery of the disc portion 44, and a front end edge 451 of the connecting tube portion 45. And a plurality of engagement pieces 46 (four in this embodiment as shown in FIG. 3). The front end side of the engagement piece 46 as the preload applying means is engaged with the end surface 402 of the outer ring 40. FIG. 2B shows the shape of the inner ring 38 when the inner ring 38 is formed by press working. In FIG. 2B, the elastic ring 39 as an elastic body is connected to the inner ring 38 and the outer ring 40 in a natural state where the elastic ring 39 is not elastically deformed.

  The engagement piece 46 in FIGS. 1 and 2A shows a state where the engagement piece 46 in FIG. 2B is bent from the inner side to the outer side in the radial direction of the inner ring 38. The engagement piece 46 that is bent in this manner and engaged with the end surface 402 of the outer ring 40 elastically deforms the rubber elastic ring 39. In other words, the outer peripheral portion 391 of the elastic ring 39 on the outer ring 40 side and the inner peripheral portion 392 of the elastic ring 39 on the inner ring 38 side are relative to each other in the direction of the rotation axis of the hub 36 (that is, the rotation axis 181 of the rotary shaft 18). A preload that elastically deforms the elastic ring 39 so as to be displaced is applied to the elastic ring 39 by the engagement of the engagement piece 46 and the outer ring 40. In the following, such a preload will be referred to as a frictional preload. The elastic ring 39 in FIG. 1 and FIG. 2A is elastically deformed by applying a pre-friction preload, and the elastic ring 39 in FIG. I am doing.

In the first embodiment, the following effects can be obtained.
(1) The elastic ring 39 elastically deformed by the friction preload is not deformed by external vibration. Therefore, the outer ring 40 is prevented from being displaced relative to the inner ring 38 in the direction of the rotation axis 181 of the hub 36, and contact between the outer ring 40 and the armature 42 is prevented.

  (2) The configuration in which the engagement piece 46 is engaged with the end surface 402 of the outer ring 40 and the elastic ring 39 is elastically deformed is simple in giving a frictional preload that greatly elastically deforms the elastic ring 39. is there.

  (3) When the engagement piece 46 is not bent, the elastic ring 39 is in a natural state in which it is not elastically deformed. When the engagement piece 46 is bent, the elastic ring 39 is rubbed and preloaded. It is elastically deformed. By adjusting the degree of bending of the engagement piece 46, it is possible to adjust the magnitude of the pre-load preload applied to the elastic ring 39, and hence the magnitude of the elastic deformation of the elastic ring 39. By performing such adjustment, it is possible to reliably apply a friction preload so that the elastic ring 39 is not deformed by external vibration.

  (4) When the elastic ring 39 breaks due to an impact load torque, the outer ring 40 loses the support of the inner ring 38 and becomes free, but the front end edge 451 of the connecting tube portion 45 of the inner ring 38. The plurality of engagement pieces 46 provided on the outer ring 40 contribute to prevention of the outer ring 40 from falling off.

(5) The engaging piece 46 can be formed at the same time as the inner ring 38 is pressed, and the engaging piece 46 can be easily formed without increasing the number of parts.
The number of the engagement pieces 46 may be three as in the second embodiment of FIG. 4, or five or more. In the case of FIG. 4, the individual engagement pieces 46 can be easily engaged with the outer ring 40, and the frictional preload applied to the elastic ring 39 by the individual engagement pieces 46 can be easily equalized.

Next, a third embodiment of FIG. 5 will be described. The same reference numerals are used for the same components as those in the first embodiment.
The engaging piece 46A as a preload applying means provided on the inner ring 38 is bent so as to engage with the outer peripheral side of the end face 393 of the elastic ring 39. Also in this case, the frictional preload that elastically deforms the elastic ring 39 is applied to the elastic ring 39 so that the outer peripheral portion 391 and the inner peripheral portion 392 of the elastic ring 39 are relatively displaced in the direction of the rotation axis 181 of the hub 36. Is granted.

Next, a fourth embodiment of FIG. 6 will be described. The same reference numerals are used for the same components as those in the first embodiment.
An engagement piece 46B as a preload applying means provided on the inner ring 38 is bent so as to engage with the end face 403 of the armature 42 on the side facing the suction disk 302. Also in this case, the frictional preload that elastically deforms the elastic ring 39 is applied to the elastic ring 39 so that the outer peripheral portion 391 and the inner peripheral portion 392 of the elastic ring 39 are relatively displaced in the direction of the rotation axis 181 of the hub 36. Is granted.

Next, a fifth embodiment of FIG. 7 will be described. The same reference numerals are used for the same components as those in the first embodiment.
An engagement piece 48 provided as a preload applying means provided on the outer ring 40 is bent so as to engage with the rear surface 441 of the disc portion 44 on the side facing the armature 42. Also in this case, the frictional preload that elastically deforms the elastic ring 39 is applied to the elastic ring 39 so that the outer peripheral portion 391 and the inner peripheral portion 392 of the elastic ring 39 are relatively displaced in the direction of the rotation axis 181 of the hub 36. Is granted. In the fifth embodiment, even when the elastic ring 39 is broken, the outer ring 40 is prevented from falling off by the engagement piece 48.

Next, a sixth embodiment of FIG. 8 will be described. The same reference numerals are used for the same components as those in the first embodiment.
The engaging piece 48 </ b> A provided as a preload applying means provided on the outer ring 40 is bent so as to engage with the front end edge 451 of the connecting cylinder portion 45. Also in this case, the frictional preload that elastically deforms the elastic ring 39 is applied to the elastic ring 39 so that the outer peripheral portion 391 and the inner peripheral portion 392 of the elastic ring 39 are relatively displaced in the direction of the rotation axis 181 of the hub 36. Is granted. In the sixth embodiment, even when the elastic ring 39 is broken, the outer ring 40 is prevented from dropping by the plurality of engagement pieces 48A.

In the present invention, the following embodiments are also possible.
The engagement pieces 46, 46A, 46B may be formed separately from the inner ring 38.
The engagement pieces 48, 48A may be formed separately from the outer ring 40.

The engagement piece may be screwed to the base 37, the inner ring 38 or the outer ring 40.
The base 37 and the inner ring 38 may be integrally formed.

A plurality of rubbers may be arranged around the inner ring 38 at equal intervals instead of the elastic ring 39.
-You may use a spring as an elastic body.

  As disclosed in Patent Document 1, the present invention may be applied to an electromagnetic spring clutch type power transmission mechanism in which a coil spring is wound (reduced in diameter) when the armature 42 is attracted to the adsorption disk 302.

1 is a side sectional view showing a first embodiment. (A) is a partial expanded side sectional view. FIG. 4B is a side sectional view showing the inner ring 38 before the engagement piece 46 is bent. The front view of an electromagnetic spring clutch type power transmission mechanism. The front view of the electromagnetic spring clutch type power transmission mechanism which shows 2nd Embodiment. The partial expanded side sectional view which shows 3rd Embodiment. The partial expanded side sectional view which shows 4th Embodiment. The partial expanded side sectional view which shows 5th Embodiment. The partial expanded side sectional view which shows 6th Embodiment.

Explanation of symbols

  181: A rotational axis. 29 ... Electromagnetic spring clutch type power transmission mechanism. 30: A rotor as a driving side rotating body. 34 ... Solenoid. 36: Hub as a driven rotating body. 38 ... Inner ring as a rotating body on the output side. 39: An elastic ring as an elastic body. 391 ... peripheral part. 392 ... inner peripheral part. 40: An outer ring as a rotating body on the input side. 402: End face. 41 ... Coil spring. 42 ... Armature. 45: Connecting cylinder part. 46, 46A, 46B, 48, 48A ... engagement pieces as preload applying means.

Claims (5)

In the state where the driving side rotating body rotates with the driving side rotating body, the armature attracted to the driving side rotating body by energizing the solenoid, and the armature being attracted to the driving side rotating body, the driving A coil spring that expands or contracts in diameter as the side rotating body rotates, and a driven-side rotating body that transmits the rotational driving force of the driving-side rotating body through the expanded or contracted coil spring. The driven-side rotator includes an input-side rotator that contacts the coil spring and obtains a rotational driving force from the drive-side rotator, an output-side rotator, the input-side rotator, and the output-side rotator. An electromagnetic spring clutch type power transmission mechanism comprising: an elastic body connected to the elastic body for transmitting the rotational driving force of the input side rotating body to the output side rotating body;
At least one of the output-side rotator and the input-side rotator includes an electromagnetic spring provided with a preload applying unit that rubs against the elastic body in the direction of the rotation axis of the driven-side rotator and applies a preload. Clutch type power transmission mechanism.   The preload applying means is an engagement piece formed on one of the output side rotation body and the input side rotation body, and the engagement piece is formed on the one side so as to elastically deform the elastic body. The electromagnetic spring clutch type power transmission mechanism according to claim 1 engaged with the other corresponding one.   The electromagnetic spring clutch type power transmission mechanism according to claim 2, wherein the engagement piece is engaged with the other side so as to be bent and elastically deform the elastic body.   The input-side rotator is a ring-shaped outer ring on the outer peripheral side of the output-side rotator, and the elastic body is interposed between the inner periphery of the outer ring and the outer periphery of the output-side rotator. A ring-shaped rubber elastic ring, wherein the engagement piece is provided on the output-side rotator, and the engagement piece is directed from the inside to the outside in the radial direction of the output-side rotator. The outer ring side of the elastic ring is engaged with the end surface of the outer ring by bending, and the inner peripheral part of the elastic ring on the output side rotating body side is the direction of the rotation axis of the driven side rotating body The electromagnetic spring clutch type power transmission mechanism according to claim 3, wherein the friction preload is applied to the elastic ring so as to be relatively displaced.   5. The output-side rotator includes a cylindrical connecting cylinder portion connected to the rubber elastic ring, and the engagement piece is integrally formed with an end edge of the connecting cylinder portion. Electromagnetic spring clutch power transmission mechanism.

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