JP2005180559A - Power transmission device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a power transmission device, securing durability of an elastic member. <P>SOLUTION: This power transmission device includes: a drive side rotating member rotated on receiving the rotary driving force from a driving source; a driven side rotating member connected to a rotating shaft of a driven side device; and a power transmitting member for transmitting the rotation of the drive side rotating member to the driven side rotating member. The power transmitting part is composed of a cylindrical spring member, one end of which is connected to the driven side rotating member, the other end being connected to the drive side rotating member, and which is deformed in the radial direction by the rotary driving force of the drive side rotating member, and the elastic member disposed in the deforming direction of the spring member. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a power transmission device suitable for use in a vehicle air conditioner.

  Conventionally, as a power transmission device that transmits power from a driving side rotating member that is rotationally driven by a driving source to a driven side device connected to the driven side rotating driving member, between the driving side rotating member and the driven side rotating member An apparatus is known in which an elastic member is interposed as a power transmission unit and transmits power while absorbing torque fluctuations caused by work of a driven device due to compression deformation of the elastic member (for example, Patent Document 1).

However, it has been found that in the configuration as in Patent Document 1, the elastic member is greatly distorted by compression deformation, and there is a problem in durability.
JP 2003-202065 A

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a power transmission device capable of ensuring the durability of an elastic member.

  In order to achieve the above object, according to the first aspect of the present invention, the driving side rotating member (110) that rotates by receiving the rotational driving force from the driving source and the rotating shaft (210) of the driven side device are coupled. A power transmission device including a driven side rotation member (120) and a power transmission unit (130) that transmits the rotation of the drive side rotation member (110) to the driven side rotation member (120). ), One end (134) is connected to the driven side rotating member (120), the other end (135) is connected to the driving side rotating member (110), and the rotational driving force of the driving side rotating member (110) is used. A cylindrical spring member (131) deformed in the radial direction and an elastic member (132) provided in the deformation direction of the spring member (131). When the spring member (131) is deformed in the radial direction, Spring member (131) is elastic part Characterized by pressing (132) in the radial direction.

  Accordingly, when the spring member (131) is deformed in the radial direction by the rotational driving force of the drive side rotating member (110), the spring member (131) presses the elastic member (132) in the radial direction. That is, the spring member (131) and the elastic member (132) are subjected to the distortion when the rotational driving force is transmitted from the driving side rotational member (110) to the driven side rotational member (120) and the impact when the rotational driving force varies. Therefore, the elastic member (132) is not greatly distorted. Therefore, it is possible to ensure the durability of the elastic member (131).

  According to a second aspect of the present invention, in the first aspect of the present invention, the elastic member (132) is provided in the radially inward direction of the spring member (131), and the spring member is a drive side rotating member. It is characterized by being deformed so that the inner diameter is reduced by the rotational driving force of (110).

  Thus, when the spring member (131) is deformed in the radially inward direction by the rotational driving force of the drive side rotating member (110), the elastic member (132) disposed in the radially inward direction of the spring member (131) is tightened. Since the pressure is applied, the spring member (131) and the elastic member (the deformation when the rotational driving force is transmitted from the driving side rotational member (110) to the driven side rotational member (120) and the impact when the rotational driving force varies) 132) can be dispersed and absorbed.

  The invention according to claim 3 is the invention according to claim 2, wherein the intermediate portion between the one end portion (134) and the other end portion (135) of the spring member (131) is a driven side rotating member (120). A spiral portion (136) wound so that the inner diameter is reduced by the rotational driving force of the driving side rotating member (110) is formed in the circumferential direction.

  The spiral portion (136) is greatly deformed in the circumferential direction due to distortion when the rotational driving force is transmitted and an impact when the rotational driving force varies, but the amount of reduction of the inner diameter caused by the circumferential deformation is circular. It is smaller than the amount of deformation in the circumferential direction, and the amount of deformation of the elastic member (132) is also small.

  The spiral portion (136) wound so that the inner diameter is reduced by the rotational driving force of the driving side rotating member (110) is the driving side rotating member (110) from the other end portion (135) of the spring member (131). ) Indicates a state in which the spiral portion (136) is wound in a direction (reverse rotation direction) opposite to the rotation direction (forward rotation direction).

  According to a fourth aspect of the present invention, in the first aspect of the present invention, the elastic member (132) is provided in a radially outward direction of the spring member (131), and the spring member is a driving side rotating member. It is characterized by being deformed so that the outer diameter is enlarged by the rotational driving force of (110).

  Accordingly, when the spring member (131) is deformed in the radially outward direction by the rotational driving force of the drive side rotating member (110), the elastic member (132) disposed in the radially outward direction of the spring member (131) is pressed from the inside. Therefore, the spring member (131) and the elastic member (132) are subjected to distortion when the rotational driving force is transmitted from the driving side rotational member (110) to the driven side rotational member (120) and impact when the rotational driving force varies. ) And can be absorbed.

  The invention according to claim 5 is the invention according to claim 4, wherein the intermediate portion between the one end portion (134) and the other end portion (135) of the spring member (131) is a driven side rotating member (120). A spiral portion (136) wound so that the outer diameter is enlarged by the rotational driving force of the drive side rotation member (110) is formed in the circumferential direction of the motor.

  The spiral portion (136) is greatly deformed in the circumferential direction due to distortion when the rotational driving force is transmitted and an impact when the rotational driving force varies, but the amount of expansion of the outer diameter caused by the deformation in the circumferential direction is It is smaller than the amount of deformation in the circumferential direction, and the amount of deformation of the elastic member (132) is also small.

  Note that the spiral portion (136) wound so that the outer diameter is enlarged by the rotational driving force of the drive side rotation member (110) is the rotation direction of the drive side rotation member (110) from the other end portion (135) ( This indicates a state in which the spiral portion (136) is wound in the same direction (forward rotation direction) as the forward rotation direction).

  According to a sixth aspect of the present invention, in the first aspect of the invention, the elastic member (132) is provided in the radially inward direction and the radially outward direction of the spring member (131). The drive-side rotating member (110) is deformed so that its diameter is enlarged or reduced by the rotational driving force of the drive-side rotating member (110).

  Thereby, when the diameter of the spring member (131) is deformed in the direction of expanding or reducing by the rotational driving force of the driving side rotating member (110), the spring member (131) is arranged in the radially inward direction and radially outward direction. Since the elastic member (132) is pressed, the distortion when the rotational driving force is transmitted from the driving side rotational member (110) to the driven side rotational member (120) and the impact when the rotational driving force fluctuates are spring members ( 131) and the elastic member (132) can be dispersed and absorbed.

  The invention according to claim 7 is the invention according to any one of claims 2, 4, and 6, wherein the spring member (131) is in contact with the elastic member (132) in a plane. Features.

  Thereby, the pressure per unit area which presses an elastic member (132) is disperse | distributed to a plane, and it is possible to reduce the pressure added to an elastic member (132).

  The invention according to claim 8 is the invention according to claim 3 or claim 5, wherein the spiral portion (136) continuing from the one end portion (134) of the spring member (131) is provided on the driven side rotating member (120). ) Is wound more than a half so as to be perpendicular to the rotation axis. Thereby, it is possible to prevent the spring member (131) from being twisted when the rotational driving force is transmitted.

  The invention according to claim 9 is the invention according to claim 8, wherein the spiral portion (136) continuing from the one end portion (134) of the spring member (131) is rotated by the driven side rotating member (120). One or more windings are wound so as to be perpendicular to the shaft, and press-fitted into a driven-side rotating member flange portion (125) provided on the driven-side rotating member (120) so as to extend radially outward. .

  Thereby, the force concerning the one end side of a spiral part (136) can be reduced.

  According to a tenth aspect of the present invention, in the invention according to the third or fifth aspect, the spiral portion (136) continuing from the other end portion (135) of the spring member (131) is provided on the drive side rotating member ( 110) is wound by a half or more so as to be perpendicular to the rotation axis.

  Thereby, it is possible to prevent the spring member (131) from being kinked when the rotational driving force is transmitted.

  The invention according to claim 11 is the invention according to claim 10, wherein the spiral portion (136) continuing from the other end portion (135) of the spring member (131) is provided on the drive side rotating member (110). One or more windings are wound so as to be perpendicular to the rotation axis, and are press-fitted into a driving side rotating member flange (303) provided to extend radially outward from the driving side rotating member (110). To do.

  Thereby, the force concerning the other end side of a spiral part (136) can be reduced.

  The invention described in claim 12 is characterized in that, in the invention described in claim 3 or 5, the spiral portion (136) is formed of stainless steel.

  Thereby, even if the spiral portion (136) is repeatedly deformed and damaged by friction with other components, it is possible to prevent corrosion from the friction surface.

  The invention according to claim 13 is the invention according to claim 1, wherein the surface of the elastic member (132) is subjected to a surface treatment capable of ensuring a low coefficient of friction and durability. It is characterized by.

  The invention according to claim 14 is characterized in that, in the invention according to claim 1, the elastic member (132) is elastically deformed in the circumferential direction when a force is applied in the radial direction.

  According to a fifteenth aspect of the invention, in the first aspect of the invention, the elastic member (132) is provided with a convex portion on the side in contact with the driven side rotating member (120), and the driven side rotating member ( 120) is characterized in that a concave portion is provided at a position corresponding to the convex portion, and the concave portion is fitted into the convex portion.

  The invention according to claim 16 is the invention according to claim 9, wherein the elastic member (132) includes a flange portion (125) provided on the driven side rotation member and one end portion of the spring member (131). It has an elastic member flange part (138) which fixes an elastic member (132) by being pinched by.

  Further, in the invention described in claim 17, in the invention described in claim 1, when a radial force is applied between the elastic member (132) and the spring member (131), the elastic member (132) is deformed in the circumferential direction. When the cylindrical plate (140) is arranged and the spring member (131) is deformed in the radial direction, the elastic member (132) is pressed in the radial direction via the cylindrical plate (140).

  Thereby, the force applied to the elastic member (132) is dispersed in a plane, and the pressure per unit area applied to the elastic member (132) can be reduced, and the durability of the elastic member (132) is ensured. Is possible.

  The invention according to claim 18 is the invention according to claim 16, which is arranged between the elastic member (132) and the spring member (131), and applies a force in the radial direction in the circumferential direction. The cylindrical plate (140) includes a deformable cylindrical plate (140), and the cylindrical plate (140) has a plate flange portion (143) protruding in the radial direction. The plate flange portion (143) is one end of the spring member (131). It is characterized by being sandwiched between the spiral portion (136) continuing from the portion (134) and the elastic member flange portion (138).

  According to a nineteenth aspect of the present invention, in the power transmission device according to the first aspect, the rotational driving force transmitted from the driving side rotating member (110) to the driven side rotating member (120) is not less than a predetermined value. In this case, a part of the driven side rotation member (120) is broken to have a blocking portion that blocks transmission of the rotational driving force to the rotation shaft (210).

  The invention according to claim 20 is characterized in that the power transmission device according to any one of claims 1 to 19 is used in a power transmission device for a compressor of a vehicle air conditioner. To do.

  The circumferential direction of the present invention is a direction along the circumference of a circle drawn around the rotation axis. Moreover, the code | symbol in the parenthesis attached | subjected to each said means is an example which shows a corresponding relationship with the specific means of embodiment description later mentioned.

(First embodiment)
A first embodiment of the present invention will be described below with reference to FIGS.

(Configuration of this embodiment)
FIG. 1 is a cross-sectional view of a power transmission device 100 of the present embodiment. The power transmission device 100 transmits a rotational driving force of a vehicle traveling engine (not shown) that is a driving source to a rotating shaft 210 of a compressor 200 that is a driven device. Hereinafter, in FIG. 1, the left side of the drawing is referred to as a front side, and the right side of the drawing is referred to as a rear side.

  The compressor 200 is a component part of a refrigeration cycle of a vehicle air conditioner (not shown). The compressor 200 includes a rotation shaft 210, a refrigerant compression unit (not shown) that is driven by the rotation shaft 210 and compresses refrigerant, and a refrigerant compression unit. A cylinder-shaped compressor housing 201 (hereinafter abbreviated as “housing 201”) which accommodates a discharge capacity varying means (not shown) for changing the capacity of the refrigerant to be compressed, a refrigerant compression section and a discharge capacity varying means, and supports the rotating shaft 210. Is a well-known variable capacity refrigerant compressor.

  A cylindrical sleeve portion 202 is integrally formed at the front side end portion of the housing 201 so as to protrude in the axial direction from the center portion, and the rotating shaft 210 protrudes from the center of the sleeve portion 202. The sleeve portion 202 is a bearing holding portion that holds the ball bearing 203 on the outer peripheral side.

  The rotating shaft 210 has an outer peripheral threaded portion 211 at the tip, and this outer peripheral threaded portion 211 is coupled to an inner peripheral threaded portion 121 of the hub 210 described later.

  The power transmission device 100 is broadly divided into a pulley 110 that is a driving side rotating member that rotates in response to a rotational driving force of a vehicle traveling engine (not shown), and a rotating shaft 210 of the compressor 200, and is integrated with the rotating shaft 210. A hub 120 that is a driven side rotating member that rotates in a straight line, and a power transmission unit 130 that transmits the rotation of the pulley 110 to the hub 120.

  The pulley 110 includes a cylindrical bearing holding portion 111 that is rotatably supported by the ball bearing 203 described above, a pulley-side first plate portion 117 that extends radially outward from a substantially central portion in the axial direction of the bearing holding portion 111, and A step 118 extending from the end of the pulley-side first plate 117 to the rear side, and a pulley-side second plate 112 extending radially outward from the rear-side end of the step 118 and having a recess 115 on the front side, The pulley side cylindrical plate 113 extends from the outer peripheral surface of the pulley side second plate portion 112 to the front side. Incidentally, the bearing holding portion 111, the pulley-side first plate portion 117, the step portion 118, the pulley-side second plate portion 112, and the pulley-side cylindrical wall portion 113 constituting the pulley 110 are made of, for example, an iron-based metal material or an aluminum-based metal material. It is integrally formed of a thermosetting resin material such as a metal material or a phenol resin.

  The pulley side cylinder wall 113 is a portion to which the rotational driving force of the vehicle travel engine is transmitted by a V belt (not shown), and the V belt is hung on the outer peripheral surface. For this reason, a plurality of V-shaped grooves 114 corresponding to a plurality of V-shaped grooves (not shown) formed on the inner peripheral surface of the V-belt are formed on the outer peripheral surface of the pulley-side cylindrical wall portion 113.

  The hub 120 includes a boss part 122 provided in the center as viewed from the axial direction, a hub side plate part 123 extending radially outward from the front side wall of the boss part 122, and a front side from the outer peripheral surface of the hub side plate part 123. And a hub side cylindrical wall portion 124 extending to the rear side, and a hub side flange portion 125 extending radially outward from the front side of the hub side cylindrical wall portion 124. The boss part 122, the hub side plate part 123, the hub side cylindrical wall part 124, and the hub side flange part 125 that constitute the hub 120 are integrally formed of a high carbon steel sintered material.

  A screw portion 121 is provided on the inner peripheral surface of the boss portion 122, and the inner peripheral screw portion 121 is coupled to the rotating shaft 210 of the compressor 200 to rotate integrally.

  The hub-side cylinder wall portion 124 is provided with a rubber damper fixing groove 126 on the outer peripheral surface. The rubber damper fixing groove 126 is a groove into which a rubber damper protruding wall 133 provided along an inner peripheral surface of a rubber damper 132 (described later) constituting the power transmission unit 130 is fitted.

  A hub-side protruding wall 127 extending to the rear side is provided at the radial end of the hub-side flange portion 125.

  The power transmission unit 130 includes a torsion spring 131 and a rubber damper 132 provided inside the spiral portion 136 of the torsion spring 131.

  The torsion spring front side end portion 134 is connected to the hub 120, the torsion spring rear side end portion 135 is connected to the pulley 110, and an intermediate portion between the torsion spring front side end portion 134 and the torsion spring rear side end portion 135. Forms a spiral portion 136 wound in the circumferential direction of the hub 120 so that the inner diameter is reduced by the rotational driving force of the pulley 110.

  The torsion spring 131 is a coiled spring made of stainless steel having a rectangular cross section as shown in FIG. 2A is a view of the torsion spring 131 viewed from the front side, and FIG. 2B is a view of the torsion spring 131 viewed from the side surface (the same direction as FIG. 1).

  3A is a view of the cross section of the hub 120 taken along the broken line P in FIG. The torsion spring 131 is a notch in which the torsion spring front side end portion 134 is provided in the hub side protruding wall 127 (a portion cut so that the hub side protruding wall 127 is partially lowered). It is fitted and fixed to the portion 128 (this fixing method is referred to as a short hook type), and the hub side winding start of the spiral portion 136 is more than half a turn on the hub side flange portion 125 perpendicular to the rotating shaft 210. It is rolled up. Further, in the hub side plate portion 123, the three round holes 12A provided around the boss portion 122 are holes for inserting jigs used when the hub 120 is assembled. FIG. 3B is a view seen from the direction of the arrow R in FIG.

  4 is a view of the cross section of the pulley 110 taken along the broken line S in FIG. The torsion spring 131 is fixed by a short hook type in which the torsion spring rear side end portion 135 is fitted into the pulley side locking portion 116 that extends in the radially outward direction in the recess 115 of the pulley side second plate portion 112, and the hub side Similar to the start of winding, the pulley side winding start of the spiral portion 136 is also wound around the recess 115 perpendicular to the rotating shaft 210 by a half or more.

  The spiral portion 136 is wound from the torsion spring rear side end portion 135 in a direction (reverse rotation direction) opposite to the rotation direction (forward rotation direction) of the pulley 110. As a result, the inner diameter is reduced by the rotational driving force of the pulley 110.

  The rubber damper 132 is a cylindrical elastic member as shown in FIG. 5, and a rubber damper protruding wall 133 is provided along the inner peripheral surface. The rubber damper 132 is fixed by fitting a rubber damper protruding wall 133 into a rubber damper fixing groove 126 provided in the hub 120. The rubber damper 132 is subjected to a surface treatment (for example, fluorine substitution such as PTFE (polytetrafluoroethylene) resin coating or PTFE resin laminate) capable of ensuring a low friction coefficient and durability.

  5A is a view of the rubber damper 132 viewed from the front side, and FIG. 5B is a cross-sectional view of the rubber damper 132 viewed from the side surface (the same direction as FIG. 1).

  Further, the hub 120 and the power transmission unit 130 are located on the inner peripheral side of the pulley-side cylindrical wall 113 of the pulley 110, and when the power transmission device 100 is viewed from the radial direction, the front side of the pulley-side cylindrical wall 113. From the end, the front side of the hub side cylindrical wall portion 127 and the hub side winding start of the spiral portion 136 appear to protrude.

  In addition, the pulley 110 and the hub 120 are arranged at a minute interval in the axial direction by a torsion spring 131 constituting the power transmission unit 130.

  Here, a method for assembling the power transmission device 100 of the present embodiment will be described.

  First, the hub 120 and the rubber damper 132 are assembled by fitting the rubber damper protruding wall 133 of the rubber damper 132 into the rubber damper fixing groove 126 of the hub 120.

  Next, the pulley 110 is rotatably assembled via the ball bearing 203 to the compressor 200 that is a driven device. At this time, the rotating shaft 210 of the compressor 200 protrudes in the axial direction from the front side of the pulley 110.

  Then, the torsion spring rear side end portion 135 of the torsion spring 131 is press-fitted into the pulley side locking portion 116 of the recess 115 provided in the pulley side second plate portion 305 of the pulley 110, and the torsion spring 131 and the pulley 110 are fixed. To do.

  At this time, the spiral portion 136 of the torsion spring 131 is wound at a predetermined interval in the axial direction so that it can be bent in the axial direction.

  Next, a jig (not shown) is inserted into the circular holes 12A provided at three locations on the hub 120, and is rotated from the front side of the pulley 110 while rotating in the circumferential direction of the hub 120, and is provided on the boss portion 122 of the hub 120. The inner peripheral screw portion 121 thus formed is lightly engaged with the outer peripheral screw portion 211 provided on the rotating shaft 210. When the jig is further rotated and the inner peripheral screw portion 121 of the hub 120 is fitted to the outer peripheral screw portion 211 provided on the rotating shaft 210, the distance between the hub 120 and the pulley 110 is reduced.

  When the hub-side protruding wall 127 of the hub 120 comes to a position in contact with the torsion spring front side end portion 134 of the torsion spring 131 fixed to the pulley 110 and further rotates the jig, the hub 120 moves to the pulley 110. By approaching, the torsion spring 131 is compressed in the axial direction by the hub side protruding wall 127. When the hub side locking portion 128 and the torsion spring front side end portion 134 overlap with each other while the torsion spring 131 is compressed in the axial direction by the hub side protruding wall 127, the torsion spring front side end portion 134 becomes the hub side locking portion 128. Fit into.

  Thereafter, the inner peripheral screw portion 121 and the outer peripheral screw portion 211 are completely fitted, and the hub 120 and the rotating shaft 210 are firmly fixed from the front side of the hub 120 by a locking means such as a bolt. At this time, the torsion spring 131 is kept in a slightly compressed state in the axial direction in an unloaded state.

  Next, the operation of this embodiment will be described.

  When the pulley 110 is rotated by receiving the rotational driving force of the vehicle running engine by a V-belt (not shown), the hub 120 is rotated via the power transmission unit 130, the rotating shaft 210 connected to the hub 120 is rotated, and the compressor 200 is rotated. Drive.

  The helical portion 136 of the torsion spring 131 that constitutes the power transmission unit 130 is wound so that the inner diameter is reduced by the rotational driving force of the pulley 110, so that when transmitting power from the pulley 110 to the hub 120, Transforms into

  When the spiral portion 136 is deformed in the radial direction and the inner diameter is reduced, the rubber damper 132 provided on the outer peripheral surface of the hub side cylindrical wall portion 124 is pressed so as to be tightened in the radial direction.

  Next, the effect of this embodiment will be described.

  Distortion when power is transmitted from the pulley 110 to the hub 120 and shock when the rotational driving force fluctuates are dispersed and absorbed by the torsion spring 131 and the rubber damper 132, so that the durability of the rubber damper 132 can be ensured. It is.

  Further, the helical portion 136 of the torsion spring 131 is greatly twisted by the impact of torque fluctuation and deforms in the circumferential direction, but the amount of reduction of the inner diameter due to the deformation in the circumferential direction is smaller than the deformation amount in the circumferential direction. . That is, since the amount of deformation of the rubber damper 132 is also smaller than the amount of deformation of the torsion spring 131 in the circumferential direction, it is not necessary to elastically deform the rubber damper 132 and the durability of the rubber damper 132 can be further improved.

  In addition, since the spiral portion 136 of the torsion spring 131 is a spring having a rectangular cross section, it comes into contact with the rubber damper 132 in a plane, so that the pressure that presses the rubber damper 132 up is dispersed in the plane, and the unit area applied to the rubber damper 132 It is possible to reduce the hit pressure.

  Further, since the torsion spring 131 is a stainless spring, even if the inner diameter of the torsion spring 131 is repeatedly reduced and deformed and damaged by friction with other components, corrosion from the friction surface can be prevented. .

  Further, the torsion spring front side end portion 134 is fitted and fixed to a hub side locking portion 128 provided on the hub side protruding wall 127, and the hub side winding start of the spiral portion 136 is perpendicular to the rotating shaft 210 on the hub side. Since the flange portion 125 is wound by a half or more, it is possible to prevent the torsion spring 131 from being twisted due to a torque load.

  Similarly, the pulley side winding start of the spiral portion 136 is also wound around the concave portion 115 perpendicularly to the rotating shaft 210, so that the torsion spring 131 can be prevented from being twisted due to torque load.

  Further, the power transmission device 100 is maintained in a state where the torsion spring 131 is slightly compressed in the axial direction in an assembled state (no load state). That is, a compression reaction force of the torsion spring 131 is applied to the pulley 110 and the hub 120 in the axial direction.

  As a result, even if the helical portion 136 of the torsion spring 131 is deformed in the direction in which the diameter of the torsion spring 131 is expanded due to negative torque described later, the torsion spring front is affected by the axial reaction force of the torsion spring 131. Since the side end portion 134 and the torsion spring rear end portion 135 are pressed against the pulley side locking portion 116 and the hub side locking portion 128, respectively, the torsion spring 131 does not come off from the hub 120 and the pulley 110. .

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. In addition, the same code | symbol was attached | subjected to the site | part same as 1st Embodiment. FIG. 6 is a cross-sectional view of the power transmission device 100 according to the second embodiment. In the first embodiment, the torsion spring front side end portion 134 is fitted and fixed to the hub side locking portion 128 provided on the hub side protruding wall 127, and the hub side winding start of the spiral portion 136 is connected to the rotating shaft 210. In the present embodiment, the hub side flange portion 125 is formed so as to be thicker than the first embodiment, and the hub side flange portion 125 is formed thicker than the first embodiment. An annular press-fitting groove 129 having a hub locking portion 128 that protrudes in the radially outward direction is provided on the rear side, and the front side end portion 134 of the torsion spring 131 is fixed by the hub locking portion 128, and the spiral portion 136. The hub side winding start is wound one or more turns around the hub side flange portion 125 perpendicularly to the rotation shaft 210 and press-fitted and fixed in the press-fitting groove 129.

  As a result, it is possible to reduce the force applied to the hub side winding start of the torsion spring front side end portion 134 and the spiral portion 136.

(Modification of the first embodiment and the second embodiment)
In the first embodiment and the second embodiment described above, a cylindrical elastic member as shown in FIG. 5 is used as the rubber damper 132. However, as shown in FIG. 7, a rubber damper notch 137 is provided in the rubber damper 132. It may be. When the rubber damper notch 137 is provided, the rubber damper 132 is elastically deformed in the circumferential direction when pressed in the radial direction. As a result, it is possible to increase the effect of absorbing the impact of torque fluctuation by the rubber damper 132. 7A is a view of the rubber damper 132 in the modification as seen from the front side, and FIG. 7B is a cross-sectional view as seen from the side surface (the same direction as FIG. 1).

  Further, in the first embodiment and the second embodiment, nothing is interposed between the torsion spring 131 and the rubber damper 132, but a cylindrical shape as shown in FIG. 8 is provided between the torsion spring 131 and the rubber damper 132. The plate 140 may be interposed. 8A is a view of the plate 140 viewed from the front side, and FIG. 8B is a cross-sectional view of the plate 140 viewed from the side surface (the same direction as FIG. 1).

  The plate 140 has a cylindrical shape in which a plate notch 141 is formed, and a plurality of bent plate portions 142 extending radially inward are provided on the front side edge, and a rubber damper 132 and a hub side flange are provided. The plate 140 is fixed by being sandwiched between the portions 125. The plate 140 is deformed in the circumferential direction by the plate notch 141 when pressed in the radial direction.

  FIG. 9 is a cross-sectional view showing only the upper half in a state in which the plate 140 is interposed between the torsion spring 131 and the rubber damper 132 in the first and second embodiments described above. In the plate 140, the bent plate portion 142 is fixed by being sandwiched between the front side of the rubber damper 132 and the rear side of the hub side flange portion 125. 9A is a cross-sectional view when the plate 140 is applied to the first embodiment, and FIG. 9B is a cross-sectional view when the plate 140 is applied to the second embodiment.

  As a result, the inside of the spiral portion 136 is in contact with the rubber damper 132 through the plate 140 in a plane, so that the pressure that presses the rubber damper 132 up is dispersed on the plane, and the pressure per unit area applied to the rubber damper 132 is reduced. It is possible.

(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIG. In addition, the same code | symbol was attached | subjected to the site | part same as 1st Embodiment.

  FIG. 10 is a cross-sectional view showing only the upper half of the power transmission device 100 in the present embodiment. In the first embodiment and the second embodiment, the rubber damper protruding wall 133 is provided on the inner peripheral portion of the rubber damper 132, and the rubber damper protruding wall 133 is fixed by being fitted into the rubber damper fixing groove 126 provided in the hub 120. In this embodiment, a rubber damper flange 138 extending radially outward is provided at the front end of the rubber damper 132, and the rubber damper flange 138 is connected to the hub flange 125, the torsion spring front end 134, and the spiral. The elastic member is fixed by being sandwiched between the hub side winding start of the portion 136. Note that the torsion spring 131 of this embodiment has a circular cross section.

(Modification of the third embodiment)
FIG. 11 is a cross-sectional view showing only the upper half of the power transmission device 100 according to a modification of the third embodiment. In the present embodiment, a cylindrical plate 140 is interposed between the torsion spring 131 and the rubber damper 132, as in the modifications of the first and second embodiments. The plate 140 according to the present embodiment has plate flange portions 143 that project from the front side edge to the radially outer side at a plurality of locations. The plate flange portion 143 includes the torsion spring front side end portion 134 and the spiral portion 136. Between the hub side winding and the rubber damper flange 138 and fixed.

(Fourth embodiment)
Next, a fourth embodiment of the present invention will be described with reference to FIGS. In addition, the same code | symbol was attached | subjected to the site | part same as 1st thru | or 3rd embodiment.

  In the first to third embodiments, the spiral portion 136 of the torsion spring 131 is configured so that the inner diameter is reduced by the rotational driving force of the pulley 110, and the rubber damper 132 is provided inside the spiral portion 136. In the embodiment, the spiral portion 136 of the torsion spring 131 is configured such that the outer diameter is enlarged by the rotational driving force of the pulley 110, and the rubber damper 132 is provided outside the spiral portion 136.

  FIG. 12 is a cross-sectional view of the power transmission device 100 in the present embodiment. The hub 120 in the present embodiment has a hub inner cylindrical portion 300 (the hub-side cylindrical wall portion 124 of the first embodiment extends only to the front side) extending from the outer peripheral surface of the hub-side plate portion 123 to the front side. Yes. The hub inner cylinder part 300 is provided with a notch 302 for fixing the torsion spring front side end part 134.

  Further, the hub 120 has a hub outer cylinder portion 301 (the hub-side protruding wall 127 of the first embodiment further extended to the rear side) extending to the rear side at the radial end of the hub-side flange portion 125. doing.

  The pulley 110 in the present embodiment extends radially outward from the rear side of the side wall of the bearing holding portion 111, and the groove portion into which the spiral portion 136 of the torsion spring 131 starts to be wound on the pulley side and the torsion spring rear side end portion 135 is fitted on the front side. A pulley-side first plate portion 303 having 307, a step portion 304 extending from the end portion of the pulley-side first plate portion 303 to the front side, and a pulley-side second portion extending radially outward from the front-side end portion of the step portion 304. The plate portion 305 includes a pulley-side cylindrical wall portion 306 extending from the outer peripheral surface of the pulley-side second plate portion 305 to the front side and the rear side.

  FIG. 13 is a view showing the configuration of the torsion spring 131 in this embodiment, FIG. 13 (a) is a view of the torsion spring 131 viewed from the front side, and FIG. 13 (b) is an illustration of the torsion spring 131. It is the figure seen from the side. In the torsion spring 131 in the present embodiment, the torsion spring front side end portion 134 and the torsion spring rear side end portion 135 are bent in the radially inward direction, and the spiral portion 136 is opposite in winding direction to the first to third embodiments. It has become.

  Specifically, the spiral portion 136 is wound from the rear end portion 135 of the torsion spring in the same direction as the rotation direction (forward rotation direction) of the pulley 110.

  FIG. 14 is a view showing a coupling structure between the torsion spring front side end portion 134 and the hub 120 in this embodiment, and is a cross-sectional view taken along the broken line P in FIG. . The torsion spring front side end portion 134 is fixed by being fitted into a notch portion 302 provided in the hub inner cylinder portion 300.

FIG. 15 is a view showing a coupling structure between the torsion spring rear end portion 135 and the pulley 110 in the present embodiment. The pulley 110 is a cross section taken along the broken line S in FIG. 2 is a sectional view of a ball bearing 203. FIG. The groove portion 307 is provided with a protruding portion 308 protruding in the inner diameter direction (in other words, the protruding portion 308 is formed such that the pulley-side first plate portion 303 is recessed in the inner diameter direction). The torsion spring rear side end portion 135 is fixed by being fitted into the protruding portion 308. FIG. 16 is a view showing the configuration of the rubber damper 132 in this embodiment, and FIG. 16 (a) is the same as FIG. A cross-sectional view taken along a cross section, FIG. 16B, is a view of the rubber damper 132 viewed from the front side. A rubber damper fixing groove 126 is provided on the inner peripheral side of the hub outer cylinder portion 301, and the rubber damper 132 is fixed by fitting a rubber damper protruding wall 133 provided on the outer peripheral surface of the rubber damper 132 into the rubber damper fixing groove 126. (See FIG. 12).

  Also in this embodiment, as in the first embodiment, the impact of torque fluctuation is dispersed and absorbed by the torsion spring 131 and the rubber damper 132, so that the durability of the rubber damper can be ensured.

  In addition, the helical portion 136 of the torsion spring 131 is largely twisted by the impact of torque fluctuation and deforms in the circumferential direction. However, the expansion amount of the outer diameter due to the deformation in the circumferential direction is larger than the deformation amount in the circumferential direction. small. That is, since the amount of deformation of the rubber damper 132 is also smaller than the amount of deformation of the torsion spring 131 in the circumferential direction, it is not necessary to elastically deform the rubber damper 132 and the durability of the rubber damper 132 can be further improved.

(Fifth embodiment)
Next, a fifth embodiment of the present invention will be described with reference to FIGS. In addition, the same code | symbol was attached | subjected to the site | part same as 1st thru | or 4th embodiment.

  In the first to third embodiments, the spiral portion 136 of the torsion spring 131 is configured such that the inner diameter is reduced by the rotational driving force of the pulley 110, and a rubber damper 132 is provided inside the spiral portion 136. In the fourth embodiment, The helical portion 136 of the torsion spring 131 is configured so that the outer diameter is enlarged by the rotational driving force of the pulley 110, and the rubber damper 132 is provided on the outside of the helical portion 136. The spiral portion 136 is configured such that the inner diameter is reduced by the rotational driving force of the pulley 110, and rubber dampers 132 are provided outside and inside the spiral portion 136.

  FIG. 17 is a cross-sectional view of the power transmission device 100 in the present embodiment. The hub 120 according to the present embodiment includes a hub outer cylinder portion 301 (first embodiment) extending to the rear side at the radial end of the hub side cylinder wall portion 124 and the hub side flange portion 125 having the same shape as the first embodiment. The hub side protruding wall 127 of the configuration is further extended to the rear side). The hub outer tube portion 301 is provided with a hub outer tube notch portion 316 communicating with a rubber damper outer tube notch portion 315 described later.

  A rubber damper 132 as shown in FIG. 18 is fixed to a rubber damper fixing groove 126 provided on the outer peripheral surface of the hub side cylindrical wall portion 124.

  18 is a view showing the configuration of the rubber damper 132 in the present embodiment, FIG. 18 (a) is a cross-sectional view of the rubber damper 132 cut along the same cross section as FIG. 17, and FIG. 18 (b) is a broken line in FIG. It is sectional drawing which looked at the cross section cut by U from the direction of the arrow V. FIG.

  The rubber damper 132 in this embodiment has a shape in which a rubber damper inner cylinder 309 and a rubber damper outer cylinder 310 are connected by a front side end surface 311.

  As in the first embodiment, a rubber damper protruding wall 133 is provided on the inner peripheral surface of the rubber damper inner cylinder 309.

  The rubber damper outer cylinder 310 is disposed coaxially with the rubber damper inner cylinder 309, and the inner peripheral surface 313 of the rubber damper outer cylinder 310 is spaced apart from the outer peripheral surface 312 of the rubber damper inner cylinder 310 by a front end surface 311. Are arranged.

  The rubber damper outer cylinder 310 is provided with a rubber damper outer cylinder hole notch 315 cut from the rear side to the front side.

  As shown in FIG. 17, the torsion spring 131 in this embodiment is disposed between the outer peripheral surface 312 of the rubber damper inner cylinder 309 and the inner peripheral surface 313 of the rubber damper outer cylinder 310.

  19A is a view of the cross section of the hub 120, the rubber damper 132, and the torsion spring 131 taken along the section indicated by the broken line P in FIG. 17 as viewed from the direction indicated by the arrow Q. The side end portion 134 is fixed to the hub 120 by being fitted into the rubber damper outer cylinder hole notch 315 and the hub outer cylinder notch 316. FIG. 19B is a partial side view of the hub 120 viewed from the direction indicated by the arrow R in FIG.

  The pulley 110 in this embodiment has the same structure as that of the first embodiment, and the torsion spring rear side end portion 135 of the torsion spring 131 is the pulley-side second plate portion 112 as in the first embodiment. Of the recess 115 is fixed by a short hook type that is fitted into a pulley-side locking portion 116 that spreads radially outward.

  According to the present embodiment, since the torsion spring 131 is disposed between the rubber damper inner cylinder 309 and the rubber damper outer cylinder 310 of the rubber damper 132, not only the diameter of the torsion spring 131 is reduced but also the outer diameter is enlarged. In addition, the fluctuation of the rotational driving force can be dispersed and absorbed by the torsion spring 131 and the rubber damper 132.

  That is, when the torsion spring 131 is wound so that the inner diameter is reduced by the rotational driving force in the forward rotation direction, and the compressor 200 is operated at a low capacity and negative torque is generated (when negative torque is generated, the rotational driving force in the reverse rotation direction is generated). Even if the outer diameter of the torsion spring 131 is deformed in a direction in which the outer diameter of the torsion spring 131 increases, the impact can be dispersed and absorbed by the torsion spring 131 and the rubber damper 132.

(Other embodiments)
In the above embodiment, stainless steel is used as the material of the torsion spring 131, but the present invention is not limited to this, and a piano wire, a hard steel wire, an oil tempered wire, or the like may be used. In addition, even if the diameter of the torsion spring 131 is repeatedly deformed and damaged by friction with other components, surface treatment may be performed by plating, electrodeposition coating, or the like in order to prevent corrosion from the friction surface. Good.

  Moreover, in the said embodiment, although the torsion spring 131 was used as a spring member, you may make it use a spiral spring.

  In the above embodiment, the fixing structure for fixing the torsion spring front side end portion 134 and the torsion spring rear side end portion 135 to the hub 120 and the pulley 110 is a short hook type. You may make it fix to the hub 120 and the pulley 110 by general end shapes, such as a two-step bending.

  In the above embodiment, the hub side plate is used when a rotational driving force of a predetermined value or more is transmitted to the power transmission device 100, such as when the rotating shaft 210 stops moving due to the compressor 200 biting in a foreign object or the like. A torque limiter mechanism that cuts off transmission of the rotational driving force to the rotating shaft 210 when a part of the portion 123 is broken may be incorporated.

  In the first to third embodiments, the cylindrical plate 140 is disposed between the torsion spring 131 and the rubber damper 132 as a modification, but this modification is applied to the fourth and fifth embodiments. Also good.

  Further, in the fifth embodiment, the rubber dampers 132 are disposed on both the inner and outer diameter sides of the torsion spring 131 wound so that the inner diameter is reduced by the rotational driving force in the forward rotation direction. However, the rubber dampers 132 may be disposed on both the inner and outer diameter sides of the torsion spring 131 wound so that the outer diameter is increased by the rotational driving force in the forward rotation direction. .

  Further, in the second embodiment, the front side end portion 134 of the torsion spring 131 is fixed by the hub locking portion 128, and the hub side winding start of the spiral portion 136 is set to 1 on the hub side flange portion 125 perpendicular to the rotation shaft 210. Although the winding is more than the winding, and the press-fitting groove 129 is press-fitted and fixed, even if the press-fitting groove 129 is formed wider than the spiral part 136, the hub locking portion 128 causes the front end 134 of the torsion spring 131 to move. If fixed, the inner diameter of the spiral portion 136 is reduced by the rotational driving force of the pulley 110 and the inner wall of the press-fitting groove 129 is tightened, so that the hub 120 and the torsion spring 131 are fixed. Is done.

It is sectional drawing of the power transmission device 100 in 1st Embodiment. It is a figure which shows the shape of the torsion spring 131. FIG. It is the figure which looked at the cross section of the hub 120 in the broken line P in FIG. FIG. 2 is a view of a cross section of a pulley 110 taken along a broken line S in FIG. It is a figure which shows the shape of the rubber damper 132 in 1st Embodiment. It is sectional drawing of the power transmission device 100 in 2nd Embodiment. It is a figure which shows the shape of the rubber damper 132 in the modification of 1st, 2nd embodiment. It is a figure which shows the shape of the plate 140 in the modification of 1st, 2nd embodiment. It is sectional drawing showing only the upper half of the state which interposed the plate 140 between the torsion spring 131 and the rubber damper 132 in the modification of 1st Embodiment and 2nd Embodiment. It is sectional drawing which shows only the upper half of the power transmission device 100 in 3rd Embodiment. It is sectional drawing which shows only the upper half of the power transmission device 100 in the modification of 3rd Embodiment. It is sectional drawing of the power transmission device 100 in 4th Embodiment. It is a figure which shows the shape of the torsion spring 131 in 4th Embodiment. It is the figure which looked at the cross section of the hub 120 in the broken line P in FIG. It is the figure which looked at the cross section of the pulley 110 in the broken line S in FIG. It is a figure which shows the shape of the rubber damper 132 in 1st Embodiment. It is sectional drawing of the power transmission device 100 in 5th Embodiment. It is a figure which shows the shape of the rubber damper 132 in 5th Embodiment. It is the figure which looked at the cross section of the hub 120 in the broken line P in FIG.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... 100 ... Power transmission device, 110 ... Pulley, 120 ... Hub, 130 ... Power transmission part, 131 ... Torsion spring, 132 ... Rubber damper, 133 ... Rubber damper protruding wall, 134 ... Torsion spring front side end part, 135 ... Torsion spring Rear side end portion, 136 ... spiral portion, 137 ... rubber damper notch, 138 ... rubber damper flange portion, 140 ... plate, 210 ... rotating shaft.

Claims (20)

A driving side rotating member (110) that rotates by receiving a rotational driving force from a driving source;
A driven side rotating member (120) coupled to the rotating shaft (210) of the driven side device;
A power transmission device including a power transmission unit (130) for transmitting rotation of the driving side rotation member (110) to the driven side rotation member (120);
The power transmission unit (130) has one end (134) connected to the driven-side rotating member (120) and the other end (135) connected to the driving-side rotating member (110). A cylindrical spring member (131) deformed in the radial direction by the rotational driving force of the member (110);
An elastic member (132) provided in the deformation direction of the spring member (131),
When the spring member (131) is deformed in the radial direction, the spring member (131) presses the elastic member (132) in the radial direction. The elastic member (132) is provided in the radially inward direction of the spring member (131),
2. The power transmission device according to claim 1, wherein the spring member is deformed so that an inner diameter thereof is reduced by a rotational driving force of the driving-side rotating member (110). The intermediate portion between the one end portion (134) and the other end portion (135) of the spring member (131) rotates the drive side rotating member (110) in the circumferential direction of the driven side rotating member (120). The power transmission device according to claim 2, wherein a spiral portion (136) wound so that the inner diameter is reduced by a driving force is formed. The elastic member (132) is provided in the radially outward direction of the spring member (131),
2. The power transmission device according to claim 1, wherein the spring member is deformed so that an outer diameter thereof is enlarged by a rotational driving force of the driving side rotating member (110). The intermediate portion between the one end portion (134) and the other end portion (135) of the spring member (131) rotates the drive side rotating member (110) in the circumferential direction of the driven side rotating member (120). The power transmission device according to claim 4, wherein a spiral portion (136) wound so that an outer diameter is enlarged by a driving force is formed. The elastic member (132) is provided in the radially inward direction and radially outward direction of the spring member (131),
2. The power transmission device according to claim 1, wherein the spring member is deformed so that a diameter thereof is enlarged or reduced by a rotational driving force of the driving side rotating member (110). The power transmission device according to any one of claims 2, 4, and 6, wherein the spring member (131) is in contact with the elastic member (132) in a plane. The spiral portion (136) continuing from the one end portion (134) of the spring member (131) is wound on the driven side rotation member (120) by more than half a turn so as to be perpendicular to the rotation axis. The power transmission device according to claim 3 or 5, wherein the power transmission device is provided. The spiral portion (136) continuing from the one end portion (134) of the spring member (131) is wound around the driven side rotation member (120) by one or more turns so as to be perpendicular to the rotation axis. The power transmission device according to claim 8, wherein the power transmission device is press-fitted into a driven side rotating member flange portion (125) provided so as to extend radially outward from the side rotating member (120). The spiral portion (136) continuing from the other end portion (135) of the spring member (131) is wound on the driving side rotation member (110) by a half or more turns so as to be perpendicular to the rotation axis. The power transmission device according to claim 3 or 5, wherein the power transmission device is provided. The spiral portion (136) continued from the other end portion (135) of the spring member (131) is wound around the drive side rotation member (110) by one or more turns so as to be perpendicular to the rotation axis. 11. The power transmission device according to claim 10, wherein the power transmission device is press-fitted into a drive-side rotation member flange portion (303) provided so as to extend radially outward from the drive-side rotation member (110). The power transmission device according to claim 3 or 5, wherein the spiral portion (136) is made of stainless steel. The power transmission device according to claim 1, wherein the surface of the elastic member (132) is subjected to a surface treatment capable of ensuring a low coefficient of friction and durability. The power transmission device according to claim 1, wherein the elastic member (132) elastically deforms in a circumferential direction when a force is applied in a radial direction. The elastic member (132) is provided with a convex portion on the side in contact with the driven side rotating member (120), and the driven side rotating member (120) is provided with a concave portion at a position corresponding to the convex portion. The power transmission device according to claim 1, wherein the concave portion is fitted into the convex portion. The elastic member (132) is an elastic member flange sandwiched between a flange portion (125) provided on the driven side rotating member and a spiral portion (136) continuing from the one end portion (134) of the spring member (131). The power transmission device according to claim 9, further comprising a portion (138). Between the elastic member (132) and the spring member (131), a cylindrical plate (140) that is deformed in the circumferential direction when a force is applied in the radial direction is arranged,
The power transmission device according to claim 1, wherein when the spring member (131) is deformed in the radial direction, the elastic member (132) is pressed in the radial direction via the cylindrical plate (140). . A cylindrical plate (140) disposed between the elastic member (132) and the spring member (131) and deformed in a circumferential direction when a force is applied in a radial direction;
The cylindrical plate (140) has a plate flange portion (143) protruding radially.
The said plate flange part (143) is pinched | interposed into the said helical part (136) continuing from the one end part (134) of the said spring member (131), and the said elastic member flange part (138), It is characterized by the above-mentioned. 16. The power transmission device according to 16. When the rotational driving force transmitted from the driving side rotating member (110) to the driven side rotating member (120) becomes a predetermined value or more, a part of the driven side rotating member (120) is broken, 2. The power transmission device according to claim 1, further comprising a blocking portion that blocks transmission of a rotational driving force to the rotating shaft. The power transmission device according to any one of claims 1 to 19, wherein the power transmission device is used in a power transmission device for a compressor of a vehicle air conditioner.

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