JP5384290B2 - Torque limiter and torsion damper equipped with the torque limiter - Google Patents

Description

  The present invention relates to a friction type torque limiter that suppresses transmission of excessive torque, and a torsion damper including the torque limiter.

  For example, a torsion damper that absorbs torsional vibration due to torque fluctuation is provided at a connecting portion between an output shaft of an internal combustion engine and an input shaft of a transmission in a car. As such a torsion damper, a torque limiter that causes slippage when an excessive torque is input and suppresses an excessive load from acting on each part of the internal combustion engine and the transmission connected via the torsion damper. There are known torsion dampers equipped with.

  As shown in FIG. 11, in the torsion damper disclosed in Patent Document 1, the input shaft 1 and the hub 2 of the transmission shown by the two-dot chain line are connected to the center left side of FIG. A pair of accommodating members 3 and 4 are connected to the portion. The disc member 5 is sandwiched between the pair of accommodating members 3 and 4 and the accommodating members 3 and 4 and the disc member 5 are connected via the coil spring 6 to absorb torsional vibration caused by torque fluctuation. A damper 8 is formed.

  Further, a friction member 9 is fixed to the outer periphery of the disk member 5, and the friction member 9 is connected to the output shaft 10 of the internal combustion engine indicated by a two-dot chain line on the center right side of FIG. The friction type torque limiter 13 is formed by being sandwiched between the ring member 12 and the ring member 12.

  The ring member 12 is urged toward the front case 11 by the urging force of the disc spring 15 sandwiched between the front case 11 and the rear case 14 together with the friction member 9 and the ring member 12. Then, the magnitude of the frictional force generated between the front case 11 and the ring member 12 and the frictional member 9 is adjusted by this urging force, and the slip generation torque, which is the minimum torque at which the torque limiter 13 causes slipping, is adjusted. The size has been adjusted.

  According to the torsion damper provided with such a torque limiter 13, when the input torque is less than the slip generation torque, the front case 11 and the disk member 5 are integrally rotated using the frictional force generated in the friction member 9, and the internal combustion engine Torque can be transmitted between the output shaft 10 of the engine and the input shaft 1 of the transmission. On the other hand, when the input torque is equal to or greater than the slip generation torque, the friction member 9 slides between the front case 11 and the ring member 12, and the transmission and the internal combustion engine connected via the torsion damper are used. It is possible to suppress an excessive load from acting on each part.

JP 2008-274969 A

  By the way, in the friction type torque limiter applied to the torsion damper or the like as described above, the frictional force acting on the friction member by adjusting the urging force of the elastic member (cone spring) sandwiched with the friction member. Is adjusted to adjust the magnitude of the slip generation torque. Therefore, when the clamping pressure for holding the friction member increases or decreases due to variations in characteristics (elastic coefficient, dimensions, etc.) of the elastic member and variations in the thickness of the members (friction member or ring member) held together with the elastic member. The magnitude of the slip generation torque changes. As a result, slippage does not occur when torque transmission should be suppressed, and it becomes impossible to protect the internal combustion engine and the transmission from excessive loads, or slipping occurs in the friction member when torque should be transmitted. May not be able to transmit an appropriate torque.

  The present invention has been made in view of the above circumstances, and its purpose is to cause variations in slip generation torque due to variations in characteristics of elastic members and variations in dimensions of friction members and the like sandwiched with the elastic members. An object of the present invention is to provide a torque limiter that can suppress this.

In the following, means for achieving the above object and its effects are described.
In the first aspect of the present invention, a friction member is interposed between a pair of members that transmit torque, and the friction member acting on the friction member by sandwiching the friction member together with the elastic member is used. In the friction type torque limiter in which the members are connected, an adjustment member capable of changing the thickness is sandwiched together with the friction member and the elastic member, and the adjustment member is combined with the friction member and the elastic member. The gist is that the thickness can be changed while being sandwiched .

  In the torque limiter in which the adjusting member capable of changing the thickness is sandwiched with the friction member and the elastic member as in the above configuration, the elastic member is sandwiched with the adjusting member as the thickness of the adjusting member is increased. The amount of deformation increases and the clamping pressure acting on the friction member increases. On the other hand, as the adjustment member is made thinner, the deformation amount of the elastic member is reduced and the clamping force acting on the friction member is reduced. That is, according to the first aspect of the present invention, the clamping pressure acting on the friction member can be adjusted by changing the thickness of the adjustment member.

  For this reason, even when there are variations in the characteristics (elastic coefficient, dimensions, etc.) of the elastic member and the dimensions of the friction member, etc. held together with the elastic member, the clamping pressure acting on the friction member by changing the thickness of the adjustment member By adjusting the offset, it is possible to cancel the change in the clamping pressure due to the variation and suppress the change in the magnitude of the slip generation torque. Therefore, according to the first aspect of the present invention, it is possible to suppress the occurrence of variations in the slip generation torque due to variations in the characteristics of the elastic members and variations in the dimensions of the friction members sandwiched with the elastic members. Will be able to.

  According to a second aspect of the present invention, in the torque limiter according to the first aspect, the friction member and the adjustment member have a disk shape, and the torque limiter includes the laminated friction member and the adjustment member. The adjusting member is sandwiched from the thickness direction, and the adjusting member has a sawtooth shape in which the inclined surface is inclined so that the thickness gradually increases toward one side in the circumferential direction. The gist of the present invention is that a pair of cam plates each having a cam surface provided on is combined in a face-to-face relationship so that the cam surfaces come into contact with each other.

  According to the above configuration, the cam plates combined in a face-to-face relationship are rotated relative to each other so that the cam plates slide along the inclined surfaces of the cam surfaces. Each inclined surface formed in a sawtooth shape on the cam surface is inclined so that the thickness gradually increases toward one side in the circumferential direction. Therefore, the cam plate is relatively rotated as described above, and each cam plate is By sliding along the inclined surface, the thickness of the adjusting member constituted by combining these cam plates is changed accordingly. That is, according to the structure of the said Claim 2, the clamping force which acts on a friction member can be adjusted by rotating the cam plate of the adjustment member clamped with the friction member and the elastic member relatively. become.

  According to a third aspect of the present invention, in the torque limiter according to the second aspect, the adjustment member is provided with a rotation suppressing means for suppressing a relative rotation of the cam plate due to the action of the clamping pressure. This is the gist.

  The adjusting member that is clamped together with the friction member and the elastic member acts so that the clamping pressure compresses the adjusting member in the thickness direction of the adjusting member, that is, in the direction of reducing the thickness of the adjusting member. . At this time, when the cam plate is relatively rotated in the direction of reducing the thickness of the adjusting member by the action of the clamping pressure, the clamping pressure acting on the friction member is reduced, and the slip generation torque is reduced. Therefore, as in the invention described in claim 3, it is desirable to provide a rotation suppressing means to suppress the relative rotation of the cam plate in the direction of reducing the thickness of the adjusting member due to the action of the clamping pressure. . By adopting such a configuration, it is possible to suppress the relative rotation of the cam plate due to the action of the clamping pressure, and to appropriately maintain the slip generation torque.

  According to a fourth aspect of the present invention, in the torque limiter according to the third aspect, the inclined surface of the cam plate is continuously provided with a small inclined surface that is inclined toward one side in the circumferential direction, similarly to the inclined surface. The stepped portion formed between the adjacent small inclined surfaces is formed in a sawtooth shape and meshes with the same stepped portion formed on the other cam plate combined face to face as the rotation suppressing means. Its gist is to function.

  According to a fifth aspect of the present invention, in the torque limiter according to the third aspect of the present invention, the inclined surface of the cam plate is subjected to corrugated processing so that undulations continue in the circumferential direction of the cam plate. In addition, the gist of the invention is to function as the rotation suppression means when the inclined surfaces processed into a wave shape mesh with each other.

  As a specific configuration of the rotation restraining means, as described in claim 4 above, each sloping surface formed on the cam plate is a small slanting toward one side in the circumferential direction similarly to the sloping surface. It is possible to adopt a configuration in which the inclined surfaces are formed in a sawtooth shape and the inclined surfaces in the sawtooth shape are engaged with each other. According to such a configuration, when the cam plate tries to relatively rotate in the direction of reducing the thickness of the adjusting member, the other cam in which the stepped portions existing between the adjacent small inclined surfaces are combined face to face. The cam plate meshes with the step portion of the plate, and the relative rotation of the cam plate due to the action of the clamping pressure is suppressed.

  In addition, as a specific configuration of the rotation restraining means, as shown in the above-mentioned claim 5, the cam plate is subjected to a wave-like process so that the undulations are continued in the circumferential direction, as described above. It is also possible to adopt a configuration in which the inclined surfaces processed into a wave shape are engaged with each other. When such a configuration is adopted, the undulating inclined surfaces are in mesh with each other, so that the relative rotation of the cam plate due to the action of the clamping pressure is suppressed.

  A sixth aspect of the invention includes the torque limiter according to any one of the first to fifth aspects of the present invention, and a damper that absorbs torsional vibration caused by fluctuations in input torque by elastic deformation of a coil spring. This is a torsion damper that connects the output shaft of the engine and the input shaft of the transmission.

  Specifically, the torque limiter according to the first to fifth aspects can be applied to a torsion damper that connects the output shaft of the internal combustion engine and the input shaft of the transmission as shown in the sixth aspect.

Sectional drawing of a torsion damper provided with the torque limiter concerning one Embodiment of this invention. The front view which fractures | ruptures and shows a part of torsion damper concerning the embodiment. Sectional drawing which expands and shows the torque limiter vicinity of the torsion damper concerning the embodiment. Explanatory drawing explaining the change aspect of the thickness of the adjustment member of the torque limiter concerning the embodiment. Explanatory drawing explaining the change aspect of the thickness of the adjustment member of the torque limiter concerning the embodiment. Explanatory drawing explaining the change aspect of the thickness of the adjustment member of the torque limiter concerning the embodiment. The schematic diagram which shows the example of a change of the adjustment member of the torque limiter concerning this invention. Sectional drawing which shows the example of a change of the torque limiter concerning this invention. Sectional drawing which shows the example of a change of the torque limiter concerning this invention. Sectional drawing which shows the example of a change of the torque limiter concerning this invention. Sectional drawing of a torsion damper provided with the conventional torque limiter.

  Hereinafter, an embodiment in which a torque limiter according to the present invention is embodied as a torque limiter provided in a torsion damper that connects a hybrid transaxle of a hybrid vehicle and an internal combustion engine will be described with reference to FIGS.

  FIG. 1 is a cross-sectional view of a torsion damper 100 including the torque limiter 120 according to the present embodiment, and FIG. 2 is a front view showing a part of the torsion damper 100 in a cutaway manner. 1 shows a cross section in the direction along the line AA in FIG.

  As shown in FIGS. 1 and 2, the torsion damper 100 according to the present embodiment has a disk shape. The inner peripheral portion is connected to the input shaft 200 of the hybrid transaxle indicated by a two-dot chain line on the left side of the center of FIG. 1, while the outer peripheral portion is indicated by a two-dot chain line on the right side of FIG. As described above, the engine is connected to the crankshaft 300 of the internal combustion engine via the flywheel 400, and transmits torque between the input shaft 200 and the crankshaft 300.

  As shown in FIG. 1, the hub 110 to which the input shaft 200 is connected has a cylindrical shape, and a spline 110 a with which the inserted input shaft 200 is engaged is formed on the inner peripheral surface thereof. In addition, a flange extending in the radial direction is provided on the outer peripheral surface of the hub 110, and a first support member 123 and a second support member 124 that sandwich friction plates 121 and 122 as friction members are provided on the flange with the rivet 111. It is fixed with.

  As shown in FIG. 1, the second support member 124 is bent so that the radially outer peripheral portion is separated from the first support member 123, and in the thickness direction of the torsion damper 100 (left and right direction in FIG. 1). A spline extending in the left-right direction in FIG. 1 is formed on the radially outer peripheral surface of the extending portion so that the first friction plate 121 meshes with the first friction plate 121 so as not to be relatively rotatable.

  On the outer peripheral side of the first support member 123 and the second support member 124, a ring-shaped intermediate member 112 connected to the flywheel 400 via a damper 130 is disposed as will be described later.

  As shown in FIG. 1, the first support member 123 and the second support member 124 mesh with a spline formed on the radially inner surface of the intermediate member 112 so as not to be relatively rotatable. The second friction plates 122 and the first friction plates 121 meshing with the splines of the second support member 124 are sandwiched and stacked alternately. In addition, between the first support member 123 and the second support member 124, together with the friction plates 121, 122, an adjustment member 150 capable of changing the thickness and a disc spring 125 are sandwiched. The magnitude of the frictional force generated between the friction plates 121 and 122 is adjusted by the biasing force of the spring 125.

  The intermediate member 112 engaged with the second friction plate 122 includes a disk member 131 extending toward the radially outer peripheral side, a first side wall member 126 and a second side wall member 127 extending toward the radially inner peripheral side, and rivets 113. It is fixed by.

  As shown in FIG. 1, the first side wall member 126 and the second side wall member 127 extend toward the radially inner peripheral side of the torsion damper 100 and surround a portion where the friction plates 121 and 122 are sandwiched. As shown in FIG. 1, the outer peripheral surface of the hub 110 and the inner peripheral side end of the first side wall member 126 face each other, and the outer peripheral surface of the hub 110 and the inner peripheral side end of the second side wall member 127. The oil seals 128 are press-fitted into the portions facing each other. Thus, an oil chamber 129 is formed that surrounds the portion where the friction plates 121 and 122 are sandwiched by the first side wall member 126 and the second side wall member 127 and the oil seal 128.

  The oil chamber 129 formed in this way is filled with lubricating oil, thereby forming a wet torque limiter 120 sandwiched in a state where the friction plates 121 and 122 are immersed in the lubricating oil. Yes.

  On the other hand, in the disk member 131 fixed to the intermediate member 112 together with the first side wall member 126 and the second side wall member 127, through holes 131a extending in the circumferential direction are spaced apart in the circumferential direction as shown in the lower part of FIG. Six are formed. Further, as shown in FIG. 1, the disk member 131 is sandwiched between the first housing member 132 and the second housing member 133 so as to be relatively rotatable.

  Six openings are respectively formed at positions corresponding to the through holes 131a in the storage members 132 and 133. The storage members 132 and 133 are shown in the lower part of FIG. As shown, the outer peripheral side portion is joined by a rivet 115. By joining the first housing member 132 and the second housing member 133 with the disc member 131 sandwiched in this way, the openings of the housing members 132 and 133 are communicated with each other, as shown in the upper part of FIG. An accommodation space 134 is formed at a position corresponding to the through hole 131a.

  Then, as shown in FIG. 2, the coil springs 135 are respectively placed inside the housing members 132, 133 and the disk member 131 so that the housing spaces 134 and the through holes 131 a overlap each other. One by one.

  Thus, in the torsion damper 100 of the present embodiment, the disk member 131 is rotatably sandwiched between the first housing member 132 and the second housing member 133, and a through hole 131 a formed in the disk member 131. The damper 130 is formed by accommodating the coil spring 135 inside the housing space 134 and the housing space 134 in an overlapped state.

  According to such a damper 130, when the accommodating members 132, 133 and the disk member 131 are rotated relative to each other so that the accommodating space 134 and the through hole 131a are displaced, the coil spring 135 is elastically deformed so as to be compressed. become. That is, when the disk member 131 connected to the hub 110 via the torque limiter 120 and the housing members 132 and 133 are rotated relative to each other by the torque fluctuation generated between the input shaft 200 and the crankshaft 300, the coil The spring 135 is elastically deformed. Thereby, the torsional vibration generated between the input shaft 200 and the crankshaft 300 is absorbed by the elastic deformation of the coil spring 135, and the torsional vibration generated by the torque fluctuation between the internal combustion engine and the hybrid transaxle is absorbed. Become.

  In addition, in the radial direction inner peripheral side end part of the 1st accommodating member 132 and the 2nd accommodating member 133, when the relative rotational phase difference of the disk member 131 and these accommodating members 132 and 133 becomes more than predetermined amount, A hysteresis mechanism 114 is provided that acts as a brake that prevents the relative rotational phase difference from increasing further.

  Hereinafter, the torque limiter 120 in the torsion damper 100 according to the present embodiment will be described in more detail with reference to FIGS. 3 is an enlarged cross-sectional view showing the vicinity of the torque limiter 120 in FIG. 1. FIGS. 4 to 6 are views of the adjusting member 150 sandwiched together with the friction plates 121 and 122 and the disc spring 125 in the torque limiter 120. FIG. It is explanatory drawing explaining the change aspect of thickness.

  As described above, in the torque limiter 120 according to the present embodiment, the adjustment member 150 is sandwiched between the support members 123 and 124 together with the disc spring 125 and the friction plates 121 and 122.

  As shown in FIG. 3, the first friction plate 121 meshing with the second support member 124 and the second friction plate 122 meshing with the intermediate member 112 are alternately stacked in the support member 123, 124. Among the friction plates 121 and 122 stacked as shown in the center right side of FIG. 3, a disc spring is interposed between the first friction plate 121 located on the rightmost side in FIG. 3 and the second support member 124. 125 is sandwiched.

  On the other hand, between the friction plates 121 and 122 stacked as shown in the center of FIG. 3, the second friction plate 122 located on the leftmost side in FIG. The adjustment member 150 is sandwiched.

  As shown in FIG. 4, the adjustment member 150 is configured by combining a first cam plate 151 and a second cam plate 152 having the same shape so as to face each other. 4 to 6 schematically show the cross-sectional structure of the adjusting member 150 in the direction along the line BB in FIG.

  As shown in FIG. 4, the first cam plate 151 is continuously provided with an inclined surface 153 inclined so as to gradually increase in thickness toward the upper side in FIG. 4, that is, toward one side in the circumferential direction of the first cam plate 151. Thus, a cam surface provided in a sawtooth shape is formed. As shown in FIG. 4, each inclined surface 153 includes three small inclined surfaces 153 a, which are inclined so that the thickness of the first cam plate 151 increases in the upward direction in FIG. 153b and 153c are formed in a sawtooth shape.

  That is, in the first cam plate 151, a sawtooth-shaped inclined surface 153 is formed by the first small inclined surface 153a, the second small inclined surface 153b, and the third small inclined surface 153c having different heights in the thickness direction. Thus, the sawtooth inclined surface 153 is further provided in a sawtooth shape continuously in the circumferential direction.

  Thus, in the first cam plate 151, the small inclined surfaces 153a, 153b, and 153c are arranged in a sawtooth shape. Therefore, the first step portion 153d exists between the first small inclined surface 153a and the second small inclined surface 153b adjacent to each other, and the second small inclined surface 153b and the third small inclined surface 153c adjacent to each other exist. A second step 153e exists between them, and a third step 153f exists between the third small inclined surface 153c and the first small inclined surface 153a adjacent to each other. As described above, since the inclined surface 153 is inclined so that the thickness of the first cam plate 151 increases toward the upper side in FIG. 4, the third step portion 153 f existing between the adjacent inclined surfaces 153. In that case, the step is larger than the first step portion 153d and the second step portion 153e.

  The second cam plate 152 combined with the first cam plate 151 has the same shape as the first cam plate 151. Therefore, as shown in FIG. 4, in the second cam plate 152 combined with the first cam plate 151 so as to face each other, the inclined surface is inclined so that the thickness gradually increases downward in FIG. 4. A cam surface in which 154 is provided in a sawtooth shape is formed.

  The inclined surface 154 includes a first small inclined surface 154a, a second small inclined surface 154b, and a third small inclined surface 154c that are inclined so that the thickness of the second cam plate 152 increases toward the lower side in FIG. The inclined surfaces 154 are formed in a sawtooth shape.

  In this way, even in the second cam plate 152, the small inclined surfaces 154a, 154b, and 154c are arranged in a sawtooth shape, similarly to the first cam plate 151. Therefore, the first step portion 154d exists between the first small inclined surface 154a and the second small inclined surface 154b adjacent to each other, and the second small inclined surface 154b and the third small inclined surface 154c adjacent to each other exist. A second step 154e exists between them, and a third step 154f exists between the third small inclined surface 154c and the first small inclined surface 154a adjacent to each other. Since the inclined surface 154 is inclined so that the thickness of the second cam plate 152 increases toward the lower side of FIG. 4 as described above, the third step portion 154f existing between the inclined surfaces 154 adjacent to each other. The step is larger than the first step portion 154d and the second step portion 154e.

4 to 6, for convenience of explanation, the adjustment member 150 is illustrated by providing a slight gap between the first cam plate 151 and the second cam plate 152 that are originally in contact with each other. .
The adjustment member 150 is configured by combining the first cam plate 151 and the second cam plate formed in this manner so as to face each other.

  Therefore, as shown in FIG. 4, the cam plates 151 and 152 are combined in such a phase that the inclined surfaces 153 of the first cam plate 151 and the inclined surfaces 154 of the second cam plate 152 face each other in front of each other. The first small inclined surface 153a and the third small inclined surface 154c are in contact with each other, the second small inclined surface 153b and the second small inclined surface 154b are in contact with each other, and the third small inclined surface 153c and the first small inclined surface 153c are in contact with each other. It will be in the 1st contact state which the small inclined surface 154a contact | abuts.

  In the first contact state, as shown in FIG. 4, the first step portion 153d and the second step portion 154e on the inclined surfaces 153 and 154 engage with each other, and the second step portion. 153e and the first step 154d are engaged, and the third step 153f and the third step 154f are engaged.

Further, in the first contact state, the thickness of the adjustment member 150 is “T1” as shown in the lower part of FIG.
When the first cam plate 151 and the second cam plate 152 are rotated relative to each other from the first contact state as indicated by an arrow in FIG. Sliding along the inclined surfaces 153 and 154, the adjustment member 150 first shifts to the second contact state shown in FIG.

  In the second contact state, as shown in FIG. 5, the second small inclined surface 153b and the third small inclined surface 154c are in contact with each other, and the third small inclined surface 153c and the second small inclined surface 154b are in contact. Are in contact with each other while the first small inclined surface 153a and the first small inclined surface 154a face each other.

  In the second contact state, as shown in FIG. 5, the first step portion 153d and the third step portion 154f on each of the inclined surfaces 153 and 154 engage with each other, and the second step portion 153e and the second step 154e are engaged, and the third step 153f and the first step 154d are engaged.

In the second contact state, the thickness of the adjustment member 150 becomes “T2” larger than “T1” as shown in the lower part of FIG.
Further, when the first cam plate 151 and the second cam plate 152 are relatively rotated from the second contact state as indicated by an arrow in FIG. 5, the cam plates 151 and 152 are mutually connected. Sliding along the inclined surfaces 153 and 154 of the cam surface, the adjustment member 150 shifts to the third contact state shown in FIG.

  As shown in FIG. 6, in the third contact state, the third small inclined surface 153c and the third small inclined surface 154c are in contact, while the first small inclined surface 153a and the second small inclined surface 154b. In addition, the second small inclined surface 153b and the first small inclined surface 154a are separated from each other while facing each other.

  In the third contact state, as shown in FIG. 6, the second step portion 153e and the third step portion 154f on each of the inclined surfaces 153 and 154 engage with each other, and the third step portion 153f and the second stepped portion 154e are engaged with each other.

Further, in the third contact state, the thickness of the adjustment member 150 becomes “T3” which is larger than “T2” as shown in the lower part of FIG.
When the first cam plate 151 and the second cam plate 152 are further rotated relative to each other as shown by arrows in FIG. 6 from this third contact state, the inclined surfaces 153 and 154 face each other. In order to get over 153 and 154, the adjustment member 150 returns to the first contact state shown in FIG.

  As described above, in the adjustment member 150, the first cam plate 151 and the second cam plate 152 are rotated relative to each other so that the contact state of the cam plates 151 and 152 is changed from the first contact state to the first contact state. The second contact state, the second contact state to the third contact state, and the third contact state to the first contact state. As the contact state changes, the adjustment member 150 has three thicknesses from “T1” to “T2”, from “T2” to “T3”, and from “T3” to “T1”. ("T1", "T2", "T3").

  In the torque limiter 120 according to the present embodiment, the adjusting member 150 capable of changing the thickness by relatively rotating the cam plates 151 and 152 in this manner is provided with the disc spring 125 and the friction plate 121, Along with 122, support members 123 and 124 are used. Therefore, the amount of deformation of the disc spring 125 sandwiched with the adjusting member 150 is changed by relatively rotating the cam plates 151 and 152 and changing their thicknesses while being sandwiched between the support members 123 and 124. The biasing force acting on the friction plates 121 and 122, that is, the clamping pressure acting on the friction plates 121 and 122 can be adjusted.

  In the torque limiter 120 of the present embodiment, the cam plates 151 and 152 can be relatively rotated while being sandwiched between the support members 123 and 124 as shown in FIG. In addition, a recess 151 a is formed on the outer peripheral surface of the first cam plate 151.

  According to such a configuration, in the process of assembling the torsion damper 100, the flange of the hub 110 and each support member 123 with the friction plates 121, 122, the disc spring 125, and the adjustment member 150 sandwiched between the support members 123, 124. , 124 are joined by the rivet 111 and before the intermediate member 112 and the second friction plate 122 are engaged with each other, a jig is engaged with the recess 151a to rotate the first cam plate 151. . When the first cam plate 151 is rotated using the jig in this manner, the first cam plate 151 and the second cam plate 152 are relatively rotated while being sandwiched between the support members 123 and 124. Thus, the thickness of the adjustment member 150 can be changed.

  In addition, the structure for rotating the cam plates 151 and 152 is not limited to such a structure, and can be changed as appropriate. For example, it is possible to employ a configuration in which a convex portion is provided on the outer peripheral surface of the first cam plate 151 and the first cam plate 151 is rotated by grasping the convex portion.

According to the embodiment described above, the following effects can be obtained.
(1) Since the adjusting member 150 capable of changing the thickness is sandwiched with the friction plates 121 and 122 and the disc spring 125, the adjusting member 150 is sandwiched with the adjusting member 150 as the thickness of the adjusting member 150 is increased. Further, the amount of deformation of the disc spring 125 increases, and the clamping pressure acting on the friction plates 121 and 122 increases. On the other hand, as the thickness of the adjustment member 150 is reduced, the amount of deformation of the disc spring 125 is reduced, and the clamping force acting on the friction plates 121 and 122 is reduced. In other words, the clamping force acting on the friction plates 121 and 122 can be adjusted by changing the thickness of the adjusting member 150.

  Therefore, even when there are variations in the characteristics (elastic coefficient, dimensions, etc.) of the disc spring 125 and the dimensions of the friction plates 121, 122 and the support members 123, 124, the thickness of the adjustment member 150 is changed to change the friction plate 121. , 122 can be adjusted to cancel the change in the pinching pressure due to the variation, and to suppress the change in the magnitude of the slip generation torque. Therefore, it is possible to suppress the occurrence of variations in the slip generation torque due to variations in the characteristics of the disc spring 125 and variations in the dimensions of the friction plates 121, 122 and the like sandwiched with the disc spring 125.

  (2) By rotating the cam plates 151 and 152 combined in a face-to-face relationship, the cam plates 151 and 152 slide along the cam surfaces as described above. The inclined surfaces 153 and 154 formed in a sawtooth shape on the cam surface are inclined so that the thickness gradually increases toward one side in the circumferential direction. Therefore, the cam plates 151 and 152 are relatively rotated as described above, and the cam plates 151 and 152 are slid along the inclined surfaces 153 and 154, so that the cam plates 151 and 152 are combined. As a result, the thickness of the adjusting member 150 is changed. In other words, by rotating the cam plates 151 and 152 of the adjustment member 150 held together with the friction plates 121 and 122 and the disc spring 125, the adjustment member 150 remains in the state of being held between the support members 123 and 124. The thickness can be changed, and the clamping pressure acting on the friction plates 121 and 122 can be adjusted.

  (3) The adjusting member 150 held together with the friction plates 121 and 122 and the disc spring 125 has a holding pressure so that the adjusting member 150 is compressed in the thickness direction, that is, the thickness of the adjusting member 150 is increased. Acts in the direction of thinning. At this time, when the cam plates 151 and 152 are relatively rotated in the direction in which the thickness of the adjustment member 150 is reduced by the action of the clamping force (the direction opposite to the arrows in FIGS. 4 to 6), the friction plates 121 and The pinching force acting on 122 is reduced, and the slip generation torque is reduced. On the other hand, in the above-described embodiment, the inclined surfaces 153 and 154 of the cam plates 151 and 152 are provided with a small inclined surface in a sawtooth shape, and the stepped portions existing between the small inclined surfaces are engaged with each other. ing. For this reason, the cam plates 151 and 152 are prevented from rotating relative to each other by the action of the clamping pressure due to the engagement of these stepped portions, and the slip generation torque can be suitably maintained.

In addition, the said embodiment can also be implemented with the following forms which changed this suitably.
In the above embodiment, the example in which the disc spring 125 is adopted as the elastic member sandwiched together with the friction plates 121 and 122 is shown, but the elastic member is not limited to the disc spring. That is, the elastic member only needs to be able to be elastically deformed when being clamped together with the friction plates 121 and 122 and to adjust the clamping force acting on the friction plates 121 and 122. A coil spring or the like can also be employed.

  In the embodiment, the three small inclined surfaces 153a, 153b, and 153c are formed on the inclined surface 153, and the three small inclined surfaces 154a, 154b, and 154c are formed on the inclined surface 154, and the adjustment member The torque limiter 120 capable of changing the thickness of 150 in three stages is illustrated. On the other hand, the number of small inclined surfaces formed on the inclined surfaces 153 and 154 is not limited to three. That is, the number of small inclined surfaces formed on the inclined surfaces 153 and 154 is the same as the number of small inclined surfaces formed on the inclined surface 153 and the number of small inclined surfaces formed on the inclined surface 154. There may be two or four or more.

  Since the thickness of the adjustment member 150 can be changed in multiple steps as the number of small inclined surfaces formed on the inclined surfaces 153 and 154 increases, the friction plate 121, In order to finely adjust the clamping force acting on 122, it is desirable to increase the number of small inclined surfaces formed on the inclined surfaces 153 and 154.

  In the above embodiment, the inclined surfaces 153 and 154 are formed in the inclined surfaces 153 and 154 so that the stepped portions existing between the small inclined surfaces mesh with each other and function as a rotation suppressing means. The structure to perform was illustrated. On the other hand, the structure of the rotation suppressing means for suppressing the relative rotation of the cam plates 151 and 152 due to the action of the clamping pressure can be changed as appropriate. For example, as shown in FIG. 7, it is possible to adopt a configuration in which the inclined surfaces 153 and 154 of the cam plates 151 and 152 are waved so that the undulations continue in the circumferential direction of the cam plates 151 and 152. . If such a configuration is adopted, the undulating inclined surfaces 153 and 154 mesh with each other, so that the relative rotation of the cam plates 151 and 152 due to the action of the clamping pressure is suppressed.

  In the above embodiment, the portion where the friction plates 121 and 122 are sandwiched is surrounded by the side wall members 126 and 127 to form the oil chamber 129, and the friction chambers 121 and 122 are filled with the lubricating oil. A configuration in which the present invention is applied to a wet torque limiter 120 sandwiched between the two is shown. In contrast, the present invention is not limited to wet torque limiters. That is, the present invention can also be applied to a dry torque limiter in which the friction plates 121 and 122 are not immersed in the lubricating oil.

  In the above embodiment, the friction plates 121 and 122 are provided as the friction members, and the first friction plate 121 that rotates integrally with one member (hub 110) and the other member (of the pair of members) The configuration in which the present invention is applied to the torque limiter 120 in which the disk member 131) and the second friction plates 122 that rotate integrally are alternately stacked and sandwiched is illustrated. On the other hand, the present invention is not limited to the torque limiter having such a configuration. For example, as in the conventional torque limiter 13 shown in FIG. 11, the friction member 9 fixed to one member (disk member 5) is rotated integrally with the other member (front case 11 and rear case 14). In the torque limiter clamped by the moving ring member 12, the adjusting member 150 can be disposed between the friction member 9 and the ring member 12.

Even in such a configuration, by changing the thickness of the adjustment member 150, the deformation amount of the disc spring 15 can be changed, and the clamping force acting on the friction member 9 can be adjusted.
-If the adjustment member 150 is clamped with the friction plate which is a friction member, and the elastic member which urges | biases this, the arrangement | positioning position can be changed suitably. For example, as shown in FIG. 8, a configuration in which the adjustment member 150 is provided between the friction plates 121 and 122 and the disc spring 125 that are stacked may be employed.

-Moreover, as FIG. 9 shows, the structure which provides the adjustment member 150 between the 2nd support member 124 and the disk spring 125 is also employable.
Further, a configuration in which the adjusting member 150 is disposed between the friction plates 121 and 122 stacked as shown in FIG.

  In the above-described embodiment, the configuration in which the torque limiter according to the present invention is provided in the torsion damper 100 that couples the hybrid transaxle of the hybrid vehicle and the internal combustion engine is illustrated. However, the torque limiter according to the present invention is the hybrid transaxle and the internal combustion engine. The present invention is not limited to the torsion damper that connects the two. For example, the torque limiter of the present invention can be applied to a torsion damper or the like that connects an automatic transmission and an internal combustion engine.

  -In the above-mentioned embodiment, although the example which applied torque limiter 120 concerning the present invention to the torque limiter of torsion damper 100 was shown, the torque limiter of the present invention is not limitedly applied to a torsion damper. . That is, the present invention can be applied to any friction type torque limiter that suppresses excessive torque transmission due to sliding of the friction member, so that no damper is provided and only the function of suppressing excessive torque transmission is provided. The present invention can also be applied to a torque transmission mechanism having

DESCRIPTION OF SYMBOLS 100 ... Torsion damper, 110 ... Hub, 110a ... Spline, 111 ... Rivet, 112 ... Intermediate member, 113 ... Rivet, 114 ... Hysteresis mechanism, 115 ... Rivet, 120 ... Torque limiter, 121 ... First friction plate, 122 ... First 2 friction plates, 123 ... first support member, 124 ... second support member, 125 ... disc spring, 126 ... first side wall member, 127 ... second side wall member, 128 ... oil seal, 129 ... oil chamber, 130 ... damper 131 ... Disc member, 131a ... Through hole, 132 ... First accommodation member, 133 ... Second accommodation member, 134 ... Accommodation space, 135 ... Coil spring, 150 ... Adjustment member, 151 ... First cam plate, 152 ... First 2 cam plates, 153 ... inclined surfaces, 153a, 153b, 153c ... small inclined surfaces, 153d, 153e, 153f ... step Department, 154 ... inclined surface, 154a, 154b, 154c ... small inclined surfaces, 154d, 154e, 154 f ... stepped portion, 200 ... input shaft, 300 ... Crankshaft, 400 ... flywheel.

Claims (6)

A friction type torque in which a friction member is interposed between a pair of members transmitting torque and the pair of members are connected by utilizing a frictional force acting on the friction member by sandwiching the friction member together with an elastic member. In the limiter,
An adjustment member capable of changing the thickness is sandwiched together with the friction member and the elastic member ,
A torque limiter characterized in that the adjustment member can be changed in thickness while being held together with the friction member and the elastic member . The torque limiter according to claim 1,
The friction member and the adjustment member have a disk shape,
The torque limiter sandwiches the laminated friction member and the adjustment member together with the elastic member from the thickness direction,
The adjusting member has a pair of cam plates each having a cam surface in which an inclined surface inclined so as to gradually increase in thickness toward one side in the circumferential direction is provided in a sawtooth shape continuously in the circumferential direction. A torque limiter characterized in that the cam surfaces are combined so as to face each other. The torque limiter according to claim 2,
The torque limiter is characterized in that the adjustment member is provided with a rotation suppressing means for suppressing relative rotation of the cam plate due to the action of the clamping pressure. The torque limiter according to claim 3,
On the inclined surface of the cam plate, similarly to the inclined surface, a small inclined surface that is inclined toward one side in the circumferential direction is continuously formed in a sawtooth shape,
Torque characterized in that a step portion existing between adjacent small inclined surfaces meshes with the same step portion formed on the other cam plate combined face to face, thereby functioning as the rotation suppressing means. limiter. The torque limiter according to claim 3,
On the inclined surface of the cam plate, a wavy process is applied so that undulations continue in the circumferential direction of the cam plate,
A torque limiter that functions as the rotation restraining means when the inclined surfaces processed into a wave shape mesh with each other. A torque limiter according to any one of claims 1 to 5, and a damper that absorbs torsional vibration due to fluctuations in input torque by elastic deformation of a coil spring,
A torsion damper that connects an output shaft of an internal combustion engine and an input shaft of a transmission.

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