JP2005207475A - Clutch unit - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a clutch unit capable of preventing component parts from being damaged by over-load even when large torque equal to or exceeding the set value to signify over-load is applied. <P>SOLUTION: The clutch unit has an input outer ring 1 and an output inner ring 12 which are installed with possibility of rotating in the regular and the reverse direction relative to a housing 16, a roller 13 able to make engagement and disengagement interposed between the input outer ring 1 and the output inner ring 12, and a retainer 14 to retain the roller 13, and using the retainer 14, the roller 13 is changed over between engagement and disengagement by controlling the rotational phase difference between the input outer ring 1 and the retainer 14 through application of a frictional resistance to the retainer 14 for the rotation of the retainer 14 relative to the housing 16 through the relative rotation with the input outer ring 1, wherein the output inner ring 12 is split into two members 12a and 12b, which are joined together so that a slip is generated between their joining surfaces 10a and 10b when an excessive torque is applied. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention is used for, for example, an electric slide door, an electric back door, an electric seat, a power window, an electric steering, etc., and transmits only rotational torque in one direction from the input side to the output side, while the positive side from the output side. The present invention relates to a clutch unit having a reverse input blocking function that blocks rotational torque in both reverse directions and does not transmit the torque to the input side.

  For example, it is used for electric sliding doors, electric back doors, electric seats, power windows, electric steering, etc., and only rotational torque in one direction from the input side is transmitted to the output side, while rotational torque in both forward and reverse directions is cut off from the output side. There are various types of clutch units having a reverse input blocking function that does not transmit to the input side.

  FIGS. 8A and 8B show an example of a clutch unit having a reverse input blocking function, for example. The clutch unit includes an input outer ring 1 as an input side rotation member, an output inner ring 2 as an output side rotation member, a roller 3 as a torque transmission member, a cage 4 that holds the roller 3, and a cage 4, a centering spring 5 as an elastic member for positioning 4, a housing 6 as a stationary member, and a sliding spring 7 as a rotational resistance applying means for applying a frictional resistance to the cage 4 against the rotation of the cage 4. And the main part is composed.

  The aforementioned input outer ring 1 is rotatably supported by a housing 6 via a bearing 8, and a wedge space is formed on the inner peripheral surface of the output outer ring 1 symmetrically in both forward and reverse rotation directions with the outer peripheral surface of the output inner ring 2. The cam surfaces 9 are formed at equal intervals in the circumferential direction. A sliding spring 7 slidably mounted on the housing 6 has a shape that can engage with a protrusion (not shown) formed on the cage 4 in the circumferential direction.

  The aforementioned output inner ring 2 is rotatably supported on the housing 6 via a bearing 8 and is arranged coaxially with the input outer ring 1. The cage 4 accommodates and arranges the rollers 3 in a plurality of pockets formed at equal intervals in the circumferential direction, and a centering spring 5 is fitted to a part of the pockets and the input outer ring 1. . These input outer ring 1, output inner ring 2, roller 3, cage 4, centering spring 5 and sliding spring 7 are accommodated in a housing 6.

  In this clutch unit, in the initial state where the rotational torque does not act on the input outer ring 1, the roller 3 is caused to act on the cam surface 9 of the input outer ring 1 by the action of the centering spring 5 fitted to the input outer ring 1 and the cage 4. It is held in a state located in the center in the circumferential direction. At this time, a gap is set between the roller 3 and the input outer ring 1. The cage 4 provides a frictional resistance with the housing 6 by a sliding spring 7.

  Even if rotational torque acts on the output inner ring 2 in this state, the roller 3 held by the cage 4 positioned by the centering spring 5 continues to be positioned at the circumferential center of the wedge space. Since there is a gap between the outer ring 1, the input outer ring 1 and the output inner ring 2 do not engage in the rotational direction, the output inner ring 2 idles in both forward and reverse directions, and the rotational torque input to the output inner ring 2 1 is interrupted without being transmitted.

  On the other hand, when the forward rotation torque or the reverse rotation torque acts on the input outer ring 1, the input outer ring 1 tries to rotate. At this time, since the retainer 4 is connected to the input outer ring 1 by the centering spring 5, the cage 4 starts rotating together with the input outer ring 1. When the retainer 4 rotates, the protrusion of the retainer 4 comes into contact with the sliding spring 7, and the sliding spring 7 rotates around in this state. The sliding spring 7 receives a sliding frictional resistance with the housing 6, and this sliding frictional resistance becomes a rotational resistance of the cage 4 through the protrusions.

Here, since the rotational resistance of the cage 4 due to the sliding frictional resistance of the sliding spring 7 is larger than the elastic force of the centering spring 5, the centering spring 5 is elastically deformed, and accordingly, the rotational phase difference is applied to the cage 4. Due to the rotational phase difference, the roller 3 moves relative to the input outer ring 1 and is engaged in the wedge space, and the rotational torque input to the input outer ring 1 is transmitted to the output inner ring 2 (for example, , See Patent Document 1).
JP 2003-120715 A

  By the way, in the clutch unit described above, when the input outer ring 1 starts to rotate, the rotation of the cage 4 receiving sliding friction resistance with the housing 6 from the sliding spring 7 is delayed, and the pocket of the cage 4 is retained. The held roller 3 is engaged with the wedge space between the cam surface 9 of the input outer ring 1 and the outer diameter surface of the output inner ring 2, so that rotational torque is transmitted.

  Here, when this clutch unit is used as an outfitting clutch such as an electric slide door, pinching or the like occurs during driving of the electric slide door, and thereby a large torque (a set value or more) is input to the input outer ring 1. Then, there is a possibility that the torque exceeding the set value becomes an overload, and parts such as the roller 3, the input outer ring 1 and the output inner ring 2 constituting the roller clutch portion are damaged.

  Therefore, the present invention has been proposed in view of the above-described problems, and the object of the present invention is that even when a large torque exceeding a set value that causes an overload is input, the component of the component due to the overload is It is an object of the present invention to provide a clutch unit that can prevent damage.

  As technical means for achieving the above object, the present invention provides an input-side rotating member and an output-side rotating member, which are arranged so that they can freely rotate in the forward and reverse directions with respect to a stationary member. A cage is provided with respect to rotation of the cage with respect to the stationary side member through a relative rotation with respect to the input side rotation member by a cage that holds the torque transmission member that can be engaged and disengaged therebetween and holds the torque transmission member. A clutch unit that switches between engagement and disengagement of the torque transmission member by controlling a rotational phase difference between the input side rotating member and the cage by applying a frictional resistance, the clutch unit of the input side rotating member and the output side rotating member One of the two members is divided into two members, and the two members are joined so that slip occurs between the respective joint surfaces when an excessive torque is applied.

  When the clutch unit according to the present invention is used as a clutch for an outfitting system component such as an electric slide door, even if an excessive torque is applied due to pinching or the like while the electric slide door is being driven, By adopting a structure that causes slippage on the pressure contact surface with the member, it is possible to avoid excessive torque from acting on components such as the roller, the input outer ring, and the output inner ring that constitute the roller clutch portion.

  Of the above-described two members in the present invention, it is desirable to have a structure in which an elastic member is fitted to one member and the other member is pressed against one member by the elastic force of the elastic member. Of the two members, one member is a hollow member, and the other member is a shaft member, and a flange formed on the shaft end of the shaft member is joined to the inner diameter end of the hollow member, and the shaft member The flange surface and the inner diameter end surface of the hollow member are preferably sliding surfaces. Here, as the above-mentioned “elastic member”, a wave spring or the like is suitable. Note that the above-described sliding surface can be tapered with respect to the axial direction.

  In addition, the present invention can be structured such that one member is press-fitted into the other member and both are connected by a locking member, and one of the two members is a hollow member. And the other member is a shaft-shaped member, and a flange formed at the shaft end of the shaft-shaped member is joined to the inner diameter end of the hollow member, and the outer diameter surface of the shaft-shaped member and the inner diameter surface of the hollow member are A sliding surface is preferred. Here, as the above-described “locking member”, a retaining ring or the like is suitable. Note that the above-described sliding surface can be tapered with respect to the axial direction.

  When the clutch unit according to the present invention is used as a clutch for an outfitting system component such as an electric slide door, even if an excessive torque is applied due to pinching or the like while the electric slide door is being driven, By using a structure that causes slippage on the pressure contact surface with the cylindrical member, it is possible to prevent damage to parts such as the roller, the input outer ring, and the output inner ring that constitute the roller clutch portion due to excessive torque. it can. In addition, since the above-described structure exhibits a torque limiter function, the clutch portion can be downsized in strength, and the external motor and supporting parts can be downsized.

  Embodiments of the clutch unit according to the present invention will be described in detail below. The same parts as those in FIGS. 8A and 8B are denoted by the same reference numerals.

  The clutch unit of the first embodiment shown in FIGS. 1A and 1B includes an input outer ring 1 as an input side rotating member, an output inner ring 12 as an output side rotating member, and a roller 3 as a torque transmission member. The retainer 4 for holding the roller 3, the centering spring 5 as an elastic member for positioning the retainer 4, the housing 6 as a stationary member, and the retainer 4 against the rotation of the retainer 4 The main part is composed of a sliding spring 7 as a rotational resistance applying means for applying a frictional resistance.

  The aforementioned input outer ring 1 is rotatably supported by a housing 6 via a bearing 8, and a wedge space is formed on the inner peripheral surface thereof symmetrically in both forward and reverse rotation directions with the outer peripheral surface of the output inner ring 12. The cam surfaces 9 are formed at equal intervals in the circumferential direction. The input outer ring 1 is directly connected to a drive unit (not shown) composed of, for example, an electric motor and a speed reduction mechanism, or is indirectly connected to the drive unit via power transmission means such as a chain. A sliding spring 7 slidably mounted on the housing 6 has a shape that can engage with a protrusion (not shown) formed on the cage 4 in the circumferential direction.

  The cage 4 accommodates and arranges the rollers 3 in a plurality of pockets formed at equal intervals in the circumferential direction, and a centering spring 5 is fitted to a part of the pockets and the input outer ring 1. These input outer ring 1, output inner ring 12, roller 3, cage 4, centering spring 5 and sliding spring 7 are housed in a housing 6.

  The above-mentioned output inner ring 12 has a hollow member 12a having an outer diameter surface that forms a wedge space opposite to the cam surface 9 of the input outer ring 1, and is rotatably supported on the housing 6 via a bearing 8. It is composed of two members including a shaft-shaped member 12b inserted into the hollow-shaped member 12a and integrally having a flange at the inner shaft end. In the output inner ring 12, the elastic member 20 is fitted into an annular groove formed in the large-diameter hole of the hollow member 12a, thereby connecting the hollow member 12a and the shaft-like member 12b with the elastic force. . That is, the flange surface of the shaft-shaped member 12b is pressed against the inner diameter end surface of the hollow-shaped member 12a by the elastic member 20, and the pressure-contact surfaces (sliding surfaces) 10a, 10b between the hollow-shaped member 12a and the shaft-shaped member 12b when excessive torque is applied. It has a structure that causes slipping.

  In the first embodiment described above, the case where the output inner ring 12 is divided into two members 12a and 12b has been described. However, the input outer ring can be divided into two members. 2 (a) and 2 (b) show a second embodiment in which the input outer ring 11 is constituted by two members 11a and 11b. The other component parts are the same as those in the first embodiment, and the output inner ring 2 is the same as in the conventional case, so the duplicated explanation is omitted.

  The input outer ring 11 in this second embodiment has a cam surface 9 that forms a wedge space facing the outer diameter surface of the output inner ring 2, and is a hollow shape that is rotatably supported by a housing 6 via a bearing 8. It is composed of two members including a member 11a and a shaft-shaped member 11b which is inserted into the hollow-shaped member 11a and integrally has a flange at the inner shaft end. In this input outer ring 11, the elastic member 20 is fitted into an annular groove formed in the large-diameter hole of the hollow member 11a, thereby connecting the hollow member 11a and the shaft-like member 11b with the elastic force. . That is, the flange surface of the shaft-shaped member 11b is pressed against the inner diameter end surface of the hollow-shaped member 11a by the elastic member 20, and the pressure-contact surfaces (sliding surfaces) 10a, 10b between the hollow-shaped member 11a and the shaft-shaped member 11b when an excessive torque is applied. It has a structure that causes slipping.

  As a modification of the first embodiment described above, FIGS. 3A and 3B show a third embodiment in which the output inner ring 12 ′ is divided into two members 12 a ′ and 12 b ′. In the third embodiment, in the output inner ring 12 ′ composed of two members, a hollow member 12a ′ and a shaft member 12b ′, the pressure contact surface of the hollow member 12a ′ and the shaft member 12b ′ by the elastic member 20 (Sliding surfaces) 10a 'and 10b' are tapered so that a slip is generated between the tapered pressure contact surfaces 10a 'and 10b' of the hollow member 12a 'and the shaft-like member 12b' when an excessive torque is applied. .

  The third embodiment described above is applied to the first embodiment in which the output inner ring 12 is divided into two members, the hollow member 12a and the shaft member 12b, but the input outer ring 11 is hollow. The present invention can also be applied to the second embodiment configured by two members of the member 11a and the shaft-shaped member 11b.

  In the clutch unit in the first to third embodiments, in the initial state where the rotational torque does not act on the input outer ring 1 (11), the centering spring 5 fitted to the input outer ring 1 (11) and the cage 4 By the action, the roller 3 is held in a state of being positioned at the center in the circumferential direction of the cam surface 9 of the input outer ring 1 (11). At this time, a gap is set between the roller 3 and the input outer ring 1 (11). The cage 4 provides a frictional resistance with the housing 6 by a sliding spring 7.

  In this state, even if rotational torque acts on the output inner rings 12, 12 '(2), the roller 3 held by the cage 4 positioned by the centering spring 5 continues to be positioned at the circumferential center of the wedge space. Since there is a gap between the roller 3 and the input outer ring 1 (11), the input outer ring 1 (11) and the output inner rings 12, 12 ′ (2) do not engage in the rotation direction, and the output inner rings 12, 12 ′ ( 2) idles in both forward and reverse directions, and the rotational torque input to the output inner ring 12, 12 '(2) is cut off without being transmitted to the input outer ring 1 (11).

  On the other hand, when the forward rotation torque or the reverse rotation torque acts on the input outer ring 1 (11), the input outer ring 1 (11) tends to rotate. At this time, since the retainer 4 is connected to the input outer ring 1 (11) by the centering spring 5, it starts rotating together with the input outer ring 1 (11). When the retainer 4 rotates, the protrusion of the retainer 4 comes into contact with the sliding spring 7, and the sliding spring 7 is rotated in that state. The sliding spring 7 receives a sliding frictional resistance with the housing 6, and this sliding frictional resistance becomes a rotational resistance of the cage 4 through the protrusions.

  Here, since the rotational resistance of the cage 4 due to the sliding frictional resistance of the sliding spring 7 is larger than the elastic force of the centering spring 5, the centering spring 5 is elastically deformed, and the rotational phase difference is applied to the cage 4 accordingly. Due to the rotational phase difference, the roller 3 moves relative to the input outer ring 1 (11) and is engaged in the wedge space, and the rotational torque input to the input outer ring 1 (11) , 12 ′ (2).

  When this clutch unit is used as a clutch for an outfitting system component such as an electric slide door, even if an excessive torque is applied due to being caught during driving of the electric slide door, the hollow members 12a, 12a ′ (11a) and the shaft members 12b, 12b ′ (11b) and the pressure contact surfaces 10a, 10a ′ and 10b, 10b ′ have a structure that causes slippage, so that the roller constituting the roller clutch portion by the action of excessive torque 3. It is possible to prevent damage to parts such as the input outer ring 1 (11) and the output inner ring 12, 12 ′ (2).

  Although the first to third embodiments described above are applied to the conventional clutch unit shown in FIGS. 8A and 8B, other types of clutch units described below are also applicable. Applicable.

  4 (a) and 4 (b) show a clutch unit in the fourth embodiment. In this clutch unit, the outer diameter surface of the output inner ring 22 is a polygonal surface 25, the inner diameter surface of the input outer ring 21 is a cylindrical surface 26, the output inner ring 22, the polygonal surface 25, and the cylindrical surface 26 of the input outer ring 21. A cage 24 is inserted between them, and a roller 23 is held in a pocket provided in the cage 24, and an electromagnetic clutch 27 is incorporated.

  When the electromagnetic clutch 27 is not energized, the clutch unit urges an elastic force for centering the output inner ring 22 and the cage 24 by the centering spring 29, and when the electromagnetic clutch 27 is energized, the input outer ring 21 is energized. The rotor 28b rotated and fixed via the rotor guide 28a is attracted to the armature 30a, and the rotation of the input outer ring 21 is transmitted to the cage 24 via the plate 30b that rotates and fixes the armature 30a and the cage 24. Has been.

  In the fourth embodiment, as in the second embodiment described above, the input outer ring 21 is composed of two members, a hollow member 21a and a shaft-like member 21b, and the elastic member 20 is provided on the inner diameter of the hollow member 21a. By fitting, the flange surface of the shaft-shaped member 21b is pressed against the inner diameter end surface of the hollow-shaped member 21a with its elastic force, and the pressure-contact surface (sliding surface) between the hollow-shaped member 21a and the shaft-shaped member 21b when excessive torque is applied. 10a and 10b are configured to cause slippage.

  FIGS. 5A and 5B show a clutch unit in the fifth embodiment. In this clutch unit, a cage 34 is used as an input side rotation member, a polygonal cam surface 39 is provided on the outer diameter surface of the output inner ring 32, and a pair of rollers 33 is inserted into each pocket of the cage 34 and the rollers An elastic member 40 that biases the separation force between them is arranged to fix the outer ring 31 to a stationary system, and the reverse torque is blocked by the roller 33 locking to the outer ring 31 when the rotational torque reversely input to the output inner ring 32 is locked. It has a function.

  In the fifth embodiment, the output inner ring 32 is constituted by two members, a hollow member 32a and a shaft-like member 32b, and the elastic member 20 is fitted to the inner diameter of the hollow member 32a. Thus, the flange surface of the shaft-shaped member 32b is pressed against the inner diameter end surface of the hollow-shaped member 32a, and slippage occurs between the pressure-contact surfaces (sliding surfaces) 10a and 10b of the hollow-shaped member 32a and the shaft-shaped member 32b when an excessive torque is applied. Yes.

  6A and 6B show a clutch unit in the sixth embodiment. In this clutch unit, the inner diameter surface of the input outer ring 41 is a cam surface 49, the outer diameter surface of the output inner ring 42 is a cylindrical surface 50, and the cage 44 is fixed by an elastic member 48 that is rotationally fixed to a housing 46. When the outer ring 41 is swung and rotated, the roller 43 held in the pocket of the cage 44 meshes between the cam surface 49 of the input outer ring 41 and the cylindrical surface 50 of the output inner ring 42, thereby transmitting torque to the output inner ring 42. When no rotational torque is input to the input outer ring 41, the input outer ring 41, the retainer 44, and the roller 43 are returned to their original positions by the elastic force of the elastic member 48.

  In this sixth embodiment, the output inner ring 42 is constituted by two members, a hollow member 42a and a shaft-like member 42b, and the elastic member 20 is fitted to the inner diameter of the hollow member 42a, so that the elastic force is used. Thus, the flange surface of the shaft-shaped member 42b is pressed against the inner diameter end surface of the hollow-shaped member 42a, and slippage occurs between the pressure-contact surfaces (sliding surfaces) 10a and 10b of the hollow-shaped member 42a and the shaft-shaped member 42b when an excessive torque is applied. Yes.

  FIGS. 7A and 7B show a clutch unit in the seventh embodiment. In this clutch unit, an outer diameter surface of the output inner ring 52 is an axially tapered cam surface 59 and an inner diameter surface of the input outer ring 51 is a cam surface 60, and a tapered roller 53 is provided between the output inner ring 52 and the input outer ring 51. Is inserted, and the cage 54 is moved in the axial direction to transmit / cut off the rotational torque.

  In the seventh embodiment, the output inner ring 52 is constituted by two members, a hollow member 52a and a shaft-like member 52b, and the elastic member 20 is fitted to the inner diameter of the hollow member 52a. Accordingly, the flange surface of the shaft-shaped member 52b is pressed against the inner diameter end surface of the hollow member 52a, and a slip is caused between the pressure-contact surfaces (sliding surfaces) 10a and 10b of the hollow member 52a and the shaft-shaped member 52b when an excessive torque is applied. Yes.

  In each of the above-described embodiments, the flange surface of the shaft-shaped member is pressed against the inner diameter end surface of the hollow member with the elastic force of the elastic member 20, and the pressure-contact surface between the hollow member and the shaft-shaped member when an excessive torque is applied. In addition to this structure, the hollow member is pressed into the hollow member by press-fitting the shaft-like member to connect them, and a retaining ring is fitted in place of the elastic member, so that the hollow member can be operated when excessive torque is applied. It is also possible to adopt a structure that causes slippage between the press-fitting surfaces of the shaft-shaped member (the inner diameter surface of the hollow member and the outer diameter surface of the shaft-shaped member).

In the first embodiment of the clutch unit according to the present invention, (a) is a sectional view taken along line BB in (b), and (b) is a sectional view taken along line AA in (a). In the second embodiment of the clutch unit according to the present invention, (a) is a cross-sectional view taken along line DD of (b), and (b) is a cross-sectional view taken along line CC of (a). In 3rd embodiment of the clutch unit which concerns on this invention, (a) is sectional drawing which follows the FF line of (b), (b) is sectional drawing which follows the EE line of (a). (A) is sectional drawing which follows the HH line of (b), (b) is sectional drawing which follows the GG line of (a) by 4th embodiment of the clutch unit which concerns on this invention. (A) is sectional drawing which follows the JJ line of (b), (b) is sectional drawing which follows the II line | wire of (a) by 5th embodiment of the clutch unit which concerns on this invention. (A) is sectional drawing which follows the LL line | wire of (b), (b) is sectional drawing which follows the KK line | wire of (a) by 6th embodiment of the clutch unit which concerns on this invention. (A) is sectional drawing which follows the NN line | wire of (b), (b) is sectional drawing which follows the MM line | wire of (a) by 7th embodiment of the clutch unit which concerns on this invention. In the conventional example of a clutch unit, (a) is sectional drawing which follows the PP line of (b), (b) is sectional drawing which follows the OO line of (a).

Explanation of symbols

10a, 10b Sliding surface 11 Input side rotating member (input outer ring)
12 Output side rotating member (output inner ring)
12a member (hollow member)
12b member (shaft-shaped member)
13 Torque transmission member (roller)
14 Cage 16 Static side member (housing)
17 Rotation resistance applying means (sliding spring)
20 Elastic member

Claims (6)

  An input-side rotating member and an output-side rotating member are arranged so as to be rotatable in forward and reverse directions with respect to the stationary side member, and a torque transmitting member that can be engaged / disengaged is interposed between the input-side rotating member and the output-side rotating member, The cage that holds the torque transmitting member causes a frictional resistance to act on the cage against the rotation of the cage with respect to the stationary side member through relative rotation with respect to the input side rotating member, and the rotational position of the input side rotating member and the cage. A clutch unit that switches between engagement and disengagement of the torque transmission member by controlling a phase difference, wherein either one of the input side rotation member and the output side rotation member is divided into two members, and the two members are excessively large. A clutch unit that is joined so that slippage occurs between the respective joint surfaces during torque action.   2. The clutch unit according to claim 1, wherein an elastic member is fitted to one of the two members, and the other member is pressed against the one member by the elastic force of the elastic member.   Of the two members, one member is a hollow member, and the other member is a shaft member, and a flange formed on the shaft end of the shaft member is joined to the inner diameter end of the hollow member to form a shaft. The clutch unit according to claim 2, wherein the flange surface of the member and the inner diameter end surface of the hollow member are sliding surfaces.   The clutch unit according to claim 1, wherein the one member is press-fitted into the other member, and both are connected by a locking member.   Of the two members, one member is a hollow member, and the other member is a shaft member, and a flange formed on the shaft end of the shaft member is joined to the inner diameter end of the hollow member to form a shaft. The clutch unit according to claim 3, wherein the outer diameter surface of the member and the inner diameter surface of the hollow member are sliding surfaces.   The clutch unit according to claim 3 or 5, wherein the sliding surface is tapered in the axial direction.