Friction clutch device and method of assembling the same

Abstract

To provide an assembling method of a friction clutch device capable of easily adjusting a set load of a return spring.SOLUTION: In a first load characteristic that is a relationship between an axial position of the inner ring 32 with respect to the rotary tube portion 13 and a magnitude of an axial load F, the first load characteristic being acquired by pressing the inner ring 32 toward the one axial side to apply the axial load to the inner ring 32 in a state where the stopper member is not locked to the locking groove 12, the second load characteristic is a relationship between the axial position of the inner ring 32 with respect to the rotary tube portion 13 and the magnitude of the axial load F, which is obtained by applying the axial load F to the inner ring 32 by pressing the inner ring 32 toward one side in the axial direction in a state in which the axial position of the inner ring 32 with respect to the rotary tube portion 13 when the axial load F is equal to a desired set load and the locking members 35 having a predetermined axial thickness are locked in the locking grooves 12. The axial thickness of the stopper member is determined based on a difference from the axial position of the inner ring 32 with respect to the rotary cylinder part 13 at a thickness calculation reference point where a change amount of an axial load F per unit moving amount of the inner ring 32 becomes a predetermined thickness calculation reference threshold or less.SELECTED DRAWING: Figure 18

Description

[Technical Field]

[0001] The present disclosure relates to a friction clutch device that switches between a connected mode in which a first member and a second member rotate integrally and a disconnected mode in which the first member and the second member rotate relative to each other, and a method for assembling the same. [Background technology]

[0002] In rotating machinery such as automobiles and machine tools, a transmission is provided between a power source, such as an engine or an electric motor, and a driven object to efficiently utilize the output of the power source. When a gear-type transmission with multiple stages is used as such a transmission, a clutch device is installed between the power source and the transmission to switch between a locked state in which the output torque of the power source can be transmitted to the transmission and an unlocked state in which it cannot be transmitted. Examples of such clutch devices include a friction clutch that transmits power through friction between a pair of opposing friction surfaces, and a dog clutch that transmits power through meshing pawls.

[0003] The friction clutch can switch between a connected mode in which torque can be transmitted and a disconnected mode in which torque cannot be transmitted, regardless of the phase difference or rotational speed difference between a pair of opposing engaging members.

[0004] 21 shows a normally open type friction clutch device 100 described in JP 2024-013596 A. When the friction clutch device 100 is switched to the connection mode, an electric actuator 101 rotates and drives a drive cam 103 of a cam device 102, displacing a holder 104 in a direction that increases the distance between the holder 104 and the drive cam 103. The holder 104 presses a pressing member 105 toward one axial side (the left side in FIG. 21) against the elastic force of a return spring 110, thereby pressing a plurality of first friction plates 106a, 106b and a second friction plate 107 against each other. This causes a first member 108 and a second member 109 to rotate integrally.

[0005] On the other hand, when the friction clutch device 100 is switched to the disengagement mode, the electric actuator 101 rotates the drive cam 103, displacing the holder 104 in a direction that shortens the gap between the drive cam 103, and the return spring (elastic member) 110 presses the pressing member 105 toward the other axial side (the right side in FIG. 21), thereby releasing the force that the pressing member 105 applies to the first friction plates 106a, 106b and the second friction plate 107 pressing them against each other. This causes the first member 108 and the second member 109 to rotate relative to each other. [Prior art documents] [Patent documents]

[0006] [Patent Document 1] Japanese Patent Application Publication No. 2024-013596 Summary of the Invention [Problem to be solved by the invention]

[0007] Controlling the friction clutch device 100 requires a set load F0 of the return spring 110 and a clutch clearance C. In the friction clutch device 100 described in JP 2024-013596 A, the set load F0 of the return spring 110 and the clutch clearance C can be adjusted by adjusting the axial thickness T of a retaining ring 114 that prevents displacement of an inner ring 113 constituting a rolling bearing 112 that supports a first member 108 on a support member 111 to the other axial side, and the axial thickness TP of the first friction plate 106b that is located furthest to the other axial side among the multiple first friction plates 106a, 106b.

[0008] The set load F0 of the return spring 110 is the spring load (repulsive force) of the return spring 110 in a state in which the pressing member 105 is not applying a force pressing the first friction plates 106a, 106b and the second friction plate 107 against each other. Also, the clutch clearance C is the amount of axial movement of the holder 104 from the state in which the axial dimension of the cam device 102 is at its shortest until the fastening force of the friction clutch device 100 reaches a predetermined value.

[0009] The set load F0 of the return spring 110 can be found, for example, as follows: First, a distance L1 is measured between the portion of the first member 108 with which the return spring 110 abuts and the side surface on the other axial side of the retaining ring 114 (or the surface of the inner surface of the retaining groove 115 in which the retaining ring 114 is retained, facing one axial side). Then, with the axial dimension of the cam device 102 at its shortest, a distance L2 is measured between the portion of the pressing member 105 with which the return spring 110 abuts and the side surface on the other axial side of the inner ring 113.

[0010] The set length L0 of the return spring 110 is calculated by subtracting the distance L2 and the axial thickness T of the retaining ring 114 from the distance L1, and the set load F0 is calculated based on the set length L0 and the spring characteristics of the return spring 110 that have been calculated in advance.

[0011] To find the clutch clearance C, first, with the axial dimension of the cam device 102 at its shortest, measure the distance L3 between the side surface on one axial side of the first friction plate 106b located furthest on the other axial side and the side surface on the other axial side of the retaining ring 114. Also, with the axial dimension of the cam device 102 at its shortest, measure the distance L4 between the part of the pressing member 105 facing the first friction plate 106b located furthest on the other axial side and the side surface on the other axial side of the inner ring 113.

[0012] The clutch clearance C is calculated by subtracting the distance L4, the axial thickness T of the retaining ring 114, and the axial thickness TP of the first friction plate 106b located furthest on the other axial side from the distance L3.

[0013] The distances L1 to L4 must be measured by temporarily assembling the members that make up the friction clutch device 100. After measuring the distances L1 to L4, the friction clutch device 100 must be disassembled and reassembled after replacing the retaining ring 114 and / or the first friction plate 106b so that the set load F0 of the return spring 110 and the clutch clearance C become the desired values. This tends to increase the assembly cost of the friction clutch device 100.

[0014] Furthermore, in the above-described method, the set load F0 is calculated using the spring characteristics of the return spring 110 that are calculated in advance based on the set length L0 of the return spring 110, and the set load F0 of the return spring 110 is not directly measured. Therefore, there is a possibility that the error in the calculated set load F0 will be large.

[0015] An object of the present disclosure is to provide a method for assembling a friction clutch device that allows for easy adjustment of the set load of a return spring. [Means for solving the problem]

[0016] The friction clutch device that is the subject of the assembly method of the friction clutch device of one embodiment of the present disclosure, and the friction clutch device of one embodiment of the present disclosure, comprise a first member, a second member, a support member, a radial rolling bearing, a stopper member, a friction engagement portion, an expansion / contraction device, a pressing member, a release bearing, and a return spring.

[0017] The first member includes a rotary cylindrical portion having a locking groove on its outer circumferential surface.

[0018] The second member is supported coaxially with the first member and rotatable relative to the first member.

[0019] The support member has a fixed cylindrical portion that is arranged coaxially with the rotating cylindrical portion around the rotating cylindrical portion, and is fixed to a portion that does not rotate when in use.

[0020] The radial rolling bearing has an outer ring fitted into the fixed cylindrical portion so that it cannot be displaced in at least one axial direction relative to the fixed cylindrical portion, an inner ring fitted into the rotating cylindrical portion so that it can be displaced in the axial direction relative to the rotating cylindrical portion, and a plurality of rolling elements arranged between the outer ring and the inner ring.

[0021] The stopper member is engaged with the engagement groove, and its side surface on one axial side abuts against the side surface on the other axial side of the inner ring, either directly or via another member, thereby preventing the inner ring from displacing toward the other axial side relative to the fixed cylindrical portion.

[0022] The friction engagement portion has at least one, and preferably a plurality of, first and second friction plates that are supported to allow relative displacement in the axial direction.

[0023] The expansion / contraction device has a first element supported on the support member so that it cannot move axially, and a second element supported on the support member so that it can move axially, and expands and contracts the distance between the first element and the second element.

[0024] The pressing member is disposed opposite the side surface on the other axial side of the friction plate that is located furthest on the other axial side among the first friction plate and the second friction plate, and is supported so as to be movable toward and away from the friction plate located furthest on the other axial side in the axial direction.

[0025] The release bearing is disposed between the second element and the pressing member.

[0026] The return spring elastically biases the pressing member toward the other axial side.

[0027] The friction clutch device switches to a connection mode in which the first member and the second member rotate as a unit by pressing the first friction plate and the second friction plate against each other based on increasing the distance between the first element and the second element, and switches to a disconnection mode in which the first member and the second member rotate relative to each other by releasing the force pressing the first friction plate and the second friction plate against each other based on decreasing the distance between the first element and the second element.

[0028] A method for assembling a friction clutch device according to one aspect of the present disclosure includes a first load characteristic obtaining step, a second load characteristic obtaining step, and an adjustment step.

[0029] In the first load characteristic acquisition process, the inner ring is pressed toward one axial side with the stopper member not engaged in the engagement groove, and an axial load is applied to the inner ring, thereby acquiring a first load characteristic, which is the relationship between the axial position of the inner ring relative to the rotating cylindrical portion and the magnitude of the axial load.

[0030] In the second load characteristic acquisition process, with a locking member having a predetermined axial thickness engaged in the locking groove, the inner ring is pressed toward one axial side to apply an axial load to the inner ring, thereby acquiring a second load characteristic, which is the relationship between the axial position of the inner ring relative to the rotating cylindrical portion and the magnitude of the axial load.

[0031] In the adjustment process, the axial thickness of the stopper member is determined based on a first difference value, which is the difference between the axial position of the inner ring relative to the rotating cylindrical portion when the axial load becomes the same as a desired set load under the first load characteristic, and the axial position of the inner ring relative to the rotating cylindrical portion at a point where the axial load increases to a predetermined value under the second load characteristic.

[0032] In one embodiment of the assembly method for a friction clutch device of the present disclosure, the stopper member can have the locking member, the side surface on one axial side of which abuts against the side surface on the other axial side of the inner ring, either directly or via another member, and an adjustment member, which is arranged adjacent to the other axial side of the locking member and has the side surface on the other axial side abutting against a surface of the inner surface of the locking groove facing the one axial side, and in the adjustment process, after determining the axial thickness of the adjustment member based on the first difference value, the adjustment member can be locked in the locking groove so as to be adjacent to the other axial side of the locking member.

[0033] A method for assembling a friction clutch device according to one embodiment of the present disclosure may further include a clutch clearance acquisition process for determining a clutch clearance, which is the axial movement of the second element from the state where the distance between the first element and the second element is shortest until the fastening force of the friction engagement portion reaches a predetermined value, based on the axial position of the inner ring relative to the rotating cylindrical portion at a first reference point where the amount of change in the axial load per unit movement of the inner ring in the first load characteristic is equal to or greater than a predetermined first threshold value, and the combined position obtained by adding the first difference value to the axial position of the inner ring relative to the rotating cylindrical portion at a second reference point where the amount of change in the axial load per unit movement of the inner ring in the second load characteristic is equal to or less than a predetermined second threshold value.

[0034] In the clutch clearance obtaining process, a gradient of a tangent at the first reference point with respect to the first load characteristic is defined as the gradient, and a linear function passing through the first reference point is defined as a spring load function that is a relationship between the axial position of the inner ring with respect to the rotating cylindrical portion and the load applied to the return spring, The clutch clearance can be calculated based on the difference between the axial position of the inner ring relative to the rotating cylindrical portion when the difference between the first load characteristic and the spring load function reaches a predetermined threshold value, and the summed position.

[0035] A method for assembling a friction clutch device according to one aspect of the present disclosure includes: a third load characteristic acquisition step of applying an axial load to the inner ring by pressing the inner ring toward one axial side with the stopper member engaged in the engagement groove, thereby acquiring a third load characteristic which is a relationship between the axial position of the inner ring with respect to the rotating cylindrical portion and the magnitude of the axial load; a confirmation step of determining a confirmation reference axial position, which is the axial position at which the axial load in the third load characteristic has increased to the predetermined value, and confirming whether a difference between the axial load in the confirmation reference axial position in the first load characteristic and the desired set load is within a predetermined error range; The sensor may further include:

[0036] In one embodiment of the friction clutch device of the present disclosure, the stopper member has a locking member whose side surface on one axial side abuts against the side surface on the other axial side of the inner ring directly or via another member, and an adjustment member that is arranged adjacent to the other axial side of the locking member and whose side surface on the other axial side abuts against a surface of the inner surface of the locking groove that faces toward the one axial side.

[0037] The friction clutch device according to one aspect of the present disclosure may further include a spacer disposed between the inner ring and the stopper member.

[0038] In one aspect of the friction clutch device disclosed herein, the first element can be configured as a drive cam having a cam surface on one axial side thereof and rotatably supported on the support member, and the second element can be configured as a holder supported non-rotatably on the support member. In this case, the expansion / contraction device further includes a plurality of rolling elements held by the holder, each of which has a rolling surface on its outer circumferential surface that is in rolling contact with the cam surface, and the axial dimension of the expansion / contraction device is expanded / contracted by rotating the drive cam.

[0039] The friction clutch device according to one aspect of the present disclosure may further include an electric actuator that rotationally drives the drive cam.

[0040] In the friction clutch device according to one aspect of the present disclosure, the return spring may be configured as a leaf spring. [Effects of the Invention]

[0041] According to the method for assembling a friction clutch device of one aspect of the present disclosure, the set load of the return spring can be easily adjusted. [Brief explanation of the drawings]

[0042] [Figure 1] FIG. 1 is an end view of a friction clutch device according to an embodiment of the present disclosure, as viewed from one axial side. [Figure 2] FIG. 2 is an end view of the friction clutch device as seen from the other axial side. [Figure 3] FIG. 3 is a cross-sectional view taken along the line AA in FIG. [Figure 4] FIG. 4 is an enlarged view of part B in FIG. [Figure 5] FIG. 5 is an exploded perspective view showing the friction clutch device. [Figure 6] FIG. 6 is a perspective view of the friction clutch device, with the second member omitted, as viewed from one axial side. [Figure 7] FIG. 7 is a perspective view of the friction clutch device, with the second member omitted, as viewed from the other axial side. [Figure 8] FIG. 8 is a perspective view showing the first member. [Figure 9] FIG. 9 is a cross-sectional view showing the first member. [Figure 10] FIG. 10 is a perspective view showing the support member. [Figure 11] FIG. 11 is a side view showing the expansion / contraction device. [Figure 12] Figure 12 is a diagram equivalent to an enlarged view of the central portion of Figure 11, where (A) is a diagram showing the state in which the cam side stopper surface and the holder side stopper surface are in contact, (B) is a diagram showing the state in which the rolling body is positioned on the reference surface, and (C) is a diagram showing the state in which the rolling body has climbed onto the inclined surface portion. [Figure 13] FIG. 13 is a perspective view showing the drive cam and the worm. [Figure 14] FIG. 14 is an end view of the holder and the rolling element assembled together, as viewed from the other axial side. [Figure 15] FIG. 15 is a cross-sectional view taken along CC in FIG. [Figure 16] FIG. 16 is an exploded perspective view showing the assembly of the rolling elements to the holder. [Figure 17] FIG. 17 is a diagram schematically showing an example of the first load characteristic, the second load characteristic, and the third load characteristic. [Figure 18] FIG. 18 is a cross-sectional view showing a state in which the first load characteristic acquisition step is performed. [Figure 19] 19(A) and 19(B) are diagrams corresponding to the enlarged view of part D in FIG. 18, showing how the second load characteristic acquisition step is performed. [Figure 20] 20(A) and 20(B) are diagrams corresponding to the enlarged view of part D in FIG. 18, showing how the third load characteristic acquisition step is performed. [Figure 21] FIG. 21 is a cross-sectional view showing an example of a conventional friction clutch device. DETAILED DESCRIPTION OF THE INVENTION

[0043] An example of an embodiment of the present disclosure will be described with reference to FIGS. 1 to 20(B).

[0044] The friction clutch device according to an embodiment of the present disclosure and the friction clutch device assembled by the method for assembling the friction clutch device according to an embodiment of the present disclosure can be disposed between a pair of rotating members or between a rotating member and a fixed member in various mechanical devices. Specifically, the friction clutch device is disposed, for example, in the drive system of an automobile between a drive source such as an electric motor or an engine and a transmission, or between the transmission and a differential.

[0045] (Structure of friction clutch device) The friction clutch device 1 includes a first member 2, a second member 3, a support member 4, a radial rolling bearing 5, a stopper member 6, a friction engagement portion 7, an expansion / contraction device 8, a pressing member 9, a release bearing 10, and a return spring 11.

[0046] In the following description, unless otherwise specified, the axial direction, radial direction, and circumferential direction refer to the axial direction, radial direction, and circumferential direction of the first member 2. One axial side refers to the left side in Fig. 3, and the other axial side refers to the right side in Fig. 3.

[0047] The first member 2 has a rotating cylindrical portion 13 having a locking groove 12 on its outer circumferential surface. The first member 2 is rotatably supported via a radial rolling bearing 5 on a support member 4 that is fixed to a portion that does not rotate even during use. The first member 2 is connected to a first rotating member (not shown) such as the output shaft of a drive source or the output shaft of a transmission so as to be able to transmit torque.

[0048] In this example, the rotating cylindrical portion 13 has a large-diameter cylindrical portion 14 on one axial side and a small-diameter cylindrical portion 15 on the other axial side. The outer circumferential surfaces of the large-diameter cylindrical portion 14 and the small-diameter cylindrical portion 15 are connected by an inner-diameter step surface 16 facing the other axial side.

[0049] In this example, the locking groove 12 is provided on the outer peripheral surface of the other axial end of the small-diameter cylindrical portion 15. The locking groove 12 has a substantially rectangular cross-sectional shape. That is, the locking groove 12 has a side surface facing one axial side, a side surface facing the other axial side, and a bottom surface facing radially outward, and the side surface facing one axial side and the side surface facing the other axial side are arranged substantially parallel to each other.

[0050] The large-diameter cylindrical portion 14 has inner-side oil passage holes 17 that penetrate radially at a plurality of circumferential positions in an axially intermediate portion.

[0051] The small-diameter cylindrical portion 15 has a female spline portion 18 on its inner circumferential surface. The first member 2 is connected to the first rotating member so as to be able to transmit torque by spline-engaging the female spline portion 18 with a male spline portion provided on the first rotating member.

[0052] In addition to the rotating cylindrical portion 13, the first member 2 further includes a hollow circular side plate portion 19 extending radially outward from one axial end of the rotating cylindrical portion 13, and a first cylindrical portion 20 extending radially outward from the radially outer end of the side plate portion 19.

[0053] The first cylindrical portion 20 is disposed coaxially with the rotating cylindrical portion 13 around the rotating cylindrical portion 13. The axial dimension of the first cylindrical portion 20 is shorter than the axial dimension of the rotating cylindrical portion 13. Therefore, the other axial end of the first cylindrical portion 20 is located on one axial side of the other axial end of the rotating cylindrical portion 13. In this example, the other axial end of the first cylindrical portion 20 is located radially outside the other axial side portion of the large-diameter cylindrical portion 14.

[0054] The first cylindrical portion 20 has an inner diameter side uneven portion 21 on its outer surface, in which concave and convex portions are arranged alternately in the circumferential direction, and has outer side oil passage holes 22 that penetrate radially at multiple locations in the circumferential direction.

[0055] The second member 3 is supported coaxially with the first member 2 and capable of relative rotation with respect to the first member 2. The second member 3 is connected to a second rotating member (not shown) such as an input shaft of a transmission or an input shaft of a differential device so as to be capable of transmitting torque.

[0056] In this example, the second member 3 has a second cylindrical portion 23 disposed around the first cylindrical portion 20 and coaxial with the first cylindrical portion 20. The second cylindrical portion 23 has an outer diameter side uneven portion 24 on its inner circumferential surface, in which recesses and protrusions are alternately arranged in the circumferential direction.

[0057] The support member 4 has a fixed cylinder portion 25 arranged coaxially with the rotating cylinder portion 13 around the rotating cylinder portion 13, and is fixed to a portion that does not rotate when in use.

[0058] In this example, the fixed cylindrical portion 25 has a stepped cylindrical inner peripheral surface formed by connecting a small diameter portion 26 on one axial side and a large diameter portion 27 on the other axial side by an outer diameter side stepped surface 28 facing the other axial side. In this example, the outer diameter side stepped surface 28 is located on the other axial side of the inner diameter side stepped surface 16.

[0059] The fixed cylinder portion 25 also has a male spline portion 29 on the outer peripheral surface of one axial end portion.

[0060] In this example, the support member 4 includes, in addition to the fixed cylindrical portion 25, a hollow circular flange portion 30 that extends radially outward from the other axial end of the fixed cylindrical portion 25.

[0061] The flange portion 30 has a plurality of through holes 58a, 58b penetrating in the axial direction at a plurality of positions in the circumferential direction. In this example, of the plurality of through holes 58a, 58b, the inner diameter of one through hole 58a is larger than the inner diameter of the remaining through hole 58b.

[0062] The support member 4 is positioned relative to the fixed part by inserting a pin portion protruding from the fixed part, which does not rotate even when the housing or the like is in use, into one of the through holes 58a, and is then supported and fixed to the fixed part by a bolt inserted through the remaining through hole 58b, so that the support member 4 does not rotate or displace even when in use.

[0063] The radial rolling bearing 5 supports the first member 2 rotatably relative to the support member 4. For this purpose, the radial rolling bearing 5 has an outer ring 31 fitted into the fixed cylindrical portion 25 so that it cannot be displaced in at least one axial direction relative to the fixed cylindrical portion 25, an inner ring 32 fitted into the rotating cylindrical portion 13 so that it can be displaced in the axial direction relative to the rotating cylindrical portion 13, and a plurality of rolling elements 33 arranged between the outer ring 31 and the inner ring 32.

[0064] In this example, the outer ring 31 is fitted into the large diameter portion 27 without any radial play, with its end face on one axial side abutting against the outer diameter side stepped surface 28 of the support member 4. The inner ring 32 is fitted onto the small diameter cylindrical portion 15 of the rotating cylindrical portion 13 so as to be movable in the axial direction, and is prevented from being displaced toward the other axial side relative to the small diameter cylindrical portion 15 by the stopper member 6 engaged in the engaging groove 12. The end face on one axial side of the inner ring 32 faces the inner diameter side stepped surface 16 of the first member 2 via a gap.

[0065] The radial rolling bearing 5 is configured by a radial rolling bearing capable of supporting radial loads and thrust loads. For example, the radial rolling bearing 5 can be configured by a radial angular contact ball bearing, a deep groove ball bearing, a radial tapered rolling bearing, etc. In this example, the radial rolling bearing 5 is configured by a radial ball bearing in which the rolling elements 33 are balls, the outer ring 31 has an angular outer ring raceway on its inner peripheral surface, and the inner ring 32 has a deep groove inner ring raceway on its outer peripheral surface.

[0066] The stopper member 6 is engaged with the engagement groove 12, and its side surface on one axial side abuts against the side surface on the other axial side of the inner ring 32 directly or via another member, thereby preventing the inner ring 32 from displacing toward the other axial side relative to the rotating cylindrical portion 13.

[0067] In this example, the side surface of the stopper member 6 on one axial side is in contact with the side surface of the inner ring 32 on the other axial side via the spacer 34. In other words, the spacer 34 is sandwiched between the side surface of the stopper member 6 on one axial side and the side surface of the inner ring 32 on the other axial side.

[0068] The stopper member 6 has a locking member 35 having a side surface on one axial side thereof abutting against a side surface on the other axial side of the inner ring 32 directly or via another member, and an adjusting member 36 arranged adjacent to the other axial side of the locking member 35 and having a side surface on the other axial side abutting against a surface of the inner surface of the locking groove 12 facing the one axial side. In this example, the locking member 35 has a side surface on one axial side thereof abutting against the side surface on the other axial side of the inner ring 32 via a spacer 34.

[0069] The locking member 35 and the adjusting member 36 can each be configured as a retaining ring having a segmented annular shape.

[0070] The locking member 35 has a predetermined axial thickness T 35 On the other hand, the adjustment member 36 is configured by a retaining ring having an axial thickness T 36 The appropriate axial thickness T was selected from among several different types of retaining rings. 36 The locking member 35 is configured as a retaining ring having a constant axial thickness T 35 The adjustment member 36 has a constant axial thickness T 36 It has.

[0071] The method for assembling a friction clutch device according to one aspect of the present disclosure can also be applied to a friction clutch device in which the stopper member is configured by a single retaining ring.

[0072] The friction engagement portion 7 has at least one, and preferably multiple, first friction plates 37 and second friction plates 38 that are supported so as to be capable of relative axial displacement. In this example, the friction engagement portion 7 is configured by alternately stacking five first friction plates 37 and five second friction plates 38.

[0073] The first friction plate 37 is configured in a substantially hollow circular plate shape. The first friction plate 37 is supported so as to be able to move in the axial direction but not to rotate relative to the first cylindrical portion 20 by engaging the uneven portion provided on the inner peripheral surface with the inner diameter side uneven portion 21 of the first cylindrical portion 20. In this example, the axial thickness of all the first friction plates 37, including the first friction plate 37 located furthest to the other axial side, is the same.

[0074] The second friction plate 38 is configured in a substantially hollow circular plate shape. The second friction plate 38 is supported so as to be able to move axially with respect to the second cylindrical portion 23 but not to rotate relative to the second cylindrical portion 23, by engaging the uneven portion provided on the outer peripheral surface with the outer diameter side uneven portion 24 of the second member 3.

[0075] The side surface on one axial direction of the second friction plate 38 that is located furthest to one axial direction among the five second friction plates 38 abuts or closely faces the side surface on the other axial direction of a spacer 39 that is fitted onto the one axial side portion of the first cylindrical portion 20. The spacer 39 is prevented from displacing to one axial side by a retaining ring 40 that is engaged with the outer peripheral surface of the one axial side portion of the first cylindrical portion 20.

[0076] The friction engagement portion 7 includes a return spring that elastically biases the first friction plate 37 and the second friction plate 38 in a direction separating them from each other.

[0077] The expansion / contraction device 8 has a first element supported on the support member 4 so that it cannot be displaced in the axial direction, and a second element supported on the support member 4 so that it can be displaced in the axial direction, and expands / contracts the distance between the first element and the second element, in other words, the axial dimension of the expansion / contraction device 8 itself.

[0078] The configuration of the expansion / contraction device 8 is not particularly limited as long as it can expand and contract its axial dimension. For example, the expansion / contraction device 8 can be configured with a hydraulic cylinder that expands and contracts its axial dimension in response to the supply and discharge of hydraulic pressure, or a cam device that expands and contracts its axial dimension in response to the rotation of a drive cam. From the perspective of accurately controlling the friction clutch device 1, it is preferable that the expansion / contraction device 8 be configured with a cam device. Examples of cam devices that can be used include a cam device in which a drive cam surface provided on a drive cam directly engages with a driven cam surface provided on a driven cam, a cam device in which a rolling element is sandwiched between a drive cam surface provided on a drive cam and a driven cam surface provided on a driven cam, and a cam device in which a rolling element held in a holder is brought into rolling contact with a cam surface provided on a drive cam.

[0079] In this example, the expansion / contraction device 8 includes a drive cam 41 as a first element, a holder 42 as a second element, and a plurality of rolling elements 43. As the drive cam 41 rotates, the expansion / contraction device 8 expands or contracts the axial dimension of the expansion / contraction device 8 itself.

[0080] The drive cam 41 has, on one axial side thereof, a cam surface 44 which is an uneven surface in the circumferential direction. As shown in Fig. 13, the cam surface 44 is composed of a plurality of reference surfaces 45 each made of a flat surface perpendicular to the central axis of the drive cam 41 and protrusions 46 of the same number as the reference surfaces 45, which protrude further toward one axial side than the reference surfaces 45 and are arranged alternately in the circumferential direction.

[0081] Each reference surface 45 has a fan-shaped surface shape when viewed from one axial side.

[0082] Each convex portion 46 has a flat surface portion 47 on its tip surface, a cam side stopper surface 48 on one circumferential side surface facing the rotation direction when reducing the axial dimension of the expansion / contraction device 8, and an inclined surface portion 49 on the other circumferential side surface facing the rotation direction when increasing the axial dimension of the expansion / contraction device 8.

[0083] The flat surface portion 47 is formed by a flat surface that is perpendicular to the central axis of the drive cam 41, and has a fan-shaped surface shape when viewed from one axial side.

[0084] The cam side stopper surface 48 is formed of a flat surface that is perpendicular to the flat surface portion 47.

[0085] The inclined surface portion 49 is inclined in a direction toward one axial side as it moves toward the rear side with respect to the rotation direction when increasing the axial dimension of the expansion / contraction device 8, and connects the reference surface 45 and the flat surface portion 47.

[0086] In this example, the inclined surface portion 49 is formed by a plane whose inclination angle with respect to an imaginary plane perpendicular to the central axis of the expansion / contraction device 8 is constant in the circumferential direction. However, the inclined surface portion 49 may also be formed by a curved surface or a composite surface made up of multiple flat and / or curved surfaces.

[0087] That is, cam surface 44 is configured by arranging reference surface 45, inclined surface portion 49, flat surface portion 47, and cam-side stopper surface 48 in this order multiple times in the circumferential direction. Of cam surface 44, flat surface portion 47 is located closest to one axial side, and reference surface 45 is located closest to the other axial side.

[0088] The number of reference surfaces 45 and protrusions 46 that make up the cam surface 44 is determined according to the number of rolling elements 43. In this example, the expansion / contraction device 8 has three rolling elements 43. Therefore, the cam surface 44 is formed by alternately arranging three reference surfaces 45 and three protrusions 46 in the circumferential direction. In other words, the cam surface 44 is formed by arranging the reference surface 45, the inclined surface portion 49, the flat surface portion 47, and the cam side stopper surface 48 in this order three times in the circumferential direction.

[0089] In this example, the drive cam 41 is configured to be rotatable by an electric actuator 50. For this purpose, the drive cam 41 has a gear portion 51 on a portion of the outer circumferential surface in the circumferential direction. Specifically, the drive cam 41 includes a hollow, circular main body portion 52 having a cam surface 44 on one axial side thereof, and a substantially fan-shaped protrusion portion 53 that protrudes radially outward from one circumferential point of the main body portion 52. The gear portion 51 is provided on the surface of the protrusion portion 53 that faces radially outward.

[0090] In this example, the gear portion 51 is configured by a helical gear, but the gear portion 51 may also be configured by a spur gear.

[0091] The drive cam 41 is supported by the cam support bearing 54 so as to be rotatable relative to the support member 4 but so as not to be displaced in the axial direction. In this example, the cam support bearing 54 is disposed between the inner peripheral surface of the main body 52 and the outer peripheral surface of the other axial end of the fixed cylinder 25.

[0092] The cam support bearing 54 includes an inner ring 55, an outer ring 56, and a plurality of rolling elements 57 disposed between the inner ring 55 and the outer ring 56 so as to be freely rollable.

[0093] The inner ring 55 is fitted onto the end portion on the other axial side of the fixed cylindrical portion 25, and the side surface on the other axial side abuts against the side surface on one axial side of the flange portion 30.

[0094] The outer ring 56 is fitted into the main body 52, and one axial side of the outer ring 56 abuts against a stepped surface 59 provided on the inner circumferential surface of the main body 52 and facing the other axial side.

[0095] The cam support bearing 54 is configured as a radial rolling bearing capable of supporting radial loads and thrust loads. For example, the cam support bearing 54 can be configured as a radial angular contact ball bearing, a deep groove ball bearing, a radial tapered rolling bearing, or the like. In this example, the cam support bearing 54 is configured as a radial angular contact ball bearing. That is, each of the rolling elements 57 is configured as a ball.

[0096] The holder 42 is supported so as to be unable to rotate relative to the support member 4 but to be movable in the axial direction. The holder 42 holds the plurality of rolling elements 43 so as to be rotatable about the rotation axes, which are the central axes of the rolling elements 43, in a state in which the rotation axes are arranged in radial directions about the central axis of the holder 42. For this purpose, the holder 42 includes a plurality of holding portions 60 and connecting portions 61, the number of which is equal to the number of holding portions 60, which connect two circumferentially adjacent holding portions 60 among the plurality of holding portions 60.

[0097] Each of the holding portions 60 has a generally rectangular cylindrical shape. Specifically, the holding portion 60 has a pair of support plate portions 62a, 62b and a pair of connecting plate portions 63a, 63b.

[0098] The pair of support plates 62a, 62b are each configured as a substantially rectangular flat plate and are arranged parallel to each other while being spaced apart in the radial direction. Support plates 62a, 62b each have support holes 64a, 64b. Support holes 64a, 64b each penetrate support plates 62a, 62b in the radial direction and are formed as circular holes that are coaxial with each other.

[0099] Of the pair of support plate portions 62a, 62b, the radially inner support plate portion 62a has a locking hole 65 that passes through in the axial direction at a portion of the support plate portion 62a that is off the circumferential center position.

[0100] Each of the pair of connecting plates 63a, 63b is configured in a substantially rectangular flat plate shape. The pair of connecting plates 63a, 63b connects both circumferential end portions of the pair of support plates 62a, 62b. The outer circumferential side surfaces of the pair of connecting plates 63a, 63b, specifically, the one circumferential side surface of the connecting plate 63a on one circumferential side and the other circumferential side surface of the connecting plate 63b on the other circumferential side, are parallel to each other and are configured as flat surfaces perpendicular to an imaginary plane perpendicular to the central axis of the holder 42.

[0101] Each of the connecting portions 61 connects two of the plurality of holding portions 60 that are adjacent to each other in the circumferential direction.

[0102] In this example, each connecting portion 61 is formed of a flat plate having a substantially fan-shaped end face when viewed in the axial direction. One circumferential end of each connecting portion 61 is connected to one axial end of a side surface on the other circumferential side of a connecting plate portion 63b on the other circumferential side of one of the two circumferentially adjacent holding portions 60, and the other circumferential end of each connecting portion 61 is connected to one axial end of a side surface on one circumferential side of a connecting plate portion 63a on the one circumferential side of the other of the two circumferentially adjacent holding portions 60. As a result, the holder 42 as a whole is formed in a substantially annular shape.

[0103] Each of the connecting portions 61 has a female spline portion 66 on its radially inner surface.

[0104] The holder 42 is supported so as to be unable to rotate relative to the support member 4 but to be able to move axially by spline-engaging the female spline portion 66 with the male spline portion 29 of the support member 4 to allow relative axial movement.

[0105] The number of holding portions 60 and connecting portions 61 is determined according to the number of rolling bodies 43. In this example, the expansion / contraction device 8 has three rolling bodies 43. Therefore, the holding portion 60 is made up of three holding portions 60, and the connecting portion 61 is made up of three connecting portions 61.

[0106] In this example, the holder 42 further has a holder side stopper surface 67 that abuts against the cam side stopper surface 48 when the distance between the holder 42 and the drive cam 41 is at its shortest, i.e., when the axial dimension L of the expansion / contraction device 8 is at its smallest.

[0107] The holder-side stopper surface 67 is a part of at least one of the plurality of holding portions 60, and is a portion that protrudes in the other axial direction beyond the side surface on the other axial direction of the plurality of connecting portions 61, and is provided in a portion that faces in the circumferential direction opposite the cam-side stopper surface 48. In this example, the holder-side stopper surface 67 is provided in a portion of the side surface on the other axial direction of the connecting plate portions 63b on the other circumferential side of all of the holding portions 60 that protrudes in the other axial direction beyond the side surface on the other axial direction of the connecting portions 61.

[0108] Each rolling body 43 has a rolling surface 68 on its outer surface that is in rolling contact with the cam surface 44, and is held in the holder 42 so as to be able to rotate (spin) around a rotation axis arranged radially from the central axis of the holder 42.

[0109] The rolling elements 43 are constituted by balls, cylindrical rollers, cylindrical rollers, etc. In this example, each rolling element 43 is constituted by a cylindrical roller, and is supported rotatably relative to the holder 42 by a cylindrical support shaft 69 and a plurality of rollers 70.

[0110] Specifically, rolling elements 43 are arranged around the axial middle portion of support shaft 69 (the middle portion of support shaft 69 in the radial direction centered on the central axis of holder 42), and rollers 70 are arranged to roll freely between the outer peripheral surface of support shaft 69 and the inner peripheral surface of rolling elements 43. Furthermore, both axial end portions of support shaft 69, i.e., both radial end portions of support shaft 69 centered on the central axis of holder 42, are fitted into support holes 64a, 64b of support plate portions 62a, 62b.

[0111] Furthermore, in this example, the expansion / contraction device 8 is provided with a retaining member 71 that prevents the support shaft 69 from being displaced in the axial direction of the support shaft 69 relative to the holder 42 (in the radial direction centered on the central axis of the holder 42). In this example, the retaining member 71 is configured as a cylindrical pin. Both axial ends of the retaining member 71 are press-fitted into the locking holes 65, and the axial middle portion of the retaining member 71 is positioned inside a locking groove 72 that is formed around the entire circumference of the support shaft 69 on the inner side in the radial direction of the holder 42. This prevents the support shaft 69 from falling off the holder 42.

[0112] In the expansion / contraction device 8, as the drive cam 41 rotates, the amount by which the rolling element 43 rides up from the reference surface 45 of the cam surface 44 increases or decreases, thereby displacing the holder 42 in the axial direction.

[0113] There are no particular limitations on the materials that make up the drive cam 41, holder 42, and rolling elements 43, but for example, the drive cam 41 and / or holder 42 can be made as a single unit from sintered metal, which allows drive cam 41 and / or holder 42 with complex shapes to be manufactured at low cost.

[0114] The expansion / contraction device 8 of this example further includes an electric actuator 50 that rotationally drives the drive cam 41. The electric actuator 50 uses an electric motor (not shown) as a drive source to rotationally drive the drive cam 41. Specifically, the electric actuator 50 uses the electric motor to rotationally drive the drive cam 41 via a reducer 73. The reducer 73 is configured by meshing a worm 74, which is rotationally driven by the electric motor, with the gear portion 51 of the drive cam 41.

[0115] The pressing member 9 faces the friction plate, out of the first friction plate 37 and the second friction plate 38, that is located furthest on the other axial side, and is arranged so as to be movable toward and away from the friction plate furthest on the other axial side in the axial direction. The pressing member 9 has a portion that faces the friction plate, out of the first friction plate 37 and the second friction plate 38, that is located furthest on the other axial side.

[0116] The pressing member 9 is pressed toward one axial side against the elastic force of the return spring 11 based on the expansion of the axial dimension of the expansion / contraction device 8, whereas the pressing member 9 is pressed toward the other axial side by the elastic force of the return spring 11 based on the contraction of the axial dimension of the expansion / contraction device 8.

[0117] In this example, the pressing member 9 is fitted onto the first member 2 so as to be capable of relative displacement in the axial direction and without any rattle in the radial direction.

[0118] In this example, the pressing member 9 is formed by bending a metal plate having sufficient strength and rigidity, such as a steel plate, into a generally crank-shaped cross section. Specifically, the pressing member 9 has, in order from the inside in the radial direction, a small-diameter cylindrical portion 75, a conical cylindrical portion 76, an inner-diameter circular ring portion 77, a medium-diameter cylindrical portion 78, an outer-diameter circular ring portion 79, a large-diameter cylindrical portion 80, and a pressing portion 81.

[0119] The small diameter cylindrical portion 75 is fitted onto the large diameter cylindrical portion 14 of the rotating cylindrical portion 13 without rattle and in a manner allowing relative displacement in the axial direction. As a result, the pressing member 9 is supported so as to be capable of relative displacement in the axial direction with respect to the first member 2.

[0120] The conical cylindrical portion 76 extends radially outward from one axial end of the small-diameter cylindrical portion 75 toward one axial side.

[0121] The inner diameter side circular ring portion 77 extends radially outward from one axial end of the conical tube portion 76 .

[0122] The medium diameter cylindrical portion 78 extends from the radially outer end of the inner diameter side circular ring portion 77 toward the other axial direction, and is disposed radially outside the small diameter cylindrical portion 75 and the conical cylindrical portion 76 .

[0123] The outer diameter side circular ring portion 79 extends radially outward from the other axial end of the medium diameter cylindrical portion 78 .

[0124] The large diameter cylindrical portion 80 extends from the radially outer end of the outer diameter side circular ring portion 79 toward one axial direction, and is disposed radially outside the medium diameter cylindrical portion 78 .

[0125] The pressing portion 81 extends radially outward from one axial end of the large-diameter cylindrical portion 80. The pressing portion 81 has a circular ring-shaped side surface on one axial side that faces the friction plate that is located furthest on the other axial side out of the first friction plate 37 and the second friction plate 38. In this example, the pressing portion 81 faces the first friction plate 37 that is located furthest on the other axial side.

[0126] The release bearing 10 is disposed between the holder 42, which is the second element, and the pressing member 9.

[0127] The release bearing 10 is constituted by a rolling bearing capable of supporting at least a thrust load. Specifically, the release bearing 10 can be constituted by a rolling bearing capable of supporting only a thrust load, such as a thrust needle bearing or a thrust roller bearing, or a rolling bearing capable of supporting a radial load and a thrust load, such as an angular contact ball bearing, a deep groove ball bearing or a thrust ball bearing. In this example, the release bearing 10 is constituted by an angular contact ball bearing.

[0128] The release bearing 10 of this example includes an outer ring 82, an inner ring 83, and balls 84 that are arranged to roll freely between the outer ring 82 and the inner ring 83. The release bearing 10 is sandwiched between a side surface on one axial side of the holder 42 and a side surface on the other axial side of the inner diameter side circular ring portion 77 of the pressing member 9. More specifically, the side surface on the other axial side of the outer ring 82 abuts against a side surface on one axial side of the holder 42, and the side surface on one axial side of the inner ring 83 abuts against a side surface on the other axial side of the inner diameter side circular ring portion 77.

[0129] The return spring 11 elastically biases the pressing member 9 toward the other axial side. Therefore, when the axial dimension of the expansion / compression device 8 is contracted, the pressing member 9 is pressed toward the other axial side by the elastic force of the return spring 11. Furthermore, the elastic force of the return spring 11 applies a preload to the radial rolling bearing 5, the expansion / compression device 8, the release bearing 10, and the cam support bearing 54, regardless of the axial dimension of the expansion / compression device 8. This prevents harmful slippage from occurring at the rolling contact points.

[0130] The return spring 11 is formed of a spring such as a disc spring, a compression coil spring, or an extension coil spring. When the return spring 11 is formed of a spring that receives a compressive load, such as a disc spring or a compression coil spring, the return spring 11 is sandwiched between the pressing member 9 and the first member 2 in an elastically compressed state. On the other hand, when the return spring 11 is formed of a spring that receives a tensile load, such as an extension coil spring, the return spring 11 is stretched between the pressing member 9 and a part that does not displace in the axial direction even during use, such as the support member 4. The return spring 11 can be formed of a single spring or multiple springs. It is preferable that the return spring 11 be formed of a disc spring in order to reduce the axial dimension and obtain nonlinear spring characteristics.

[0131] In this example, the return spring 11 is composed of a single disc spring having a conical cylindrical shape whose diameter increases toward the other axial side. The small-diameter end of the return spring 11 abuts against the radially inner end of the side surface on the other axial side of the side plate portion 19 of the first member 2 via a spacer 85 having a substantially L-shaped cross section, and the large-diameter end of the return spring 11 abuts against the side surface on one axial side of the inner-diameter-side circular ring portion 77 of the pressing member 9.

[0132] In the friction clutch device 1 of this example, the return spring 11, a portion of the pressing member 9, and the release bearing 10 are configured to be positioned radially inside the first tubular portion 20 of the first member 2, regardless of the axial dimension of the expansion / contraction device 8.

[0133] Specifically, even when the rolling element 43 is positioned on the reference plane 45 and the axial dimension of the expansion / contraction device 8 is at its smallest, the return spring 11, one axial side portion of the medium-diameter cylindrical portion 78 of the pressing member 9, the inner diameter side circular ring portion 77, the tapered cylindrical portion 76, and the small diameter cylindrical portion 75, the release bearing 10, and one axial side portion of the holder 42 are positioned radially inside the first cylindrical portion 20. More specifically, in the friction clutch device 1 of this example, the release bearing 10 and one axial side portion of the holder 42 are positioned radially inside the medium diameter cylindrical portion 78 of the pressing member 9, and the first cylindrical portion 20 is positioned around the one axial side portion of the medium diameter cylindrical portion 78, the inner diameter side circular ring portion 77, the tapered cylindrical portion 76, and the small diameter cylindrical portion 75, and the return spring 11.

[0134] When the friction clutch device 1 is in use, lubricating oil is pumped in from the radially inner side of the rotating cylindrical portion 13 of the first member 2, and supplied to the expansion / contraction device 8, release bearing 10, etc. through the inner side oil passage 17, and further supplied to the friction engagement portion 7 through the outer side oil passage 22.

[0135] The friction clutch device 1 switches between a connection mode in which the first member 2 and the second member 3 rotate together and a disconnection mode in which the first member 2 and the second member 3 rotate relative to each other by expanding or contracting the distance between the first element and the second element of the expansion / contraction device 8, i.e., the axial dimension of the expansion / contraction device 8.

[0136] To switch the friction clutch device 1 to the connection mode, the axial dimension of the expansion / contraction device 8 is expanded. In this example, the electric actuator 50 rotates the drive cam 41 to position the rolling element 43 on the flat surface portion 47 or increase the amount of riding on the inclined surface portion 49. This displaces the holder 42, which is the second element, to one axial side, which is the direction in which the gap between it and the drive cam 41, which is the first element, increases, and the axial dimension of the expansion / contraction device 8 is expanded.

[0137] When the axial dimension of the expansion / contraction device 8 expands, the pressing member 9 and the release bearing 10 are pressed toward one axial side against the elastic force of the return spring 11. Furthermore, the pressing member 9 presses the first friction plate 37, which is closest to the other axial side, toward one axial side against the elastic forces of the return spring 11 and the return spring. As a result, the first friction plate 37 and the second friction plate 38 are pressed against each other, and the friction engagement portion 7 is connected, so that the first member 2 and the second member 3 rotate integrally.

[0138] On the other hand, to switch the friction clutch device 1 to the disengagement mode, the axial dimension of the expansion / contraction device 8 is contracted. In this example, the drive cam 41 is rotationally driven by the electric actuator 50 to position the rolling element 43 on the reference surface 45 or reduce the amount of riding on the inclined surface portion 49. This displaces the holder 42, which is the second element, toward the other axial side, which is the direction in which the axial distance between it and the drive cam 41, which is the first element, is reduced, and the axial dimension of the expansion / contraction device 8 is contracted.

[0139] When the axial dimension of the expansion / contraction device 8 contracts and the force pressing the pressing member 9 toward one axial side decreases, the pressing member 9 and the release bearing 10 are pressed toward the other axial side mainly by the elastic restoring force of the return spring 11. As a result, the force pressing the first friction plate 37 and the second friction plate 38 against each other decreases due to the action of the return spring, and eventually a gap is formed between the first friction plate 37 and the second friction plate 38, and the force pressing the first friction plate 37 and the second friction plate 38 against each other is lost, i.e., released. This cuts off the friction engagement portion 7, and the first member 2 and the second member 3 begin to rotate relative to each other.

[0140] In the friction clutch device 1 of this embodiment, the cam-side stopper surface 48 of the drive cam 41 and the holder-side stopper surface 67 of the holder 42 are brought into contact with each other at approximately regular intervals, thereby correcting the reference position (θ=0°) of the drive cam 41. Therefore, according to the friction clutch device 1 of this embodiment, it is possible to suppress an increase in the error in the transmission torque capacity of the friction engagement unit 7, which is determined based on the rotation angle θ of the drive cam 41, and it is possible to accurately adjust the transmission torque capacity of the friction engagement unit 7 over a long period of time.

[0141] The timing for bringing the cam side stopper surface 48 and the holder side stopper surface 67 into contact with each other can be any timing as long as it does not affect the use of the friction clutch device 1. For example, the cam side stopper surface 48 and the holder side stopper surface 67 can be brought into contact with each other every time the friction clutch device 1 is switched to the disengagement mode. And / or the cam side stopper surface 48 and the holder side stopper surface 67 can be brought into contact with each other immediately after the power to the mechanical device in which the friction clutch device 1 is incorporated is turned on.

[0142] When the friction clutch device 1 is incorporated into a vehicle and used, the cam-side stopper surface 48 and the holder-side stopper surface 67 can be brought into contact with each other at any timing that does not interfere with the running of the vehicle. More specifically, for example, the cam-side stopper surface 48 and the holder-side stopper surface 67 can be brought into contact with each other immediately after the ignition switch is turned on.

[0143] (Method of assembling a friction clutch device) A method for assembling the friction clutch device 1 while adjusting the set load F0 of the return spring 11 to a desired value and easily measuring the clutch clearance C will be described with reference to FIGS. 17 to 20(B).

[0144] 18, the first member 2, support member 4, radial rolling bearing 5, friction engagement portion 7, expander / contractor 8, pressing member 9, release bearing 10, and return spring 11 are combined to obtain friction clutch device 1z in a state in which stopper member 6 is not engaged with locking groove 12. The order in which first member 2, support member 4, radial rolling bearing 5, friction engagement portion 7, expander / contractor 8, pressing member 9, release bearing 10, and return spring 11 are combined is not particularly limited, and they can be combined in any order.

[0145] Next, with the stopper member 6 not engaged in the engagement groove 12, the inner ring 32 is pressed toward one axial side (the lower side of Figure 18) to apply an axial load F to the inner ring 32, thereby performing a first load characteristic acquisition process to acquire a first load characteristic, which is the relationship between the axial position of the inner ring 32 relative to the rotating cylindrical portion 13 and the axial load F.

[0146] The first load characteristic acquisition step can be performed using, for example, a universal testing machine (autograph), although the method is not limited to this.

[0147] In order to carry out the first load characteristic acquisition process using a universal testing machine, first, the friction clutch device 1z, in a state in which the stopper member 6 is not engaged in the engagement groove 12, is placed on the table 86 with one axial side facing downward and the other axial side facing upward.

[0148] Next, a cylindrical pressing jig 87 is placed on the other axial side surface of the spacer 34. The pressing jig 87 has an inner diameter that is larger than the outer diameter of the stopper member 6 (larger than both the outer diameter of the locking member 35 and the outer diameter of the adjustment member 36) and smaller than the outer diameter of the spacer 34, and an outer diameter that is smaller than the inner diameter of the outer ring 31.

[0149] Then, the crosshead 88 is lowered at a constant speed, and the inner ring 32 is pressed toward one axial side (the lower side in Fig. 18) via the pressing jig 87 and the spacer 34, thereby applying an axial load F to the inner ring 32, thereby obtaining a relationship (first load characteristic) between the axial position of the inner ring 32 with respect to the rotating cylindrical portion 13 and the axial load F, as shown by the solid line in Fig. 17. The axial position of the inner ring 32 with respect to the rotating cylindrical portion 13 can be obtained by measuring the amount of displacement of the crosshead 88 from a reference position where the tip end surface (lower surface) of the crosshead 88 does not contact the pressing jig 87, for example, from top dead center.

[0150] The axial load F is zero until the crosshead 88 is lowered and its tip surface (lower surface) abuts against the side surface on the other axial side of the pressing jig 87. When the tip surface of the crosshead 88 abuts against the side surface on the other axial side of the pressing jig 87, it becomes necessary to resist the elastic force of the return spring 11 in order to further lower the crosshead 88, that is, to further press the inner ring 32 toward one axial side. Therefore, the axial load F begins to increase immediately after the tip surface of the crosshead 88 abuts against the side surface on the other axial side of the pressing jig 87.

[0151] As the crosshead 88 is further lowered, the pressing member 9 moves to one axial side, and when the pressing portion 81 abuts against the side surface of the first friction plate 37 furthest on the other axial side in the axial direction, it becomes necessary to resist not only the elastic force of the return spring 11 but also the elastic force of the return spring in order to further lower the crosshead 88. For this reason, when the pressing portion 81 abuts against the side surface of the first friction plate 37 furthest on the other axial side in the axial direction, the axial load F begins to increase sharply. In other words, a point where the axial load F begins to increase sharply appears on the function curve f1 representing the first load characteristic; specifically, a first reference point P1 appears where the amount of change in the axial load F per unit movement of the inner ring 32 is equal to or greater than a predetermined first threshold value T1.

[0152] The first load characteristic needs to be acquired until the first reference point P1 appears on the function curve f1 representing the first load characteristic. Therefore, the first load characteristic is acquired until the crosshead 88 descends an amount sufficient for the first reference point P1 to appear on the function curve f1 representing the first load characteristic. More specifically, the first load characteristic is acquired until the axial load F reaches a predetermined value or until the crosshead 88 descends a predetermined amount. In this example, the first load characteristic is acquired until the axial load F reaches a predetermined value γ. The first threshold value T1 can be determined in advance by experiment or calculation.

[0153] Next, the locking groove 12 is fitted with a predetermined axial thickness T 35 In a state where the locking member 35 having the locking member 35 is locked, the inner ring 32 is pressed toward one axial side to apply an axial load F to the inner ring 32, and a second load characteristic acquisition process is performed to acquire a second load characteristic which is the relationship between the axial position of the inner ring 32 with respect to the rotating cylindrical portion 13 and the axial load F.

[0154] The second load characteristic acquisition process is carried out in basically the same manner as the first load acquisition process, using the same test equipment as that used in the first load acquisition process. For this purpose, after the first load acquisition process is completed, the crosshead 88 is raised and the pressing jig 87 is removed from the other axial side of the spacer 34. Next, a predetermined axial thickness T 35 The locking member 35 having the crosshead 88 is engaged, and then the pressing jig 87 is placed again on the side surface of the spacer 34 on the other axial side (see FIG. 19(A)). Next, the crosshead 88 is lowered at a constant speed, and the inner ring 32 is pressed toward one axial side via the pressing jig 87 and the spacer 34, thereby applying an axial load F to the inner ring 32, thereby obtaining a relationship (second load characteristic) between the axial position of the inner ring 32 with respect to the rotating cylindrical portion 13 (the displacement amount of the crosshead 88) and the axial load F, as shown by the dashed line in FIG.

[0155] As in the first load characteristic acquisition process, the crosshead 88 is lowered, and the axial load F becomes 0 until its tip surface (lower surface) abuts against the other axial side surface of the pressing jig 87. The axial load F then begins to increase immediately after the tip surface of the crosshead 88 abuts against the other axial side surface of the pressing jig 87. In the second load acquisition process, the axial position of the inner ring 32 is restricted by the locking member 35, so the amount of descent of the crosshead 88 until the axial load F starts to increase is greater than the amount of descent of the crosshead 88 until the axial load F starts to increase in the first load acquisition process.

[0156] In addition, in the second load acquisition process, the axial position of the inner ring 32 is restricted by the locking member 35, and the return spring 11 is elastically compressed, so that the increase in the axial load F per unit movement of the crosshead 88 (the slope of the tangent to the function curve f2 representing the second load characteristic) immediately after the tip surface of the crosshead 88 abuts against the other axial side surface of the spacer 34 is larger than in the first load acquisition process.

[0157] 19(B), as the crosshead 88 is further lowered, the side surface on the other axial direction of the locking member 35 moves away from the side surface of the inner surface of the locking groove 12 facing one axial direction, and the reaction force component of the elastic force of the return spring 11, which is caused by the return spring 11 being compressed due to the presence of the locking member 35, becomes zero. This causes the increase in the axial load F per unit movement of the crosshead 88 to become gentle. In other words, a point appears on the function curve f2 representing the second load characteristic where the increase in the axial load F begins to become gentle; specifically, a second reference point P2 where the change in the axial load F per unit movement of the inner ring 32 becomes equal to or less than a predetermined second threshold value T2.

[0158] The second load characteristic becomes substantially the same as the first load characteristic after the side surface on the other axial side of the locking member 35 separates from the side surface facing one axial side of the inner surface of the locking groove 12. In other words, in the range where the amount of descent of the crosshead 88 is greater than the second reference point P2 (where the inner ring 32 is positioned on one axial side), the function curve f2 representing the second load characteristic and the function curve f1 representing the first load characteristic substantially coincide with each other.

[0159] The second load characteristic needs to be acquired at least until the second reference point P2 appears on the function curve f2 representing the second load characteristic. Therefore, the second load characteristic is acquired until the crosshead 88 descends an amount sufficient for the second reference point P2 to appear on the function curve f2 representing the second load characteristic. More specifically, the second load characteristic is acquired until the axial load F reaches a predetermined value or until the crosshead 88 descends a predetermined amount. In this example, the second load characteristic is acquired until the axial load F reaches a predetermined value γ. The second threshold value T2 can be determined in advance by experiment or calculation.

[0160] Next, in the first load characteristic, the axial position x of the inner ring 32 with respect to the rotating cylindrical portion 13 when the axial load F becomes equal to the desired set load F0 is F0 and, in the function curve f2 representing the second load characteristic, the axial position x of the inner ring 32 with respect to the rotating cylindrical portion 13 (the displacement amount of the crosshead 88) at the point where the axial load F increases to a predetermined value α. α2 An adjustment step is performed in which the axial thickness T6 of the stopper member 6 is determined based on a first difference value ΔD1 which is the difference between the first difference value ΔD1 and the second difference value ΔD2.

[0161] It is preferable that the predetermined value α is set as small as possible within a range in which the axial load F can be stably measured. The predetermined value α is not limited to this, but can be set to 0 N or more and 50 N or less, and is preferably set to 5 N or more and 15 N or less.

[0162] In the adjustment process, specifically, the axial thickness T6 of the stopper member 6 is adjusted to the axial thickness T 35 and the first difference value ΔD1 (T6=T 35+ΔD1). In this example, the axial thickness T 36 or the axial thickness T closest to the first difference value ΔD1 36 The adjusting member 36 having the above-mentioned characteristic is selected from among a plurality of types of adjusting members 36 prepared.

[0163] The selected adjustment member 36 is then engaged in the engagement groove 12 so as to be adjacent to the other axial side of the engagement member 35. This adjusts the axial thickness T6 of the stopper member 6, and by adjusting the amount of compression of the return spring 11 when the axial dimension of the expansion / contraction device 8 is at its shortest, the set load F0 of the return spring 11 becomes the desired value.

[0164] Next, the axial position x of the inner ring 32 with respect to the rotating tubular portion 13 at the first reference point P1 where the amount of change in the axial load F per unit movement of the inner ring 32 in the first load characteristic is equal to or greater than a predetermined first threshold T1 is calculated. P1 and the axial position x of the inner ring 32 with respect to the rotating tubular portion 13 at the first reference point P2 at which the amount of change in the axial load F per unit movement of the inner ring 32 in the second load characteristic is equal to or less than a predetermined second threshold T2. P2 The sum position x obtained by adding the first difference value ΔD1 to A Based on this, a clutch clearance acquisition process is performed to determine the clutch clearance C, which is the amount of axial movement of the holder 42 from the state in which the distance between the drive cam 41, which is the first element, and the holder 42, which is the second element, is shortest, i.e., the state in which the axial dimension of the expansion / contraction device 8 is shortest, until the fastening force of the friction engagement portion 7 reaches a predetermined value.

[0165] Specifically, first, in the function curve f1 representing the first load characteristic, the gradient of the tangent at the first reference point P1 is set as the gradient, and a spring load function fa, which is a linear function passing through the first reference point P1, is found. This spring load function fa represents the relationship between the axial position of the inner ring 32 relative to the rotating cylindrical portion 13 and an estimated value of the load applied to the return spring 11.

[0166] Next, the axial position of the inner ring 32 with respect to the rotating cylindrical portion 13 is determined when the difference ΔF between the function curve f1 representing the first load characteristic and the spring load function fa reaches a predetermined value β. The difference ΔF corresponds to the load applied to the frictional engagement portion 7, i.e., the fastening force of the frictional engagement portion 7, out of the axial load F.

[0167] The axial position of the inner ring 32 with respect to the rotating cylindrical portion 13 when the difference ΔF becomes the predetermined value β is expressed as the sum position x A The clutch clearance C (=ΔD2) is calculated by calculating a second difference value ΔD2, which is the difference between the above values. The predetermined value β is determined in advance based on the desired performance of the friction clutch device 1 and other factors.

[0168] The friction clutch device 1 is controlled using the set load F0 of the return spring 11 adjusted as described above and the calculated clutch clearance C.

[0169] As described above, in the method for assembling the friction clutch device according to one embodiment of the present disclosure, during the assembly of the friction clutch device 1, there are two states: a state in which the stopper member 6 is not engaged with the engagement groove 12, and a state in which the stopper member 6 is engaged with the engagement groove 12 by a predetermined axial thickness T 35 The relationship (first load characteristic and second load characteristic) between the axial position of the inner ring 32 with respect to the rotating cylindrical portion 13 and the axial load F is determined by pressing the inner ring 32 to one side in the axial direction with the locking member 35 having the locking member 35 locked.Then, using the first load characteristic and the second load characteristic determined in this manner, the axial thickness T6 of the stopper member 6 and the clutch clearance C are determined, which allow the set load F0 of the return spring 11 to be a desired value.

[0170] That is, according to the method for assembling a friction clutch device of one aspect of the present disclosure, there is no need to temporarily assemble the members that make up the friction clutch device 1, measure the dimensions of each part, disassemble the device after the measurements, replace parts so that the set load of the return spring becomes the desired value, and then reassemble the device in order to determine the set load F0 of the return spring 11 and the clutch clearance C. This makes it possible to prevent the assembly cost of the friction clutch device 1 from increasing unnecessarily.

[0171] In particular, in this example, from among the multiple types of adjustment members 36 prepared, an appropriate adjustment member having an axial thickness T 36 and engages it with the locking groove 12 so as to be adjacent to the other axial side of the locking member 35, thereby adjusting the axial thickness T6 of the stopper member 6. Therefore, when the stopper member 6 is configured with a single retaining ring, it is not necessary to remove the retaining ring from the locking groove 12 and replace it with a retaining ring having a different axial thickness, which is required to adjust the axial thickness T6 of the stopper member 6. From this perspective as well, it is possible to prevent an increase in the assembly cost of the friction clutch device 1.

[0172] However, when carrying out the method for assembling a friction clutch device according to one aspect of the present disclosure, the stopper member may be configured as a single retaining ring. In this case, in the adjustment step, the axial thickness of the stopper member that can obtain the desired set load is determined, the locking member is removed from the locking groove, and then the stopper member having the axial thickness that can obtain the desired set load is locked into the locking groove.

[0173] Furthermore, in the method of assembling a friction clutch device according to one aspect of the present disclosure, the set load F0 of the return spring 11 is determined based on the application of an axial load to the return spring 11. This makes it easier to keep the error in the determined set load F0 small compared to when the set length of the return spring is determined by measuring the dimensions of each part of the friction clutch device and the set load is determined based on the set length using the spring characteristics of the return spring that have been determined in advance.

[0174] The assembly method of the friction clutch device 1 of this example optionally further includes a third load characteristic acquisition process and a confirmation process for confirming whether the set load F0 of the return spring 11 is at the desired value when the stopper member 6 is engaged with the engagement groove 12.

[0175] In the third load characteristic acquisition process, with the stopper member 6 consisting of the locking member 35 and the adjustment member 36 locked in the locking groove 12, the inner ring 32 is pressed toward one axial side to apply an axial load F to the inner ring 32, thereby acquiring the third load characteristic, which is the relationship between the axial position of the inner ring 32 relative to the rotating cylindrical portion 13 and the magnitude of the axial load F.

[0176] The third load characteristic acquisition process is performed using the same test equipment as the first load acquisition process and the second load acquisition process, and is basically the same as the first load acquisition process and the second load acquisition process. To achieve this, the selected adjustment member 36 is engaged with the locking groove 12 so as to be adjacent to the other axial side of the locking member 35, and then the pressing jig 87 is placed again on the side surface of the spacer 34 on the other axial side (see FIG. 20(A)). Next, the crosshead 88 is lowered at a constant speed, and the inner ring 32 is pressed toward one axial side via the pressing jig 87 and the spacer 34, thereby applying an axial load F to the inner ring 32. This obtains the relationship between the displacement of the crosshead 88 (the axial position of the inner ring 32 relative to the rotating cylindrical portion 13) and the axial load F (third load characteristic), as shown by the dashed line in FIG. 17.

[0177] As in the first load characteristic acquisition process and the second load acquisition process, the crosshead 88 is lowered, and the axial load F becomes 0 until its tip end surface (lower surface) abuts against the other axial side surface of the pressing jig 87. The axial load F then begins to increase immediately after the tip end surface of the crosshead 88 abuts against the other axial side surface of the pressing jig 87. In the third load acquisition process, the axial position of the inner ring 32 is restricted by the stopper member 6 made up of the locking member 35 and the adjustment member 36, so the amount of descent of the crosshead 88 until the axial load F starts to increase is greater than the amount of descent of the crosshead 88 until the axial load F starts to increase in the first load characteristic acquisition process and the second load acquisition process.

[0178] In addition, in the third load acquisition process, the axial position of the inner ring 32 is regulated by the stopper member 6 consisting of the locking member 35 and the adjustment member 36, and the return spring 11 is elastically compressed, so that the increase in the axial load F per unit movement of the crosshead 88 (the slope of the tangent to the function curve f3 representing the third load characteristic) immediately after the tip surface of the crosshead 88 abuts against the other axial side surface of the pressing jig 87 is larger than in the first load acquisition process and the second load acquisition process.

[0179] As the crosshead 88 is further lowered, as shown in FIG. 20(B), when the side surface of the stopper member 6 on the other axial side of the adjustment member 36 separates from the side surface of the inner surface of the locking groove 12 facing one axial side, the reaction force component of the elastic force of the return spring 11, which is caused by the return spring 11 being compressed due to the presence of the stopper member 6, becomes zero. This causes the increase in the axial load F per unit movement of the crosshead 88 to become gentle. In other words, a third reference point P3 appears on the function curve f3 representing the third load characteristic, where the increase in the axial load F begins to become gentle; specifically, where the change in the axial load F per unit movement of the inner ring 32 becomes equal to or less than a predetermined third threshold T3. The third threshold T3 can be determined in advance by experiment or calculation. The axial position at the third reference point P3 is determined by the sum position x A Approximately equals.

[0180] The third load characteristic becomes substantially the same as the first load characteristic and the second load characteristic after the side surface on the other axial direction of the adjustment member 36 separates from the side surface facing one axial direction of the inner surface of the locking groove 12. In other words, in the range where the amount of descent of the crosshead 88 is greater than the third reference point P3 (where the inner ring 32 is positioned on one axial side), the function curve f3 representing the third load characteristic substantially coincides with the function curve f1 representing the first load characteristic and the function curve f2 representing the second load characteristic.

[0181] The third load characteristic needs to be acquired at least until the axial load F increases to the predetermined value α. In this example, the third load characteristic is acquired until the axial load F reaches the predetermined value γ.

[0182] In the confirmation process, first, a confirmation reference axial position x is determined, which is the axial position of the inner ring 32 with respect to the rotating cylindrical portion 13 (the displacement amount of the crosshead 88) at the point where the axial load F increases to a predetermined value α on the function curve f3 representing the third load characteristic. α3 Next, in the function curve f1 representing the first load characteristic, the confirmation reference direction position x α3 It is confirmed whether the difference between the axial load F at the time of the friction clutch device 1 and the desired set load F0 is within a predetermined error range. Note that the error range is determined in advance based on the required performance of the friction clutch device 1, etc.

[0183] According to this example, by carrying out procedures similar to the first load characteristic acquisition process and the second load characteristic acquisition process performed to determine the axial thickness of the stopper member 6, it is possible to confirm whether the set load F0 of the return spring 11 is at the desired value.

[0184] By carrying out the assembly method of the friction clutch device 1 of this example, it is also possible to find the set length L, which is the axial length of the return spring 11 in a state where the pressing member 9 is not applying a force pressing the first friction plate 37 and the second friction plate 38 against each other. However, from the viewpoint of controlling the friction clutch device 1, the set length L is not necessarily required.

[0185] First, the difference is calculated between the axial position of the inner ring 32 relative to the rotating cylinder portion 13 at the point where the axial load F begins to increase as the tip surface of the crosshead 88 abuts against the side surface on the other axial side of the pressing jig 87 on the function curve f3 representing the third load characteristic, and the axial position of the inner ring 32 relative to the rotating cylinder portion 13 at the point where the axial load F begins to increase as the tip surface of the crosshead 88 abuts against the side surface on the other axial side of the pressing jig 87 on the function curve f1 representing the first load characteristic.

[0186] Specifically, the difference ΔD2 is calculated between the axial position (displacement amount of the crosshead 88) x3 of the inner ring 32 relative to the rotating cylindrical portion 13 at the point where the axial load F rises to a predetermined value α on the function curve f3 representing the third load characteristic, and the axial position (displacement amount of the crosshead 88) x1 of the inner ring 32 relative to the rotating cylindrical portion 13 at the point where the axial load F rises to a predetermined value α on the function curve f1 representing the first load characteristic.

[0187] Next, the axial internal clearances of the radial rolling bearing 5, the cam support bearing 54, and the release bearing 10, as well as the amount of elastic deformation of each member constituting the friction clutch device 1 when a predetermined axial load F (=α) is applied, are subtracted from the difference ΔD2. This determines the amount of deflection ΔL, which is the difference between the axial length of the return spring 11 when nothing is locked in the locking groove 12 as shown in Figure 18, and the axial length of the return spring 11 when the stopper member 6 is locked in the locking groove 12 as shown in Figure 20(a).

[0188] The axial internal clearances of the radial rolling bearing 5, the cam support bearing 54, and the release bearing 10 can be measured in advance, for example, during their respective shipping inspections. Also, the amount of elastic deformation of each member constituting the friction clutch device 1 when a predetermined axial load F (=α) is applied can be determined in advance by experiment or calculation.

[0189] Then, the set length L of the return spring 11 can be obtained by subtracting the amount of deflection ΔL from the free length of the return spring 11, which has been measured in advance during the shipping inspection or the like.

[0190] 17 also shows the relationship between the displacement of the crosshead 88 and the axial load F when the axial load F is increased to a predetermined value as the crosshead 88 is lowered, and then the axial load F is reduced to 0 as the crosshead 88 is raised. However, from the perspective of adjusting the set load F0 of the return spring 11 and measuring the clutch clearance C, it is sufficient to obtain the relationship between the displacement of the crosshead 88 and the axial load F when the axial load F is increased to a predetermined value.

[0191] In addition, in the example shown in Figure 18, the second member 3 is not arranged around the friction engagement portion 7, but when carrying out the assembly method of the friction clutch device of one embodiment of the present disclosure, the first load characteristic acquisition process, the second load characteristic acquisition process, and the third load characteristic acquisition process may be carried out with the second member 3 arranged around the friction engagement portion 7. [Explanation of symbols]

[0192] 1, 1z Friction clutch device 2 First member 3 Second member 4 Support members 5 Radial rolling bearings 6 Stopper member 7 Friction engagement part 8. Expansion device 9 Pressing member 10 Release bearing 11 Return spring 12 Locking groove 13 Rotating cylinder 14 Large diameter cylinder 15 Small diameter cylinder part 16 Inner diameter step surface 17 Inner oil passage 18 Female spline part 19 Side plate part 20 First cylinder part 21 Inner diameter uneven part 22 Outer oil passage 23 Second cylinder part 24 Outer diameter side uneven part 25 Fixed cylinder part 26 Small diameter section 27 Large diameter section 28 Outer diameter step surface 29 Male spline part 30 Flange 31 outer ring 32 Inner circle 33 Rolling elements 34 spacer 35 Locking member 36 Adjustment member 37 1st friction plate 38 Second friction plate 39 Spacer 40 retaining ring 41 Drive cam 42 Holder 43 Rolling elements 44 Cam surface 45 Reference plane 46 Convex part 47 Flat surface part 48 Cam side stopper surface 49 Slope section 50 Electric Actuator 51 Gear section 52 Main body 53 Protrusion 54 Cam support bearing 55 Inner Circle 56 Outer ring 57 Rolling elements 58a, 58b through hole 59 Step surface 60 Holding part 61 Connecting part 62a, 62b Support plate part 63a, 63b connecting plate part 64a, 64b support hole 65 Locking hole 66 Female spline part 67 Holder side stopper surface 68 Rolling surface 69 Support shaft Around 70 71 Anti-slip member 72 Locking groove 73 Reducer 74 Warm 75 Small diameter cylinder part 76 Conical tube 77 Inner diameter circular ring 78 Medium diameter cylinder part 79 Outer ring part 80 Large diameter cylinder 81 Pressing part 82 outer ring 83 Inner circle 84 balls 85 spacer 86 tables 87 Pressing jig 88 Crosshead 100 Friction clutch device 101 Electric Actuator 102 Cam device 103 Drive Cam 104 Holder 105 Pressing member 106a, 106b 1st friction plate 107 Second friction plate 108 First member 109 Second member 110 Return spring 111 Support material 112 Rolling bearings 113 Inner circle 114 Retaining ring 115 Locking groove

Claims

1. a first member including a rotating cylindrical portion having a locking groove on an outer circumferential surface; a second member supported coaxially with the first member and capable of relative rotation with respect to the first member; a support member having a fixed cylindrical portion disposed coaxially around the rotating cylindrical portion and fixed to a portion that does not rotate during use; a radial rolling bearing including an outer ring fitted to the fixed cylindrical portion so as to be unable to displace in at least one axial direction relative to the fixed cylindrical portion, an inner ring fitted to the rotating cylindrical portion so as to be able to displace in the axial direction relative to the rotating cylindrical portion, and a plurality of rolling elements arranged between the outer ring and the inner ring; a stopper member that is engaged with the engagement groove and that prevents the inner ring from displacing toward the other axial side relative to the fixed cylindrical portion by bringing a side surface on one axial side of the stopper member into contact with a side surface on the other axial side of the inner ring directly or via another member; a friction engagement portion having at least one first friction plate and one second friction plate supported so as to be capable of relative displacement in the axial direction; an expansion / contraction device having a first element supported on the support member so as not to be displaceable in the axial direction, and a second element supported on the support member so as to be displaceable in the axial direction, and which expands and contracts a gap between the first element and the second element; a pressing member that faces a side surface on the other axial side of the friction plate that is located furthest on the other axial side among the first friction plate and the second friction plate, and is supported so as to be movable toward and away from the friction plate located furthest on the other axial side in the axial direction; a release bearing disposed between the second element and the pressing member; a return spring that elastically biases the pressing member toward the other axial side; Equipped with By increasing the gap between the first element and the second element, the first friction plate and the second friction plate are pressed against each other, thereby switching to a connection mode in which the first member and the second member rotate integrally, and by decreasing the gap between the first element and the second element, the force pressing the first friction plate and the second friction plate against each other is released, thereby switching to a disconnection mode in which the first member and the second member rotate relative to each other. A method for assembling a friction clutch device, comprising: a first load characteristic acquisition step of pressing the inner ring toward one axial side in a state where the stopper member is not engaged with the engagement groove to apply an axial load to the inner ring, thereby acquiring a first load characteristic which is a relationship between the axial position of the inner ring with respect to the rotating cylindrical portion and the magnitude of the axial load; a second load characteristic acquisition step of applying an axial load to the inner ring by pressing the inner ring toward one axial side with a locking member having a predetermined axial thickness locked in the locking groove, thereby acquiring a second load characteristic which is the relationship between the axial position of the inner ring with respect to the rotating cylindrical portion and the magnitude of the axial load; an adjusting process of determining an axial thickness of the stopper member based on a first difference value which is a difference between an axial position of the inner ring with respect to the rotating cylindrical portion when the axial load becomes equal to a desired set load under the first load characteristic, and an axial position of the inner ring with respect to the rotating cylindrical portion at a point where the axial load increases to a predetermined value under the second load characteristic; A method for assembling a friction clutch device, comprising:

2. the stopper member has the locking member, a side surface on one axial direction of which is in contact with a side surface on the other axial direction of the inner ring, either directly or via another member, and an adjusting member, which is disposed adjacent to the other axial side of the locking member and has a side surface on the other axial side of which is in contact with a surface of the inner surface of the locking groove that faces the one axial side, 2. The method for assembling a friction clutch device according to claim 1, wherein, in the adjusting step, an axial thickness of the adjustment member is determined based on the first difference value, and then the adjustment member is engaged with the engagement groove so as to be adjacent to the other axial side of the engagement member.

3. 2. The method for assembling a friction clutch device according to claim 1, further comprising a clutch clearance obtaining step of obtaining a clutch clearance which is an axial movement amount of the second element from a state where the distance between the first element and the second element is shortest until a fastening force of the friction engagement portion reaches a predetermined value, based on a combined position obtained by adding the first difference value to the axial position of the inner ring with respect to the rotating cylindrical portion at a first reference point where an amount of change in the axial load per unit movement amount of the inner ring in the first load characteristic is equal to or greater than a predetermined first threshold value, and a combined position obtained by adding the first difference value to the axial position of the inner ring with respect to the rotating cylindrical portion at a second reference point where an amount of change in the axial load per unit movement amount of the inner ring in the second load characteristic is equal to or less than a predetermined second threshold value.

4. In the clutch clearance obtaining process, a gradient of a tangent at the first reference point with respect to the first load characteristic is defined as the gradient, and a linear function passing through the first reference point is defined as a spring load function that is a relationship between the axial position of the inner ring with respect to the rotating cylindrical portion and the load applied to the return spring, 4. The method for assembling a friction clutch device according to claim 3, wherein the clutch clearance is calculated based on a difference between the axial position of the inner ring with respect to the rotating cylindrical portion when a difference between the first load characteristic and the spring load function reaches a predetermined threshold value, and the summed position.

5. a third load characteristic acquisition step of applying an axial load to the inner ring by pressing the inner ring toward one axial side with the stopper member engaged in the engagement groove, thereby acquiring a third load characteristic which is a relationship between the axial position of the inner ring with respect to the rotating cylindrical portion and the magnitude of the axial load; a confirmation step of determining a confirmation reference axial position, which is the axial position at which the axial load in the third load characteristic has increased to the predetermined value, and confirming whether a difference between the axial load in the confirmation reference axial position in the first load characteristic and the desired set load is within a predetermined error range; 10. The method of assembling a friction clutch device of claim 1, further comprising:

6. a first member including a rotating cylindrical portion having a locking groove on an outer circumferential surface; a second member supported coaxially with the first member and capable of relative rotation with respect to the first member; a support member having a fixed cylindrical portion disposed coaxially around the rotating cylindrical portion and fixed to a portion that does not rotate during use; a radial rolling bearing including an outer ring fitted to the fixed cylindrical portion so as to be unable to displace in at least one axial direction relative to the fixed cylindrical portion, an inner ring fitted to the rotating cylindrical portion so as to be able to displace in the axial direction relative to the rotating cylindrical portion, and a plurality of rolling elements arranged between the outer ring and the inner ring; a stopper member that is engaged with the engagement groove and that prevents the inner ring from displacing toward the other axial side relative to the fixed cylindrical portion by bringing a side surface on one axial side of the stopper member into contact with a side surface on the other axial side of the inner ring directly or via another member; a friction engagement portion having at least one first friction plate and one second friction plate supported so as to be capable of relative displacement in the axial direction; an expansion / contraction device having a first element supported on the support member so as not to be displaceable in the axial direction, and a second element supported on the support member so as to be displaceable in the axial direction, and which expands and contracts a gap between the first element and the second element; a pressing member that faces a side surface on the other axial side of the friction plate that is located furthest on the other axial side among the first friction plate and the second friction plate, and is supported so as to be movable toward and away from the friction plate located furthest on the other axial side in the axial direction; a release bearing disposed between the second element and the pressing member; a return spring that elastically biases the pressing member toward the other axial side; Equipped with the stopper member has a locking member having a side surface on one axial side thereof abutting against a side surface on the other axial side of the inner ring directly or via another member, and an adjusting member that is disposed adjacent to the other axial side of the locking member and has a side surface on the other axial side abutting against a surface of the inner surface of the locking groove that faces the one axial side, By increasing the gap between the first element and the second element, the first friction plate and the second friction plate are pressed against each other, thereby switching to a connection mode in which the first member and the second member rotate integrally, and by decreasing the gap between the first element and the second element, the force pressing the first friction plate and the second friction plate against each other is released, thereby switching to a disconnection mode in which the first member and the second member rotate relative to each other. Friction clutch device.

7. 7. The friction clutch device according to claim 6, further comprising a spacer disposed between said inner ring and said stopper member.

8. the first element is configured as a drive cam having a cam surface on one axial side thereof and rotatably supported by the support member, the second element is configured by a holder supported so as not to rotate relative to the support member, 7. The friction clutch device according to claim 6, wherein the expansion / contraction device has a rolling surface on its outer circumferential surface that is in rolling contact with the cam surface and further includes a plurality of rolling elements held by the holder, and the axial dimension of the expansion / contraction device is expanded / contracted by rotating the drive cam.

9. The friction clutch device according to claim 8, further comprising an electric actuator that rotationally drives the drive cam.

10. 7. The friction clutch device according to claim 6, wherein the return spring is formed of a leaf spring.

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