JP2001003955A - Starting clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To miniaturize a transmission, to secure the space to install a one-way clutch for a back stop, and to enhance the lubricity of the one-way clutch by use of a simple structure. SOLUTION: In this starting clutch 10, an input-side element 23 and an output- side element 21 are brought into frictional engagement with each other on receiving axial load. A non-rotating element 51 is positioned within the starting clutch and a one-way clutch 50 is provided between the non-rotating element 51 and output-side element portions 52, 16.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a starting clutch which can be used in place of a torque converter of a vehicle, for example, an automobile.

[0002]

2. Description of the Related Art FIG. 16 is an axial sectional view of a conventional starting clutch. The starting clutch 100 is a multi-plate clutch 101
It has. Clutch case 1 for multi-plate clutch 101
A friction plate 102 serving as an output-side frictional engagement element and a separator plate 103 serving as an input-side frictional engagement element are alternately arranged inside 06, and a backing plate 104 is arranged at an end thereof. The left side of the backing plate 104 in the figure is supported by a retaining ring 105. On the other hand, an O-ring 107 is provided between the friction engagement element and the inner wall of the clutch case 106 on the right side in the drawing.
, And is urged by a return spring 116 in the right direction in the figure, that is, in the releasing direction. A hydraulic chamber 109 is provided between the piston 108 and the clutch case 106.

The starting clutch 100 includes a multi-plate clutch 101 having the above-described structure, a housing 110 that covers the outer periphery of the multi-plate clutch 101, a clutch case 106 and a housing 1.
10 and a damper 117 installed between them. The housing 110 is connected to an output shaft 111 of the engine, and the damper 117 includes a spring 130, a retainer plate 113 that holds the spring 130, and a claw 114 that fits into the spring 130.

The above-described starting clutch 100 is provided with an oil passage 115
When the hydraulic pressure is supplied to the hydraulic chamber 109 through the piston 108, the piston 108 operates to perform frictional engagement.

FIG. 17 is a schematic sectional view showing the arrangement of a conventional one-way clutch for preventing backward movement, and is for backstop for preventing backward movement when the vehicle starts on a slope. An output shaft 210 is disposed inside the transmission 200, and a one-way clutch 220 is provided between the output shaft 210 and a member fixed to the transmission case 230.

However, in recent years, there has been a demand for downsizing of transmissions, and it is necessary to respond to this demand. Further, as miniaturization progresses, it becomes difficult to secure a space for installing the above-described one-way clutch and to supply lubricating oil to the one-way clutch. Further, when a one-way clutch is arranged on the output shaft of the transmission, it becomes particularly difficult to supply lubricating oil to the one-way clutch. It is necessary to provide a mechanism that cuts off the torque so that the one-way clutch does not engage when the driver puts the gear into the reverse and reverses the vehicle at his / her own will.

[0007]

SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to reduce the size of a transmission, secure an installation space for a one-way clutch for a backstop, and improve the lubricity of the one-way clutch with a simple structure. It is an object of the present invention to provide a starting clutch capable of performing the following.

[0008]

In order to achieve the above object, the starting clutch of the present invention frictionally engages the input side element (23) and the output side element (21) by receiving an axial load. In the starting clutch (10), a non-rotating element (51) is arranged on the starting clutch, and a one-way clutch (50) is provided between the non-rotating element and an output-side element part (52, 16). Features.

Further, a non-rotating element is arranged on the starting clutch, and a spiral groove is formed in the output-side element portion facing the non-rotating element.

Further, the output-side element portion has an outer peripheral surface which is a sliding surface of the member for applying the load, an inner peripheral surface fitted to the output shaft by a spline, and an annular race surface having an outer raceway surface of the one-way clutch. The end of the non-rotating element is located in the recess, and the end is an inner raceway surface of the one-way clutch.

[0011] A lubrication path is provided between the output-side element portion and the non-rotating element so as to communicate with the portion where the one-way clutch is disposed.

The output side element portion and the clutch case are fixed by welding, and a gap is provided adjacent to the welded portion and penetrating to the outer peripheral side.

A concave portion adjacent to the spline is machined on the inner periphery of the output-side element portion, and a hole penetrating from the concave portion to the side surface of the output-side element portion is provided.

An O-ring is interposed between the recess and the output shaft on both sides of the spline in the axial direction.

The load is transmitted through an oil passage provided on the output shaft, an oil passage penetrating from the inner periphery to the side surface of the output-side element portion, and a gap between the output-side element portion and the clutch case. Supply hydraulic pressure to generate.

[0016]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A wet multi-plate clutch is used as a clutch in which an input side element and an output side element are frictionally engaged.
In addition, `` non-rotating element '' means that a member corresponding to the inner ring of the one-way clutch is fixed to a shaft fixed to the case of the transmission, and `` output side element part '' is a member fixed to the output shaft, The inner circumference corresponds to the outer raceway surface of the one-way clutch, and the outer circumference serves as the sliding surface of the piston of the wet multi-plate clutch. Further, a spiral groove is formed in the cylindrical portion on the inner peripheral side of the member corresponding to the outer ring of the one-way clutch, and a pumping function is added by opposing the inner peripheral surface of the member corresponding to the inner ring. For convenience of explanation, a member having a function corresponding to the inner ring of a general one-way clutch is hereinafter referred to as an “inner ring member”, and a member having a function corresponding to the outer ring of the one-way clutch is referred to as an “outer ring member”.

[0017]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a starting clutch according to the present invention will be described in detail with reference to the accompanying drawings. In the drawings, the same parts are denoted by the same reference numerals.

(First Embodiment) FIG. 1 is an axial sectional view showing a starting clutch according to a first embodiment of the present invention. The starting clutch 10 includes a wet multiple disc clutch 20 including a plurality of friction engagement elements (friction plates). Wet multi-plate clutch 2
Numeral 0 includes a clutch case 26 and a hub 27 that rotates relative to the clutch case 26. Clutch case 2
A spline portion 45 is formed on the inner periphery of 6, and the substantially annular separator plate 23, which is a friction engagement element on the output side, is fitted to the spline portion 45 so as to be movable in the axial direction.

The hub 27 of the wet multi-plate clutch 20 has cylindrical portions 14 and 15 on the inner peripheral side and the outer peripheral side, respectively.
A friction plate 21 is fitted to the spline portion 17 engraved on the outer periphery of the cylindrical portion 14 so as to be movable in the axial direction. In addition, the cylindrical portion 14 has a housing 11 on its inner periphery.
And is slid in the axial direction within a range of an operating angle of a damper 40 described later. As can be seen from FIG. 1, it is a friction plate,
The separator plates 23 and the friction plates 21 are alternately arranged in the axial direction. A friction material (not shown) is fixed to both surfaces or one surface of the friction plate 23 in the axial direction.

A backing plate 22 is further provided at the axial ends of the separator plate 23 and the friction plate 21 and on the inner periphery of the clutch case 26. The backing plate 22 is supported by a retaining ring 30 on the right side in the axial direction of FIG. 1 and is restricted from moving outward in the axial direction. On the other hand, an O-ring 32 is provided between the friction engagement element and the inner wall of the clutch case 26 on the left side in FIG.
The piston 24 is disposed through the
A hydraulic chamber 28 is defined between the hydraulic chamber 28 and the clutch case 26. On the outer peripheral side of the hydraulic chamber 28, a pressing spring 31 that constantly urges the piston 24 in the right direction in FIG. 1, that is, in the direction in which the friction engagement element is fastened, is provided.

The starting clutch 10 includes the multi-plate clutch 20 having the above structure, a housing 11 for covering the outer periphery of the multi-plate clutch 20, and a damper 40 disposed between the hub 27 and the housing 11. The housing 11 is attached to the driven plate 12 on the side opposite to the output shaft of the engine (not shown), and the damper 40 is attached to the claw 43 attached to the outer periphery of the hub 27, and attached to the housing 11, The spring 41 is held by a plate 42, and the spring 41 and the claw 43 are elastically engaged.

The above-described starting clutch 10 is provided with oil passages 71, 7
When the hydraulic pressure is supplied to the hydraulic chamber 28 through the pressure 2, the pressing force of the piston 24 increases, and the wet multi-plate clutch 20 is engaged. However, even when the hydraulic pressure is released, the piston 24 engages the frictional engagement element by the pressing force of the pressing spring 31, so that a predetermined creep torque exists.

2 to 9 show a one-way clutch 50 used in the present invention. FIG. 2 is a front view of the one-way clutch 50. FIG. The one-way clutch 50 includes an inner race member 52 having an annular outer raceway surface, and an outer race member 51 disposed outside the inner race member 52 and having an annular inner raceway surface facing the outer raceway surface of the inner race member 52.
A sprag 53 disposed between the outer raceway surface and the inner raceway surface for transmitting torque between the inner and outer race members, a ribbon spring 60 for applying a rising moment to the sprag 53, and an outer retainer for retaining the sprag 53 Vessel 5
8, inner retainer 56, inner ring member 52 and outer ring member 51
And an end bearing 85 for keeping concentricity.

FIG. 3 shows the one-way clutch 5 shown in FIG.
0 is a perspective view showing a part of the ribbon spring 60 of FIG.
FIG. 4 is a perspective view showing a state where the sprag 53 is arranged on the ribbon spring 60 of FIG. 3, and is also a perspective view of the sprag 53. The ribbon spring 60 includes two side bars 62 arranged at a predetermined distance in the axial direction, and a plurality of crossbars 6 integrally connecting the two side bars 62.
And 1. As a result, a plurality of rectangular windows are defined by the side bar 62 and the cross bar 61 at substantially equal intervals in the circumferential direction. The crossbar 61 includes a protrusion 66 extending from the crossbar 61 in the circumferential direction at a predetermined length. A wrinkle 63 that generates a spring force for applying a rising moment to the sprag 53 is provided between the protrusion 66 and the crossbar 61. Also, the protrusion 66
Has a tab 64 for supporting the sprag 53.

As shown in FIG. 4, the sprag 53 is disposed in a window 67 defined by the cross bar 61 and the side bar 62 of the ribbon spring 60, and is supported by a tab 64. Also, the sidebar 62 and the crossbar 61
At the corner of window 67 at the intersection with
An escape portion 65 for escaping the corner of No. 3 is provided. When the one-way clutch 50 is located at a predetermined position, the tab 64 contacts the sprag 53 with the constricted portion 68 of the sprag 53 and urges the sprag 53 by the spring force of the wrinkle 63. In addition, the gourd-shaped sprag 54 is the outer ring member 51.
The cam surface 54 engages with the inner peripheral raceway surface, the constricted portion 68 supported by the tab 64, and the cam surface 55 engages with the outer peripheral raceway surface of the inner race member 52.

FIG. 5 is a perspective view of the outer retainer 58 of the one-way clutch 50 used in the present invention, and FIG.
FIG. 3 is a perspective view of an inner retainer 56 of the one-way clutch 50 used in the present invention. The substantially annular outer retainer 58 includes
An elastic piece that protrudes radially outward and rubs against the inner circumferential raceway surface of the outer ring member 51 in order to generate an appropriate drag torque between the window 59 in which the sprag 53 is disposed, the flange 91, and the outer ring member 51. 81. On the other hand, the inner retainer 56 has a window 57 for disposing the sprag 53 and a flange 9.
And 2. The inner and outer retainers 56 and 58 hold the ribbon spring 60 holding the sprag 53 in an annular shape and prevent the sprag 53 from excessively moving.

FIG. 7 is a perspective view of an end bearing 85 used in the one-way clutch 50. End bearings 85 are folded back portions 86 and 8 on the inner and outer peripheral sides, respectively.
Seven. The end bearing 85 prevents a change in clearance between the inner ring member and the outer ring member due to vibration, maintains the inner and outer ring members substantially concentrically, and gives an appropriate clearance to the sprag 53. Thereby, the one-way clutch 5
The operation of 0 is performed reliably.

FIG. 8 is a side view showing an outer ring member 52 used in each embodiment of the present invention, and FIG.
FIG. The outer ring member 52 has a cam surface 54 of the sprag 53 of the one-way clutch 50 on a cylindrical portion on the outer peripheral side.
A one-way clutch 50, a sliding surface 94 that rubs against the piston 24 and the O-ring 32,
And an annular groove 97 into which a snap ring (see FIG. 1) for retaining the screw is fitted. A portion having a spiral groove 96 in an inner cylindrical portion and a portion not having the spiral groove 96 are provided. 93. When the outer ring member 52 rotates together with the output shaft 16 (see FIG. 1), the spiral groove 96 performs a pump function, and supplies lubricating oil to the one-way clutch 50.

Next, the lubrication route to the wet multi-plate clutch 20 and the one-way clutch 50 will be described. FIG.
0 is an enlarged sectional view of a portion where the one-way clutch 50 shown in FIG. 1 is installed. The lubrication path includes a path A for directly supplying the lubricating oil to the wet multi-plate clutch 20 and a one-way clutch 5.
And a path B for supplying lubricating oil to the lubricating oil. The path A is defined in a gap between the housing 11 and the inner ring member 51, and the path B is defined in a gap between the inner ring member 51 and the outer ring member 52. The inner ring member 51 has a radial through hole 75 communicating with the path B. In addition, since the outer race member 52 rotates while the inner race member 51 is fixed, the gap between the inner race portion 51 and the inner peripheral portion of the inner race member 51 has a pump function by the spiral groove 96 of the outer race member 52 described above. 80. The pump 80 can provide sufficient lubrication to the one-way clutch 50. The outer ring member 52 and the output shaft 16 are fitted with splines.

(Second Embodiment) FIG. 11 is an axial sectional view showing a starting clutch according to a second embodiment of the present invention. Since the basic configuration is almost the same as that of the first embodiment and the conventional example, the same symbols are used in the drawings, and only different points will be described.

In the second embodiment, no pressing spring for generating a creep torque is provided. Instead, a return spring 29 that biases the piston 24 to the left in the drawing, that is, the direction in which the wet multi-plate clutch 20 is released, is provided below the piston 24. Accordingly, when the hydraulic pressure is released, the piston 24 is moved leftward in the figure by the return spring 29.

(Third Embodiment) FIG. 12 is an axial sectional view showing a starting clutch according to a third embodiment of the present invention. The basic configuration is almost the same as the above-described first and second embodiments and the conventional example. Therefore, the same symbols are used in the drawings, and only different points will be described. Needless to say, the inclination angle, the number, and the like of the spiral grooves 96 can be arbitrarily set in consideration of the balance of the amount of lubricating oil supplied to the paths A and B.

In the third embodiment, the configuration of the outer race member 52 of the one-way clutch 50 and the configuration of the piston 24 are different from the above-described embodiments. The outer ring member 52 is partially fixed to the clutch case 26 by welding at a position where it contacts the clutch case 26. As shown in FIG. 13, the outer ring member 52 in this embodiment has a welded portion 76 and a groove 77 alternately adjacent to the substantially annular surface of the outer peripheral flange portion that abuts the clutch case 26 in the circumferential direction at substantially equal intervals. It is provided. Welded part 76 to clutch case 2
The outer ring member 52 is fixed to the clutch case 26 by welding to the clutch case 26.

A spline 78 is engraved on the inner periphery of the outer ring member 52, and the spline 78
And are spline-coupled to each other and movably fitted in the axial direction. A hole 72 having a predetermined angle in the axial direction is opened at one axial end of the outer race member 52 on the clutch case 26 side. As shown in FIG. 13, a plurality of holes 72 are provided substantially equally in the circumferential direction. As with the welded portion 76 and the groove 77, the number of the holes 72 may be other than the number shown.

As shown in FIG. 14, the outer ring member 52 has an annular shape in which the snap ring of the one-way clutch 50 is fitted at one axial end of the outer peripheral flange portion and on the inside opposite to the groove 77 and the welded portion 76. Of the inner peripheral cylindrical portion 84 in which the spline 78 is provided.
An annular groove 7 into which an O-ring 45 (see FIG. 15) fits is formed on the inner periphery of the groove 77 and the axial end opposite to the welded portion 76.
9 are provided. Further, an annular groove 83 into which the O-ring 46 (see FIG. 15) is fitted is provided on the inner periphery of the axial end on the same side as the groove 77 and the welded portion 76 of the inner peripheral cylindrical portion 84.

The hole 72 is formed in the spline 7 of the inner cylindrical portion 84.
Since the hole 72 and the spline 78 communicate with the annular space 89 provided adjacent to the nozzle 8, the spline 78 can be lubricated with the lubricating oil.
In addition, the space 89 is a space where the lubricating oil is stored and the oil pool and the spline 78 are escaped. Therefore, the manufacturing cost can be reduced. The inner ring member 51 is spline-coupled to the output shaft 16 by a spline portion 88, and is moved in the axial direction with respect to a resin washer 59 provided at both ends or one end in the axial direction of the inner ring member 51.
The range is regulated.

Next, the details of the lubricating path through which the lubricating oil and the hydraulic oil of FIG. 12 pass will be described with reference to FIG. 15 which is an enlarged sectional view. Lubricating oil from a hole in the output shaft 16 flows into the hole 72 via the space 89 and enters a gap defined between the outer race member 52 and the clutch case 26. At this time, the O-rings 45 and 46 are provided at two locations in the axial direction between the outer ring member 52 and the output shaft 16 and are sealed, so that the lubrication path is almost oil-tight. Accordingly, each part such as the spline 78 can be sufficiently lubricated, so that wear can be prevented. Thereafter, the lubricating oil flows into the hydraulic chamber 28 through the groove 77 of the outer ring member 52, generates a predetermined oil pressure, presses the piston 24 in the axial direction, and frictionally engages the friction plate 21 with the friction plate 21 and the separator. The plate 23 is frictionally engaged.

Further, the piston 24 engaging the friction engagement elements presses the separator plate 23 with a pressing portion 69 protruding in the axial direction, thereby achieving the engagement between the friction engagement elements. The piston 24 is formed by two O-rings 48 and 49 provided at both ends in the radial direction, respectively.
Since the oil-tight state is maintained, the oil pressure in the hydraulic chamber 28 does not leak. In the third embodiment, the piston 24
FIG. 1 shows a leaf spring 46 as a return spring.
At 5, it is biased to the left. Therefore, when the hydraulic pressure in the hydraulic chamber 28 is equal to or lower than the predetermined pressure, the leaf spring 46 moves the piston 24 in the direction in which the hydraulic chamber 28 is crushed.
That is, it moves in a direction to release the engagement between the friction engagement elements. Needless to say, the leaf spring 46 can be replaced with, for example, a disc spring or another spring.

The one-way clutch 50 used in the above-described first and third embodiments is a double-cage type having an outer and an inner retainer, but is a single-cage or one-way without a retainer. A clutch can also be used. Further, it goes without saying that a one-way clutch having a sprag other than the gourd type shown in each embodiment can be used.

[0040]

The starting clutch of the present invention described above has the following features.
The following effects are obtained.

According to the first and second aspects of the present invention, there is no need to provide a reversing switching mechanism, and a one-way clutch for preventing retraction can be provided without increasing the axial dimension.

According to the third aspect of the present invention, a lubrication path to the one-way clutch can be secured with a simple configuration.

According to the fourth aspect of the invention, the one-way clutch can be sufficiently lubricated.

According to the fifth aspect of the present invention, a starting clutch capable of performing sufficient lubrication even with a narrow lubricating oil can be obtained.

According to the sixth and seventh aspects of the present invention, the one-way clutch mechanism can be disposed in the inner peripheral space of the hub in which the friction engagement elements are disposed, so that the one-way clutch can be disposed. There is no need to increase the size of the conventional starting clutch.

According to the eighth aspect of the present invention, a hydraulic pressure for applying a load for tightening the starting clutch is supplied while increasing the mounting strength of the output side element portion without increasing the axial dimension of the device. Can be.

According to the ninth aspect of the present invention, the manufacturing cost can be reduced and the labor can be saved.

According to the tenth aspect, it is possible to suppress wear of the spline fitting portion between the output shaft and the output-side element portion.

According to the eleventh aspect, a hydraulic supply path can be provided in a small space.

[Brief description of the drawings]

FIG. 1 is an axial sectional view showing a starting clutch according to a first embodiment of the present invention.

FIG. 2 is a front view of a one-way clutch.

FIG. 3 is a perspective view of a ribbon spring of the one-way clutch.

FIG. 4 is a perspective view of a ribbon spring and a sprag in which sprags are arranged.

FIG. 5 is a perspective view of an outer retainer.

FIG. 6 is a perspective view of the inner retainer.

FIG. 7 is a perspective view of an end bearing.

FIG. 8 is a side view of the outer race member.

FIG. 9 is a front view of the outer race member.

FIG. 10 is an enlarged sectional view showing a lubrication path.

FIG. 11 is an axial sectional view showing a starting clutch according to a second embodiment of the present invention.

FIG. 12 is a front view showing an outer race member of a one-way clutch part of a starting clutch according to a third embodiment of the present invention.

FIG. 13 is a front view showing an outer race member of a one-way clutch portion of a starting clutch according to a third embodiment of the present invention.

FIG. 14 is an axial sectional view of the outer race member of FIG. 13;

FIG. 15 is an enlarged sectional view showing a lubrication path of a starting clutch according to a third embodiment of the present invention.

FIG. 16 is an axial cross section of a conventional starting clutch.

FIG. 17 is a schematic view showing an arrangement of a conventional one-way clutch for preventing backward movement.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Starting clutch 16 Output shaft 20 Wet multi-plate clutch 40 Damper 50 One-way clutch 51 Inner ring member 52 Outer ring member 96 Spiral groove

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Yoshihisa Harada 2345 Aino, Fukuroi-shi, Shizuoka NSK Warner Co., Ltd. F-term (reference) 3J057 AA04 BB04 CA12 CA20 GA11 GC06 GD30 HH01 HH02 JJ01

Claims (11)

[Claims] 1. A starting clutch in which an input side element and an output side element are frictionally engaged by receiving a load in an axial direction, wherein a non-rotating element is arranged on the starting clutch, and the non-rotating element and the output side A starting clutch in which a one-way clutch is provided between the starting clutch. 2. The starting clutch according to claim 1, wherein the non-rotating element is a shaft fixed to a transmission case or a member fixed to the shaft. 3. The starting clutch according to claim 2, wherein the shaft or a member fixed to the shaft is disposed between a housing of the starting clutch and an output shaft. 4. The starting clutch according to claim 1, further comprising a lubrication path for supplying lubricating oil to said one-way clutch. 5. The starting clutch according to claim 1, wherein a helical groove is formed in the output-side element portion facing the non-rotating element in the lubrication path. 6. The output-side element portion has an outer peripheral surface that is a sliding surface of the member that applies the load, an inner peripheral surface that is fitted to the output shaft by a spline, and an outer raceway surface of the one-way clutch. The starting clutch according to claim 1, further comprising an annular recess, wherein an end of the non-rotating element is located in the recess, and the end is an inner raceway surface of the one-way clutch. 7. The starting clutch according to claim 6, wherein a lubrication path communicating with a portion where the one-way clutch is disposed is provided between the output-side element portion and the non-rotating element. 8. The start according to claim 6, wherein the output-side element portion and the clutch case are fixed by welding, and a gap is provided adjacent to the welded portion and penetrates to the outer peripheral side. clutch. 9. An inner periphery of the output-side element portion is provided with a recess adjacent to the spline, and a hole penetrating from the recess to a side surface of the output-side element portion is provided. The starting clutch according to claim 6, wherein: 10. The starting clutch according to claim 6, wherein an O-ring is interposed between the concave portion and the output shaft on both outer sides in the axial direction of the spline. 11. An oil passage provided on the output shaft, an oil passage penetrating from the inner periphery of the output-side element portion to the side surface, and a gap between the output-side element portion and a clutch case. The starting clutch according to claim 6, wherein a hydraulic pressure for generating the load is supplied.