JP2011220499A - Power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a power transmission device that has a small number of parts with a simple structure, thereby reducing cost.SOLUTION: The power transmission device houses a driven plate 6, a torque damper 7 for connecting between the transmitting case 5 and the driven plate 6, and a clutch 8 for connecting the driven plate 6 and an output shaft 3. The driven plate 6 formed in an annular shape and the clutch inner 25 of the clutch 8 bending from the inner peripheral end of the driven plate 6 to one side direction of the same are integrally formed by press molding.

Description

  The present invention provides a transmission case driven from a crankshaft of an engine via a drive plate, a driven plate disposed so as to be relatively rotatable with the transmission case, a torque damper for connecting the transmission case and the driven plate, The driven plate and a clutch for connecting the output shaft are accommodated, and the clutch is disposed so as to surround the clutch inner and a cylindrical clutch inner connected to the driven plate. A clutch outer that is splined to the clutch inner, a drive friction plate that is slidably fitted to the clutch inner, and is arranged on the drive friction plate and is slidably fitted to the clutch outer. Friction coupling between the driven friction plates and these drive friction plates and driven friction plates, An improvement of constructed power transmission device and air to clutch actuation device.

  Such a power transmission device is already known as disclosed, for example, in Patent Document 1 below.

JP 2008-309335 A

  In such a conventional power transmission device, the coil spring of the torque damper and the drive and driven friction plate groups of the clutch are arranged in the axial direction, and the clutch inner is connected by a rivet to the intermediate member connected to the driven plate. The number of parts is large, which is an obstacle to cost reduction. In addition, since the torque damper and the clutch are arranged adjacent to each other in the axial direction, the entire apparatus is enlarged in the axial direction, making it difficult to make the system compact.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a power transmission device that has a small number of parts, can be simplified in structure, can be reduced in cost, and can be made compact. And

  In order to achieve the above object, the present invention provides a transmission case driven by a crank plate of an engine via a drive plate, a driven plate disposed to be rotatable relative to the transmission case, the transmission case and the driven case. A torque damper for connecting the plates and a clutch for connecting the driven plate and the output shaft are housed, and the clutch surrounds a cylindrical clutch inner connected to the driven plate and the clutch inner. A clutch outer that is splined to the output shaft, a drive friction plate that is slidably fitted to the clutch inner, and is disposed on the drive friction plate. Friction between a driven friction plate that is slidably fitted by spline and the drive friction plate and driven friction plate In the power transmission device comprising a clutch actuating device for connecting or releasing the frictional connection, the driven plate formed in an annular shape, and the clutch bent to one side from the inner peripheral end of the driven plate The first feature is that the inner and the inner are integrally formed by press molding.

  In addition to the first feature, the present invention has a second feature that the clutch is disposed radially inward of the torque damper.

  According to the first feature of the present invention, the number of parts is reduced and the structure is simplified by integrating the driven plate and the clutch inner bent from the inner peripheral end of the driven plate to one side thereof by press molding. Can be achieved and the cost can be reduced.

  According to the second feature of the present invention, the clutch is disposed radially inward of the torque damper, so that the power transmission device can be flattened in the axial direction and compact.

The longitudinal cross-sectional view of the power transmission device which concerns on embodiment of this invention. FIG. 2 is an enlarged sectional view taken along line 2-2 in FIG. 1.

  Embodiments of the present invention will be described below with reference to the accompanying drawings.

  1 and 2, a power transmission device 1 is interposed between an engine crankshaft 2 and an output shaft 3 arranged coaxially with the engine crankshaft 2. It comprises an annular driven plate 6 disposed in a relatively rotatable manner therein, a torque damper 7 for connecting the transmission case 5 and the driven plate 6, and a clutch 8 for connecting the driven plate 6 and the output shaft 3. Yes.

  The transmission case 5 is formed by fitting the open ends of the pair of bowl-shaped first and second case halves 5a and 5b to each other and joining them in a fluid-tight manner by welding. Further, a ring gear 10 for starting the engine is fixed by welding, and a drive plate 13 connected to the shaft end of the crankshaft 2 by a first bolt 11 is connected to the ring gear 10 by a second bolt 12.

  The first case half 5a is integrally provided with a cup-shaped case hub 14 at the center, and the case hub 14 has a bottomed support that opens at the center of the shaft end of the crankshaft 2 on the outer peripheral surface thereof. The hole 2a is supported via the first bush 15 and the end of the output shaft 3 is rotatably supported via the second bush 16 on the inner peripheral surface. Thus, the crankshaft 2, the transmission case 5 and the output shaft 3 are arranged on the same axis.

  The torque damper 7 is provided in the driven plate 6 and arranged in the circumferential direction thereof, a plurality of spring holding holes 20, a plurality of coil springs 21 held in the holding holes 20, and the spring holding holes 20 of these coil springs 21. The spring housing recesses 22 and 22 are formed in the first and second case halves 5a and 5b, respectively, so as to accommodate and hold both side portions protruding from the housing. In the illustrated example, a double spring is used for each coil spring 21, but it can also be a single spring. In this way, the torque damper 7 is formed in an annular shape concentric with the output shaft 3.

  The clutch 8 includes a cylindrical clutch inner 25 and a clutch outer 26 disposed so as to surround the clutch inner 25, and the clutch inner 25 is formed from the inner peripheral end of the annular driven plate 6. It is formed integrally with the driven plate 6 by press molding so as to bend to one side. At that time, the spline 27 is simultaneously formed on the clutch inner 25.

  A support cylinder portion 30 that is rotatably fitted to the inner peripheral surface of the clutch inner 25 is press-molded integrally with the first case half 5a, whereby the clutch inner 25 and the driven plate 6 are concentric with the output shaft 3. Supported.

  The clutch outer 26 is fixed by welding to an outer body 26a concentrically surrounding the clutch inner 25, an outer end wall 6b integrally connected to one end of the outer body 26a, and an inner peripheral end of the outer end wall 6b. The outer hub 26c is provided. The outer body 26a and the outer end wall 6b are integrally formed by pressing, and at this time, the spline 28 is simultaneously formed on the outer body 26a. The clutch outer 26 is disposed radially inward from the annular array of coil springs 21. The outer hub 26c is spline-fitted to the output shaft 3 on one side and is supported on the output shaft 3 via the third bush 17 on the other side.

  A plurality of drive friction plates 31, 31 are slidably fitted on the outer periphery of the clutch inner 25, a plurality of driven friction plates 32, 32 alternately stacked with the drive friction plates 31, 31, and one sheet The pressure receiving plate 33 is slidably fitted to the inner periphery of the outer body portion 26a. A circlip 29 that receives and supports the pressure receiving plate 33 is engaged with the inner peripheral surface near the open end of the outer barrel portion 26a.

  The clutch outer 26 is provided with a clutch actuating device 34 that frictionally connects the drive friction plate 31 and the driven friction plate 32 or releases the frictional connection. The clutch actuating device 34 includes a cylinder 35 formed on the outer end wall 6 b of the clutch outer 26, and is slidably fitted to the cylinder 35 via a first seal member 36. A piston 38 that defines the chamber 37 is provided, and a pressure plate 39 that faces the pressure receiving plate 33 across the group of the driving and driven friction plates 31 and 32 is integrally connected to the piston 38. The piston 38 is slidably supported on the output shaft 3 via the second seal member 40 by the piston hub 38a at the inner peripheral end thereof.

  Further, an auxiliary cylinder 41 is formed on the piston 38 on the radially inner side of the pressure plate 39, and a fixed piston 43 is fitted to the auxiliary cylinder 41 via a third seal member 42 so as to be relatively slidable. The fixed piston 43 is received by a stopper ring 44 that is locked to the outer periphery of the outer hub 26c, and defines an auxiliary hydraulic chamber 45 between the fixed piston 43 and the auxiliary cylinder 41. A return spring 46 is contracted between the piston 38 and the fixed piston 43. The return spring 46 urges the piston 38 in the backward direction and holds the fixed piston 43 in a contact position with the stopper ring 44. To do.

  The output shaft 3 is provided with a first oil passage 50 that communicates with the hydraulic chamber 37 and a second oil passage 51 that communicates with the auxiliary hydraulic chamber 45. The first and second oil passages 50, 51 include Hydraulic pressure discharged from an oil pump (not shown) is alternately supplied. The second oil passage 51 opens at the shaft end of the output shaft 3 and communicates with the inside of the case hub 14.

  A first thrust washer 52 slidably contacts the inner surface of the first case half 5a at one end of the outer hub 26c, and slidable at the inner surface of the second case half 5b at the other end. A second thrust washer 53 that abuts is provided. Thus, the axial movement of the outer hub 26 c is restricted by the first and second case halves 5 a and 5 b, that is, the transmission case 5 via the first and second thrust washers 52 and 53. The first thrust washer 52 has a plurality of first oil grooves 52a facing the inner surface of the first case half 5a, and the second thrust washer 53 has a plurality of second oil grooves facing the inner surface of the second case half 5b. Oil grooves 53a are engraved respectively. The clutch inner 25 and the outer body 26a are respectively provided with a first oil hole 54 and a second oil hole 55 communicating with each other.

  The clutch 8 configured in this way is disposed radially inward of the annular torque damper 7.

  Next, the operation of this embodiment will be described.

  When the second oil passage 51 is opened to an oil tank (not shown) and the first oil passage 50 is connected to the discharge side of an oil pump (not shown), the oil discharged from the oil pump is introduced into the hydraulic chamber 37 through the first oil passage 50. With the hydraulic pressure, the piston 38 moves forward against the urging force of the return spring 46 and presses the driving and driven friction plates 31 and 32 against the pressure receiving plate 33. Therefore, the driving and driven friction plates 31 and 32 are Frictionally connected to each other. As a result, the clutch 8 is turned on to enable torque transmission between the clutch inner 25 and the clutch outer 26. Therefore, the engine power is transmitted from the crankshaft 2 to the output shaft 3 through the coil spring 21 of the torque damper 7, the driven plate 6, and the clutch 8 in the on state.

  During torque transmission, if torque fluctuations occur on the crankshaft 2 or load fluctuations occur on the output shaft 3 side, the relative rotation between the transmission case 5 and the driven plate 6, that is, the spring accommodating recesses 22, 22. And the torque fluctuation or the load fluctuation can be reduced by the compression deformation of the coil spring 21 accompanying the relative rotation between the spring holding holes 20.

  Contrary to the above, when the first oil passage 50 is opened to the oil tank and the second oil passage 51 is connected to the discharge side of the oil pump, the oil discharged from the oil pump passes through the second oil passage 51 and the auxiliary hydraulic chamber. 45, and the piston 38 is moved backward by the hydraulic pressure. At this time, the biasing force of the return spring 46 also assists the backward movement. Accordingly, the piston 38 is retracted quickly, and the frictional connection between the driving and driven friction plates 31 and 32 is released. As a result, the clutch 8 enters an OFF state in which torque transmission between the clutch inner 25 and the clutch outer 26 is cut off, and power transmission between the crankshaft 2 and the output shaft 3 can be cut off.

  The oil supplied to the second oil passage 51 also flows into the case hub 14 and passes through the first bush 15 between the case hub 14 and the output shaft 3 while being lubricated, and further the first oil of the first thrust washer 52. After passing through the groove 52a, it spreads in the radial direction due to centrifugal force action, and a part of the oil flows into the clutch 8 from the first oil hole 54 of the clutch inner 25 to lubricate each part of the clutch 8, After cooling, the oil flows out from the second oil hole 55 of the outer body 26a and the opening of the outer body 26a, and further spreads in the radial direction to lubricate each part of the torque damper 7. The other oil that has passed through the first oil groove 52a of the first thrust washer 52 lubricates the rotational sliding surfaces of the clutch inner 25 and the annular support cylinder 30 and then flows to the torque damper 7 side to lubricate it. While these oils fill the transmission case 5, they flow out of the transmission case 5 from the second oil groove 53a of the second thrust washer 53 and return to the oil tank, so that the transmission case 5 is always filled with new oil. Will be.

  By the way, in such a power transmission device 1, the driven plate 6 formed in an annular shape and the clutch inner 25 bent to one side from the inner peripheral end of the driven plate 6 are integrally formed by press molding. Therefore, the number of parts is reduced and the structure is simplified, and the cost can be reduced.

  In addition, by disposing the clutch 8 radially inward of the torque damper 7, the power transmission device 1 can be flattened in the axial direction and compact.

  Further, since the transmission case 5 is formed with a support cylinder portion 30 that is rotatably fitted to the inner peripheral surface of the clutch inner 25, the transmission case 5 functions as a bearing for the clutch inner 25 and the driven plate 6 integrated therewith. Therefore, the structure can be simplified and the cost can be further reduced.

  The present invention is not limited to the above embodiment, and various design changes can be made without departing from the scope of the invention.

1 ... Power transmission device 2 ... Crankshaft 3 ... Output shaft 5 ... Transmission case 6 ... Driven plate 7 ... ... Torque damper 8 ... Clutch 13 ... Drive plate 25 ... Clutch inner 26 ... Clutch outer 30 ... Support cylinder 31 ...・ Driving friction plate 32... Followed friction plate 34.

Claims (2)

The transmission case (5) driven from the crankshaft (2) of the engine via the drive plate (13), the driven plate (6) disposed so as to be rotatable relative to the transmission case (5), and the transmission A torque damper (7) for connecting the case (5) and the driven plate (6) and a clutch (8) for connecting the driven plate (6) and the output shaft (3) are accommodated. 8) A cylindrical clutch inner (25) connected to the driven plate (6), and a clutch arranged so as to surround the clutch inner (25) and spline-coupled to the output shaft (3) The outer (26), the drive friction plate (31) slidably fitted to the clutch inner (25), and the drive friction plate (31) are disposed on top of each other. A clutch that engages and disengages the driven friction plate (32) slidably splined to the clutch outer (26), and the drive friction plate (31) and the driven friction plate (32). In the power transmission device comprising the actuating device (34),
The driven plate (6) formed in an annular shape and the clutch inner (25) bent to one side from the inner peripheral end of the driven plate (6) are integrally formed by press molding. Power transmission device. The power transmission device according to claim 1,
The power transmission device according to claim 1, wherein the clutch (8) is disposed radially inward of the torque damper (7).

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