JP2010242824A - Dust discharging structure of clutch - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a dust discharging structure of a clutch capable of preventing the sticking of abrasion powder even if the abrasion powder cannot be released to air and suppressing the defective operation of the clutch and the progress of the abrasion of a spline part. <P>SOLUTION: The dust discharging structure of the clutch includes a first clutch CL1 that axially presses a driven plate 11 and a drive plate 12 by a hydraulic actuator 13 to provide a fastened state that the plates 11, 12 are axially pressed. Abrasion powder discharging guide grooves 11b, 12b for guiding abrasion powder in the outer radial direction are formed on the driven plate 11 and the drive plate 12 in the outer radial direction. A guide taper surface 24b that is gradually displaced axially in the outer diameter direction is formed at an outer plate support 24 that supports the outer circumference of the driven plate 11. A collecting space 8 for collecting the abrasion powder is formed at a drying chamber 55b connected to an end of the guide taper surface 24b. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a technique for discharging friction powder (dust) generated on a clutch disk in a dry clutch.

Conventionally, as a dust discharge structure of a clutch, for example, one described in Patent Document 1 is known.
In this prior art, the inner peripheral end mounting portion of the flywheel is fixed to the end portion of the crankshaft, the outer peripheral frictional engagement surface is frictionally engaged with the facing of the clutch disc, and is connected to the output shaft via the clutch disc. It was transmitting power. A dust receiving portion that surrounds the output shaft and extends toward the clutch disk is formed on the outer peripheral side of the inner peripheral end mounting portion. Further, a dust hole penetrating from the side surface on the clutch disc side to the side surface on the opposite side is formed in the inner peripheral end mounting portion on the inner peripheral side of the dust receiving portion. Thereby, the splash of grease and the facing wear powder that are scattered radially outward from the output shaft by the centrifugal force are captured by the dust receiving portion, and discharged from the dust hole to the outside.

Japanese Utility Model Publication No. 5-54849

  However, in the above-described prior art, since the generated abrasion powder is released to the atmosphere using the centrifugal force generated by the rotation of the dry clutch, there is no escape place for the abrasion powder on the same circumference, or the atmosphere When it cannot be opened, the wear powder is clogged, which may cause malfunction of the clutch and accelerated wear of the spline portion.

  The present invention has been made paying attention to the above problems, and provides a dust discharge structure for a clutch that can prevent clogging of wear even when it cannot be released to the atmosphere, and that can suppress malfunction of the clutch and promotion of wear of the spline part. For the purpose.

  In order to achieve the above object, the present invention includes a clutch that presses the first plate member and the second plate member in the axial direction by pressing means to form a fastening state in which both plate members are pressed in the axial direction, At least one of the first plate member and the second plate member is formed with a wear powder discharge guide groove in the outer diameter direction for guiding the wear powder generated by the friction of both plate members in the outer diameter direction, and the outer periphery of the first plate member A collecting taper that collects wear powder in a space continuous with the tip of the guide taper surface is formed on the outer plate support that supports the guide taper surface that is gradually displaced in the outer diameter direction along the axial direction. The dust discharge structure of the clutch is characterized by providing a portion.

In the dust discharge structure of the clutch according to the present invention, the wear powder generated by rubbing the two plate members when the clutch is engaged is accumulated in the wear powder discharge guide groove, and the centrifugal force when the two plate members rotate. By this, it guide | induces to an outer diameter direction along an abrasion powder discharge | release guide groove, and also guide | induces to the outer side plate support part located in an outer diameter direction.
The wear powder guided to the outer plate support portion moves along the inclination of the guide taper surface toward the collection space portion when the first rotating body rotates. As a result, the wear powder can be discharged and collected without opening to the atmosphere.
Therefore, even when the atmosphere cannot be released, it is possible to prevent clogging of wear, and to suppress malfunction of the clutch and acceleration of wear of the spline part.

It is sectional drawing which shows the principal part of the dust discharge structure of the clutch of Example 1. FIG. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a system diagram showing a main part of a rear-wheel drive parallel hybrid vehicle to which a clutch dust discharging structure of Example 1 is applied. It is a front view which shows the driven plate 11 as a 1st plate member used for the dust discharge structure of the clutch of Example 1. FIG. It is a front view which shows the drive plate 12 as a 2nd plate member used for the dust discharge structure of the clutch of Example 1. FIG.

    Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  The dust discharge structure of the clutch according to the embodiment of the present invention is provided on the first rotating body (2) and the second rotating body (14) that can rotate coaxially, and the first rotating body (2), and the inner diameter direction. And the outer plate support portion (24) formed with the outer plate support portion (24) facing the outer plate support portion (24) at the position in the inner diameter direction of the outer plate support portion (24). The spline teeth (11a) are engaged with the inner plate support portion (15) provided and the spline grooves (24a) formed in the outer plate support portion (24), and are movable in the axial direction. A plurality of first plate members (11) supported by movement in the circumferential direction and spline grooves formed between the first plate members (11) and formed in the inner plate support portion (15). Splice to (15a) A plurality of second plate members (12), which are movable in the axial direction by engaging teeth (12a) and supported by movement in the circumferential direction, and both plate members (11, 12). A clutch (CL1) having a pressing means (13) that presses in the axial direction to form a fastening state in which both plate members (11, 12) are pressed in the axial direction, and both plate members (11, 11, At least one of 12) is provided with wear powder discharge guide grooves (11b, 12b) in the outer diameter direction for guiding the wear powder generated by the friction of both plate members (11, 12) in the outer diameter direction, and the outer plate support A guide taper surface (24b) that is gradually displaced in the outer diameter direction along the axial direction is formed in the portion (24), and the space portion (55b) that continues to the tip of the guide taper surface (24b) Collect empty to collect wear powder A dust discharge structure of the clutch, characterized in that the section (8) is provided.

  The clutch dust discharge structure of the first embodiment of the present invention will be described with reference to FIGS.

 FIG. 2 is a system diagram showing a main part of a rear-wheel drive parallel hybrid vehicle to which the clutch dust discharging structure of the first embodiment is applied.

  The drive system of the parallel hybrid vehicle of the first embodiment includes an engine Eng, a first clutch CL1, a motor generator MG, a transmission T / M, and a second clutch CL2, as shown.

  The engine Eng is a gasoline engine or a diesel engine, and the engine output shaft 1 is provided with a flywheel FW.

The motor generator MG is a synchronous motor generator including a rotor (first rotating body) 2 including a permanent magnet 21 and a stator 3 around which a stator coil is wound.
The motor generator MG can operate as an electric motor that rotates by receiving power supplied from a battery (not shown). When the rotor 2 receives rotational energy, an electromotive force is generated at both ends of the stator coil. It functions as a generator that causes the battery to be charged.

  The motor generator MG is disposed at a position between the transmission T / M and the engine Eng inside the transmission case 9 that houses the transmission T / M, and together with the first clutch CL1, the motor housing 5 Is enclosed in a closed space 55 surrounded by

  The rotor 2 is coupled to the transmission input shaft 4, and the transmission input shaft 4 is rotatable by the driving force of the motor generator MG, and the driving force transmitted from the driving wheel side (not shown) is It is formed to be able to transmit to the rotor 2.

  As shown in FIG. 1, the rotor 2 is integrally coupled to a substantially disk-shaped partition disk portion 22 that extends in the outer diameter direction from the tip of the transmission input shaft 4 and the outer periphery of the partition disk portion 22. A cylindrical drum portion 23, and a permanent magnet 21 is embedded in the outer periphery of the drum portion 23.

  Returning to FIG. 2, the first clutch (clutch) CL <b> 1 is a clutch interposed between the engine output shaft 1 and the transmission input shaft 4, and the motor generator MG is engaged and slip-engaged (half-clutch). Between the engine Eng and the engine Eng, and the drive force transmission between the two is cut off in the open state.

  The transmission T / M is a stepped transmission that automatically switches, for example, stepped gears such as forward 7 speed / reverse 1 speed according to vehicle speed, accelerator opening, etc., and is connected to the transmission input shaft 4. The connectable transmission output shaft OUT is connected to the drive wheel side (not shown).

  The second clutch CL2 is interposed between the motor generator MG and a driving wheel (not shown), and can transmit a driving force between the motor generator MG and the driving wheel (not shown) in the engaged state. This is a clutch that cuts off the transmission of the driving force. In the first embodiment, a clutch or a brake provided as an engaging element of the transmission T / M is used as the second clutch CL2.

  The hybrid vehicle to which the first embodiment is applied includes an electric vehicle travel mode (hereinafter referred to as “EV mode”), a hybrid vehicle travel mode (hereinafter referred to as “HEV mode”), and a semi-electric vehicle travel mode (hereinafter referred to as “EV mode”). And a travel mode such as a drive torque control start mode (hereinafter referred to as “WSC mode”).

  The “EV mode” is a mode in which the first clutch CL1 is disengaged and the vehicle travels only with the power of the motor generator MG.

  The “HEV mode” is a mode in which the first clutch CL1 and the second clutch CL2 are engaged, and the vehicle travels in any of the motor assist travel mode, travel power generation mode, and engine travel mode. The “quasi-EV mode” is a mode in which the first clutch CL1 is engaged, but the engine Eng is turned off and the vehicle travels only with the power of the motor generator MG. It should be noted that the first clutch CL1 is in the slip state for a short time from the start of engagement to the end of engagement when the engine Eng is started by the driving force of the motor generator MG.

  “WSC mode” controls the motor generator MG at the time of P / N → D select start from “HEV mode” or D range start from “EV mode” or “HEV mode”. Then, the slip engagement state of the second clutch CL2 is maintained, and the clutch transmission torque passing through the second clutch CL2 starts while controlling the clutch torque capacity so that the required drive torque determined according to the vehicle state and the driver operation is achieved. Mode. “WSC” is an abbreviation for “Wet Start Clutch”.

Next, the first clutch CL1 will be described.
The first clutch CL1 includes a driven plate (first plate member) 11, a drive plate (second plate member) 12, and a hydraulic actuator (pressing means) 13.

  As shown in FIG. 1, the driven plate 11 is movable in the axial direction and restricted in movement in the circumferential direction by the outer plate support portion 24 provided on the inner periphery of the drum portion 23 of the rotor 2. A plurality are arranged in the axial direction.

That is, a plurality of spline grooves 24 a extending in the axial direction are formed in the outer plate support portion 24 at equal intervals over the entire circumference.
On the other hand, on the outer periphery of the driven plate 11, a plurality of spline teeth 11a shown in FIG. 3 are formed over the entire circumference at a constant pitch in the circumferential direction. As shown in FIG. 1, the spline teeth 11 a are inserted into a plurality of spline grooves 24 a extending in the axial direction along the outer plate support portion 24 on the inner periphery of the drum portion 23. Is movable in the axial direction with respect to the outer plate support 24 and is engaged in the circumferential direction.

  Further, in the first embodiment, as shown in FIG. 3, a pair of wear powder discharge guide grooves 11 b are formed on both side surfaces of the driven plate 11 at an angle of 180 ° in the circumferential direction, and the other side surface. The pair is arranged at an angle of 90 ° and is formed over the entire length of the driven plate 11 in the radial direction. Further, the above-described spline teeth 11a are cut away from the wear powder discharge guide grooves 11b arranged in the outer diameter direction to be provided with non-installation portions 11c.

  Returning to FIG. 1, in the spline groove 24 a of the outer plate support portion 24, a guide taper surface 24 b is formed on the groove bottom surface portion so as to be inclined toward the front end portion in the right direction in the drawing of the drum portion 23. Has been. The guide taper surface 24b is formed in at least the spline grooves 24a corresponding to the positions where the spline teeth 11a of the driven plate 11 are not installed. In the first embodiment, the guide taper surfaces 24b are formed in all the spline grooves 24a. Has been.

  The drive plate 12 is interposed between the driven plates 11 in the axial direction, and is provided with an inner plate support portion 15 provided on the outer periphery of a clutch hub (second rotating body) 14 formed integrally with the tip portion of the engine output shaft 1. Further, it is supported so as to be movable in the axial direction.

The inner plate support portion 15 is disposed opposite to the outer plate support portion 24 and spaced apart in the inner diameter direction of the outer plate support portion 24.
The inner plate support portion 15 is also formed with spline grooves 15a. As shown in FIG. 4, a plurality of spline teeth 12a projecting from the inner periphery of the drive plate 12 are inserted into the spline grooves 15a, respectively. Thus, the drive plate 12 is movable in the axial direction with respect to the inner plate support portion 15 and is engaged in the circumferential direction.

  Further, wear powder discharge guide grooves 12b are formed on both side surfaces of the drive plate 12 in the radial direction to the outer peripheral end.

The hydraulic actuator 13 includes a piston 131, a cylinder 132, and a seal member 133.
The piston 131 is supported by the cylinder 132 so as to be slidable in the axial direction, and is disposed at the tip so as to overlap the plates 11 and 12 in the axial direction. , 12 is pressed and fastened, and a pressing member 131a is provided. The piston 131 is urged by a return spring 134 in the direction of the transmission T / M, which is the left direction in the drawing.

  The cylinder 132 is formed at a position on the transmission T / M side in the motor housing 5 so as to face the partition disk portion 22 and supports the base end portion 131b of the piston 131 so as to be slidable in the axial direction. . Further, the cylinder 132 is provided with an oil chamber 132a in which an oil passage 51 for guiding oil pressure is communicated from a control valve (not shown) provided in the transmission T / M. Therefore, when the hydraulic pressure is introduced into the oil chamber 132a, the piston 131 slides in the right direction in the drawing to press the plates 11 and 12 in a clutch engagement state. On the other hand, when the hydraulic pressure is discharged from the oil chamber 132a, the piston 131 slides to the left in the drawing by the urging force of the return spring 134 to form a clutch release state.

  By the way, the closed space 55 surrounded by the motor housing 5 is in a position indicated by a dotted line L in FIG. 2 and a damp chamber 55a to which oil for hydraulic control of the transmission T / M is supplied and a dry chamber to which this oil is not supplied. It is divided into a chamber 55b. Therefore, as shown in FIG. 1, the seal member 133 seals the wet chamber 55a and the dry chamber 55b at a portion where the piston 131 passes through the partition disk portion 22.

  The engine output shaft 1 is attached with a substantially disc-shaped blade (negative pressure generating mechanism) 6. The blade 6 is a component of the existing flywheel FW, and is disposed in the vicinity of the motor housing 5 in the engine side chamber 7 that is partitioned from the dry chamber 55 b by the motor housing 5. A plurality of blade ribs 61 are cut and raised in the blade plate 6 at positions facing the motor housing 5. Therefore, when the blade 6 rotates integrally with the engine output shaft 1, air is blown, and a negative pressure is formed in the space 7 a between the blade 6 and the motor housing 5.

Further, the motor housing 5 is formed with a recess 52 that is recessed in the direction of the engine Eng (rightward in the drawing) at a position overlapping the axial direction of the drum portion 23. The recess 52 has a shape that forms a substantially constant interval h1 in the axial direction with the tip of the drum portion 23, and that forms an interval h2 wider than the interval h1 in the outer diameter direction of the tip of the drum portion 23. Is formed. A collecting space portion 8 is formed between the recess 52 formed in this way and the outer periphery of the drum portion 23.
Further, in the recess 52, a hole 52 a that communicates the dry chamber 55 b and the engine side chamber 7 is formed in the axial direction so as to substantially overlap the outer plate support 24 of the drum portion 23 in the axial direction. .

(Operation of Example 1)
Next, the operation of the first embodiment will be described.
When the first clutch CL1 is repeatedly engaged and disengaged, the driven plate 11 and the drive plate 12 rub against each other to generate wear powder. When the first clutch CL1 is engaged, the wear powder moves in the circumferential direction and is collected in the wear powder discharge guide grooves 11b and 12b when the plates 11 and 12 rub against each other.

  The wear powder collected in the wear powder discharge guide grooves 11b and 12b is indicated by an arrow K1 in FIG. 1 along the wear powder discharge guide grooves 11b and 12b by centrifugal force when both plates 11 and 12 rotate. Next, it moves in the outer diameter direction.

The wear powder thus moved in the outer diameter direction is collected in the spline groove 24 a of the outer plate support 24 of the drum portion 23. The abrasion powder accumulated in the spline groove 24a is centrifugal force generated when the rotor 2 rotates, along the guide taper surface 24b, along the outer plate support portion 24, as indicated by the arrow K2, in the drum portion 23. Move in the tip direction (right direction in the figure).
In addition, when the vane plate 6 rotates, a negative pressure is formed in the space 7 a, thereby forming a pressure difference between the dry chamber 55 b and the engine side chamber 7, whereby the outer plate support 24 has a pore 52 a. As a result, an air flow toward the surface is generated, and the wear powder accumulated in the spline groove 24a also moves in the direction of the arrow K2 by this air flow.

The abrasion powder that has reached the tip of the drum portion 23 along the outer plate support portion 24 in this way moves in the outer diameter direction as indicated by an arrow K3 by the centrifugal force accompanying the rotation of the rotor 2, and the drum portion 23 and Along the shape of the recess 52, it is stored in the collection space 8.
In the collection space 8, the cross-sectional area (the cross-sectional area of the space h <b> 2) is wider than the area (the area of the space h <b> 1) between the tip of the drum portion 23 that is the inlet and the recess 52. Therefore, the backflow of the accumulated wear powder is suppressed as compared with the case where the relationship of the areas is reversed.

As described above, the first embodiment has the following effects.
a) Wear powder generated by rubbing the plates 11 and 12 is guided to the wear powder discharge guide grooves 11b and 12b and the guide taper surface 24b of the outer plate support 24, and is collected outside the outer plate support 24. It was guided to part 8.
As a result, the abrasion powder can be discharged and collected outside the plates 11 and 12 without opening the dry chamber 55b in the motor housing 5 to the atmosphere. Therefore, even if the air cannot be released, wear clogging can be prevented, and the malfunction of the first clutch CL1 and the acceleration of wear of the spline coupling portion can be suppressed.

b) A negative pressure was generated in the engine side chamber 7 by the rotation of the blade plate 6, and an air flow was generated in the direction from the outer plate support 24 to the collection space 8.
Therefore, the wear powder guided to the outer plate support 24 is guided toward the collection space 8 by this air flow, and the wear powder can be discharged and collected more efficiently.

c) The area (interval h1) of the inlet of the collection space 8 was formed smaller than the cross-sectional area (interval h2) of the collection space 8.
For this reason, it can suppress that the abrasion powder collected in the collection space part 8 flows out again.

  d) The driven plate 11 was provided with a non-installed portion 11c by cutting spline teeth at a position overlapping the wear powder discharge guide groove 11b in the outer diameter direction. Therefore, as compared with the case where the non-installed portion 11c is not provided, the wear powder moved in the outer diameter direction along the wear powder discharge guide groove 11b is easily guided to the spline groove 24a and is also guided to the spline groove 24a. When the worn powder moves in the direction of the arrow K2, this movement is less likely to be restricted by the spline teeth 11a, and the discharge of the worn powder becomes smoother.

  As mentioned above, although the dust discharge structure of the clutch of this invention was demonstrated based on Example 1, it is not restricted to these Examples about a concrete structure, It concerns on each claim of a claim Design changes and additions are allowed without departing from the scope of the invention.

  For example, in the first embodiment, the clutch is applied to the first clutch CL1 that controls the drive transmission state between the motor generator MG and the engine Eng in the hybrid vehicle. However, the application range is not limited to the hybrid vehicle. It can also be applied to industrial equipment other than vehicles. Accordingly, the rotor 2 coupled to the transmission input shaft 4 is shown as the first rotating body, and the clutch hub 14 coupled to the engine output shaft 1 is shown as the second rotating body, but the two rotating members are fastened and released. If it does, it can be applied to other rotating bodies.

  In the first embodiment, the driven plate 11 as the first plate member is formed with the wear powder discharge guide grooves 11b at four locations. However, the number and installation locations are not limited to this. In short, what is necessary is just to be able to guide the wear powder (dust) in the outer diameter direction.

  In the first embodiment, an example in which the collecting space portion is provided in the outer diameter direction of the tip of the drum portion 23 is shown. However, if the collecting space portion is outside the outer plate support portion, the installation position is set. The position is not limited to the position shown in Example 1. You may provide in the position of the axial direction of a 1st rotary body (rotor 2), for example, the recessed part 52 of the motor housing 5. FIG.

  In the first embodiment, a mechanism for generating a negative pressure in the space 7a by the rotation of the blade 6 is used as the negative pressure mechanism. For example, an external negative pressure such as an engine suction negative pressure or a negative pressure by a pump is used. You may use the mechanism which forms negative pressure using.

2 Rotor (first rotating body)
4 Transmission input shaft 5 Motor housing 6 Blade (negative pressure mechanism)
8 Collection space 11 Driven plate (first plate member)
11a Spline teeth 11b Wear powder discharge guide groove 11c Non-installation part 12 Drive plate (second plate member)
12a Spline teeth 12b Abrasion powder discharge guide groove 13 Hydraulic actuator (pressing means)
14 Clutch hub (second rotating body)
15 Inner plate support portion 24 Outer plate support portion 24a Spline groove 24b Guide taper surface 55 Closed space 55b Dry chamber (space portion)
CL1 1st clutch (clutch)
Eng engine h1 interval h2 interval MG Motor generator

Claims (3)

A first rotating body and a second rotating body that are coaxially rotatable;
An outer plate support provided on the first rotating body and formed to face the inner diameter direction;
An inner plate support portion provided on the second rotating body opposite the outer plate support portion at an inner diameter direction position of the outer plate support portion;
A plurality of first plate members that are movable in the axial direction by being engaged with spline teeth formed in the spline grooves formed in the outer plate support portion, and supported by being restricted in movement in the circumferential direction;
The first plate member is interposed between the first plate members, and the spline teeth are engaged with the spline grooves formed in the inner plate support portion so that the spline teeth can be moved in the axial direction, and the movement is restricted and supported in the circumferential direction. A plurality of second plate members,
Pressing means for pressing both plate members in the axial direction to form a fastening state in which both plate members are pressed in the axial direction;
A clutch having
At least one of the two plate members is formed with a wear powder discharge guide groove in the outer diameter direction for guiding the wear powder generated by the friction of both plate members in the outer diameter direction.
A guide taper surface that is gradually displaced in the outer diameter direction along the axial direction is formed on the outer plate support portion,
A dust discharge structure for a clutch, wherein a collection space for collecting the wear powder is provided in a space continuous to the tip of the guide taper surface.   The clutch dust discharge structure according to claim 1, further comprising a negative pressure mechanism that generates an air flow in a direction toward the collection space in the outer plate support portion.   The clutch dust discharge structure according to claim 1 or 2, wherein an area of an inlet of the collection space is formed to have a size equal to or smaller than a cross-sectional area of the collection space.

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