JP2017166594A - Friction engagement device - Google Patents

Abstract

A friction engagement device capable of engaging with a friction engagement member without generating frictional resistance is provided. A friction engagement device (1) is arranged between a piston (17), an outer plate (15) and an inner plate (16), and is movable in an axial direction, a first magnet (22), an outer plate (15) and an inner plate (15). An end plate 15a is provided so as to be opposed to the first magnet 22 in the axial direction between the plate 16 and movable in the axial direction. The first magnet 22 and the end plate 15a are arranged so that the same magnetic poles face each other. [Selection] Figure 3

Description

  The present invention relates to a friction engagement device that transmits rotation of an input member to an output member by friction engagement.

  Conventionally, like a multi-plate clutch used in a transmission, an input member, a first plate that rotates integrally with the input member, a second plate that frictionally engages with the first plate, and a second plate are integrated. There is known a friction engagement device that includes an output member that rotates in a rotating manner and that frictionally engages a first plate and a second plate to transmit the rotation of the input member to the output member (for example, Patent Documents). 1).

Japanese Utility Model Publication No. 06-001888

  By the way, in the conventional friction engagement device as described in Patent Document 1, the frictional resistance generated between the piston and the plate is reduced by arranging a thrust bearing between the piston and the plate. . However, when the differential rotation between the piston and the plate is large, the frictional resistance may not be sufficiently reduced.

  The present invention has been made in view of the above points, and an object of the present invention is to provide a friction engagement device capable of bringing a friction engagement member into an engaged state without generating frictional resistance.

  In order to achieve the above object, the friction engagement device of the present invention includes an input member (I) that is rotated by a driving force transmitted from a drive source, and a first friction that rotates integrally with the input member (I). An engagement member (15), a second friction engagement member (16) disposed so as to overlap the first friction engagement member (15) in the axial direction, and the second friction engagement member (16) An output member (O) that rotates integrally with and outputs rotation, and is movable in the axial direction, and is connected to one of the first friction engagement member (15) and the second friction engagement member (16). A piston (17) for applying a pressing force in a direction approaching the other side, a biasing member (21) for biasing the piston (17) toward one side in the axial direction, and the piston (17) are disposed inside. A housing (10), and oil is provided between the piston (17) and the housing (10). (19) is formed, and the piston (17) is a frictional engagement device (1) that is pressed to the other side in the axial direction in accordance with the hydraulic pressure supplied to the oil chamber (19). 17) is disposed on the first friction engagement member (15) and the second friction engagement member (16) side, and is movable in the axial direction, and the first magnet (22). The first friction engagement member (15) and the second friction engagement member (16) of the second friction engagement member (16) are arranged so as to face the first magnet (22) in the axial direction, and are movable in the axial direction. A magnet (15a), wherein the first magnet (22) and the second magnet (15a) are arranged so that the same magnetic poles face each other.

  Thus, in the friction engagement device of the present invention, the first magnet is disposed on the friction engagement member side of the piston, and the first magnet is opposed to the first magnet on the friction engagement member side of the first magnet. Two magnets are arranged. Furthermore, the first magnet and the second magnet are arranged so that the same magnetic poles face each other.

  Therefore, when the hydraulic pressure supplied to the oil chamber exceeds the urging force of the urging member and the piston moves to the friction engagement member side, the first magnet moves to the friction engagement member side together with the piston. And a 2nd magnet moves to the direction which presses a friction engagement member by the repulsive force with respect to a 1st magnet. At this time, the first magnet and the second magnet are not in contact with each other. Therefore, frictional resistance does not occur between the first magnet and the second magnet.

  Therefore, according to the friction engagement device of the present invention, the friction engagement member can be brought into the engaged state by transmitting the pressing force to the friction engagement member without generating the frictional resistance.

  In the friction engagement device of the present invention, it is preferable that the first friction engagement member or the second friction engagement member is formed of a magnetic material.

  Since the plate which is a friction engagement member is engaged by friction, if it continues to be used for a certain period of time, wear occurs on the surfaces in contact with each other, and the thickness in the axial direction gradually decreases.

  As such, if the axial thickness of the plate is reduced, the piston stroke required until a pressing force is applied from the piston to the plate increases. As a result, there is a problem that the responsiveness of the friction engagement device is lowered.

  In addition, the wear powder generated by the wear of the friction engagement member may be transferred to other constituent members of the friction engagement device when the treatment such as sufficient circulation of the lubricating oil inside the housing is not performed. There exists a possibility of adhering and inhibiting the operation | movement of the structural member.

  Therefore, as described above, if the friction engagement member is formed of a magnetic material, the wear powder is attached to the first magnet or the second magnet, and when wear occurs, the friction engagement member in the axial direction of the friction engagement member. The wear powder can increase the thickness of the first magnet or the second magnet while the thickness is reduced. In other words, the stroke increased due to wear can be compensated with the wear powder generated by the wear, and the decrease in responsiveness can be reduced.

  Moreover, since wear powder adheres to a 1st magnet or a 2nd magnet by this, it can prevent that wear powder adheres to another structural member. As a result, it is possible to prevent the operation of other components from being hindered by the wear powder.

Sectional drawing which shows the structure of the friction engagement apparatus which concerns on embodiment. FIGS. 2A and 2B are enlarged cross-sectional views showing a main part when the friction engagement device of FIG. 1 is not worn, FIG. 2A shows a non-engagement state, and FIG. 2B shows an engagement state. FIGS. 3A and 3B are enlarged cross-sectional views showing a main part when the friction engagement device of FIG. 1 is worn, FIG. 3A shows a disengaged state, and FIG. 3B shows an engaged state.

  Hereinafter, the friction engagement device according to the present embodiment will be described with reference to the drawings. In the present embodiment, the friction engagement device is used as a driving force transmission device for a vehicle or the like. However, the frictional engagement device according to the present invention can be mounted on other mechanisms such as a ship or the like, in addition to a driving force transmission device of another vehicle or an unmanned aircraft.

  First, with reference to FIG.1 and FIG.2, the structure of the friction engagement apparatus 1 which is what is called a wet multi-plate type clutch is demonstrated.

  As shown in FIG. 1, the friction engagement device 1 is configured as a cylindrical device. An input shaft I (input member) to which a driving force from a vehicle driving source is transmitted is inserted from one end side (right side in FIG. 1) of the opening of the friction engagement device 1. On the other hand, from the other end side (left side in FIG. 1), an output shaft O (output member) that transmits the driving force transmitted through the friction engagement device 1 to the driving wheels of the vehicle is inserted.

  The cylindrical frictional engagement device 1 includes a case 10 (housing) that forms an outer peripheral surface and an end surface, and a first portion that is disposed inside the case 10, forms a part of the inner peripheral surface, and is coupled to the input shaft I. 1 clutch hub 11 and the 2nd clutch hub 12 which is arrange | positioned coaxially with the 1st clutch hub 11 inside the case 10, comprises the other part of an internal peripheral surface, and couple | bonds with the output shaft O. .

  The case 10 is provided on the cylindrical outer peripheral side wall 10a, the other end of the outer peripheral side wall 10a, an end surface 10b provided with an opening at the center, and the opening of the end surface 10b on one side in the axial direction. It has the cylindrical inner peripheral side wall part 10c extended.

  The first clutch hub 11 includes a cylindrical first boss portion 11a that forms a part of the inner peripheral surface of the friction engagement device 1, and a radially outward side from the first boss portion 11a (the outer peripheral surface side of the case 10). And a first guide portion 11c extending from the end of the first annular portion 11b opposite to the first boss portion 11a to the other end in the axial direction. ing.

  The second clutch hub 12 is a cylindrical second boss portion 12a that forms another part of the inner peripheral surface of the friction engagement device 1, and an annular shape that extends radially outward from the second boss portion 12a. The second annular portion 12b and a second guide portion 12c extending from the end of the second annular portion 12b opposite to the second boss portion 12a to the one side in the axial direction.

  The first boss portion 11a of the first clutch hub 11 includes a cylindrical small-diameter portion 11a1 and a cylindrical large-diameter portion 11a2 that is coaxial with the small-diameter portion 11a1 and has a larger diameter than the small-diameter portion 11a1. .

  The distal end portion of the input shaft I is inserted into the cylindrical small diameter portion 11a1 from one end side. The first clutch hub 11 and the input shaft I are spline-coupled at the distal end portion of the input shaft I and a part of the inner peripheral surface of the small diameter portion 11a1.

  A second boss portion 12a of the second clutch hub 12 is inserted into the cylindrical large diameter portion 11a2 from the other end side. A first ball bearing 13 is disposed between the inner peripheral surface of the large-diameter portion 11 a 2 of the first clutch hub 11 and a portion on one end side of the outer peripheral surface of the second boss portion 12 a of the second clutch hub 12. . Therefore, the first clutch hub 11 can rotate relative to the input clutch I integrally with the second clutch hub 12 (that is, the output shaft O).

  The 2nd boss part 12a of the 2nd clutch hub 12 is constituted cylindrical, and the tip part of output axis O is inserted from the other end side. The second clutch hub 12 and the output shaft O are spline-coupled at the distal end portion of the output shaft O and a part of the inner peripheral surface of the second boss portion 12a.

  A ball bearing 14 is disposed between the other end side portion of the outer peripheral surface of the second boss portion 12 a of the second clutch hub 12 and the inner peripheral surface of the inner peripheral side wall portion 10 c of the case 10. Therefore, the second clutch hub 12 can rotate integrally with the output shaft O with respect to the case 10.

  The 1st guide part 11c of the 1st clutch hub 11 is comprised by the cylinder shape. A plurality of first groove portions 11c1 extending in the axial direction are formed on the inner peripheral surface side of the first guide portion 11c. A plurality of annular outer plates 15 (first friction engagement members) are arranged on the inner peripheral surface side of the first guide portion 11c. The outermost plate on the other end side of the outer plate 15 is an end plate 15a.

  A plurality of claw portions are formed on the outer peripheral side of the outer plate 15 so as to correspond to the first groove portion 11c1. Therefore, each outer plate 15 is movable in the axial direction on the inner peripheral surface side of the first guide portion 11c. On the other hand, the outer plate 15 rotates integrally with the first guide portion 11c (that is, the first clutch hub 11 and the input shaft I) in the circumferential direction.

  The second guide portion 12c of the second clutch hub 12 is configured in a cylindrical shape, and the first guide portion 11c of the first clutch hub 11 and the outer plate 15 disposed on the inner peripheral side of the first guide portion 11c. It is arrange | positioned rather than the inner peripheral side. A plurality of second groove portions 12c1 extending in the axial direction are formed on the outer peripheral surface side of the second guide portion 12c. A plurality of annular inner plates 16 (second friction engagement members) are arranged on the outer peripheral surface side of the second guide portion 12c.

  A plurality of claw portions are formed on the inner peripheral side of the inner plate 16 so as to correspond to the second groove portion 12c1. Therefore, each inner plate 16 is movable in the axial direction on the outer peripheral surface side of the second guide portion 12c. On the other hand, the inner plate 16 rotates integrally with the second guide portion 12c (that is, the second clutch hub 12 and the output shaft O) in the circumferential direction.

  The plurality of outer plates 15 and the plurality of inner plates 16 are arranged so as to alternately overlap in the axial direction. When the outer plate 15 and the inner plate 16 are pressed toward one side in the axial direction by the piston 17, they are frictionally engaged with each other. In the frictionally engaged state, the outer plate 15 and the inner plate 16 rotate integrally, so that the rotation of the input shaft I causes the first clutch hub 11, the outer plate 15, the inner plate 16, and the second clutch hub. 12 to the output shaft O.

  In the friction engagement device 1, the outermost plate 15 (end plate 15 a) on the other end side is disposed closer to the piston 17 than the inner plate 16 on the other end side. However, the innermost plate 16 on the other end side may be disposed closer to the piston 17 side than the outermost plate 15 on the other end side. In that case, the inner plate 16 on the other end side may be configured as an end plate.

  The outer plate 15 and the inner plate 16 are made of a magnetic material such as iron. Therefore, the wear powder generated by frictional engagement between the outer plate 15 and the inner plate 16 is a magnetic material powder.

  Further, the friction engagement device 1 includes an annular piston 17 disposed on the other end side of the outer plate 15 and the inner plate 16 inside the case 10.

  The outer peripheral surface of the piston 17 is slidable with the inner peripheral surface of the outer peripheral side wall portion 10 a of the case 10. On the other hand, the inner peripheral surface of the piston 17 is slidable with the outer peripheral surface of the inner peripheral side wall portion 10 c of the case 10. The grooves 17a provided on the outer peripheral surface and inner peripheral surface of the piston 17 are liquid-tightly sealed between the piston 17 and the outer peripheral side wall portion 10a or between the piston 17 and the inner peripheral side wall portion 10c. The ring 18 is arranged; Thereby, an oil chamber 19 is formed between the piston 17 and the case 10.

  The oil chamber 19 is supplied with hydraulic oil through an oil passage from a hydraulic control circuit HC configured with an oil pump, a plurality of valves, and the like. The hydraulic pressure of the hydraulic oil supplied from the hydraulic control circuit HC is detected by a hydraulic pressure sensor HS. The piston 17 moves to one end side in the axial direction in accordance with the increase in the volume of the oil chamber 19.

  A protrusion 17 b is provided on the surface on one end side of the piston 17. The protrusion 17b comes into contact with a protrusion receiving part 20a extending from the annular spring receiving part 20 provided on the inner peripheral side wall part 10c of the case 10 to the other side in the axial direction. Thereby, the rotation of the piston 17 around the axis is suppressed.

  A return spring 21 (biasing member) is disposed between the surface on the other end side on the radially inner side of the protrusion receiving portion 20 a of the spring receiving portion 20 and the surface on the one end side of the piston 17. The piston 17 is urged by a return spring 21 in a direction in which the volume of the oil chamber 19 is reduced (that is, the other end in the axial direction).

  Therefore, the piston 17 moves in the axial direction according to the hydraulic pressure supplied to the oil chamber 19 and the urging force of the return spring 21.

  In the friction engagement device 1, a coil spring is used as a biasing member that biases the piston 17. However, the urging member is not limited to the coil spring. For example, rubber or the like may be used in addition to a disc spring or wave spring.

  A first magnet 22 is attached at a position facing the end plate 15 a on the one end side of the piston 17. The first magnet 22 is fixed to the piston 17 and is movable in the axial direction integrally with the piston 17. The first magnet 22 may be disposed so as to be movable in the axial direction between the piston 17 and the outer plate 15 and the inner plate 16. Therefore, the first magnet 22 may be provided separately from the piston 17.

  The surface of the other end side of the first magnet 22 is entirely covered by the piston 17. This is to prevent wear powder generated by friction between the outer plate 15 and the inner plate 16 from adhering between the first magnet 22 and the piston 17.

  Of the plurality of outer plates 15, the end plate 15 a (second magnet) located on the other end side is formed of a magnet. This is because the position of the second magnet is fixed at a position overlapping the first magnet 22 and the outer plate 15 and the inner plate 16 in the axial direction.

  The second magnet is not necessarily configured integrally with the end plate 15a, and moves in the axial direction between the first magnet 22, the outer plate 15, and the inner plate 16 at a position facing the first magnet 22. What is necessary is just to arrange | position freely. Therefore, you may comprise the end plate 15a and a 2nd magnet as a different body.

  The first magnet 22 and the end plate 15a face each other in the axial direction. The first magnet 22 and the end plate 15a are arranged so that the same magnetic poles (N poles in the friction engagement device 1) face each other. Therefore, when the first magnet 22 moves together with the piston 17 toward the one end in the axial direction, the end plate 15a is also pushed by the repulsive force against the first magnet 22 and moves toward the one end in the axial direction. A pressing force is transmitted to the plate 16.

  Next, the frictional engagement between the outer plate 15 and the inner plate 16 will be described with reference to FIGS.

  As shown in FIG. 2A, a state in which sufficient hydraulic oil is not supplied from the hydraulic control circuit HC to the oil chamber 19 (that is, the hydraulic pressure supplied to the oil chamber 19 is sufficiently smaller than the urging force of the return spring 21. In the state), the piston 17 returns to a position where the urging force of the return spring 21 and the hydraulic pressure supplied to the oil chamber 19 are balanced.

  As a result, no pressing force is applied to the outer plate 15 and the inner plate 16, so that the outer plate 15 and the inner plate 16 are separated from each other (non-engaged state). As a result, the rotation of the input shaft I is not transmitted to the inner plate 16, the second clutch hub 12, and the output shaft O via the first clutch hub 11 and the outer plate 15.

  On the other hand, as shown in FIG. 2B, a state in which sufficient hydraulic oil is supplied from the hydraulic control circuit HC to the oil chamber 19 (that is, the hydraulic pressure supplied to the oil chamber 19 is sufficiently larger than the urging force of the return spring 21. 2), the piston 17 moves to one end side against the urging force of the return spring 21.

  As a result, the first magnet 22 moves to the end plate 15 a side together with the piston 17. And the end plate 15a which is a 2nd magnet moves to the direction which presses the other outer plate 15 and the inner plate 16 with the repulsive force with respect to the 1st magnet 22. FIG. At this time, the first magnet 22 and the end plate 15a are not in contact with each other.

  Therefore, no frictional resistance is generated between the first magnet 22 and the end plate 15a. Further, in the conventional friction engagement device, the thrust bearing arranged to reduce the frictional resistance between the piston 17 and the end plate 15a can be omitted.

  As a result, a pressing force is applied to the outer plate 15 and the inner plate 16, so that the outer plate 15 and the inner plate 16 are frictionally engaged with each other (engaged state). As a result, the rotation of the input shaft I is transmitted to the inner plate 16, the second clutch hub 12 and the output shaft O via the first clutch hub 11 and the outer plate 15.

  Therefore, according to the friction engagement device 1, the outer plate 15 and the inner plate can be generated without generating frictional resistance between the first magnet 22 that transmits the pressing force to the outer plate 15 and the inner plate 16 and the end plate 15 a. 16 can be brought into an engaged state.

  By the way, since the outer plate 15 and the inner plate 16 are engaged with each other by friction, if they are used for a certain period of time, wear occurs on the surfaces that are in contact with each other, and the thickness in the axial direction becomes slightly smaller. To go.

  If the axial thickness of the outer plate 15 or the inner plate 16 becomes thin in this way, the stroke of the piston 17 required until the pressing force is applied from the piston 17 to the outer plate 15 and the inner plate 16 is increased. It will increase. As a result, the conventional friction engagement device has a problem in that the responsiveness is lowered.

  In the friction engagement device 1, although the lubricating oil is circulated inside the case 10, when the amount of the lubricating oil is not enough, the wear powder is a component of the friction engagement device 1 (for example, a ball) There is a risk that it will adhere to the bearing 14 etc.) and hinder its operation. The wear powder is generated not only when the outer plate 15 and the inner plate 16 which are friction engagement members are worn, but also when other components are operated.

  Therefore, in the friction engagement device 1, the outer plate 15 and the inner plate 16 and the constituent members that are worn by operation are formed of a magnetic material. That is, the generated wear powder is a magnetic material. Thereby, as shown in FIG. 3, the abrasion powder is adhered to the opposing surfaces of the first magnet 22 and the end plate 15a.

  Thus, when the outer plate 15 or the inner plate 16 is worn, the thickness of the outer plate 15 or the inner plate 16 in the axial direction is reduced, while the wear powder is applied to the first magnet 22 or the end plate 15a. Adhering to increase the thickness of the first magnet 22 or the end plate 15a. That is, the stroke increased due to wear is compensated by the wear powder generated by the wear, and the decrease in responsiveness is reduced.

  The first magnet 22 is attached to the piston 17 over the entire surface on the other end side. Therefore, this prevents the wear powder from adhering to the surface on the other end side of the first magnet 22. As a result, the wear powder adheres to the first magnet 22 so as to increase the thickness of the first magnet 22 efficiently.

  In addition, by actively attaching the wear powder to the first magnet 22 and the end plate 15a, it is possible to prevent the wear powder from attaching to other components. As a result, in the friction engagement device 1, it is possible to prevent the operation of other constituent members from being hindered by the wear powder.

  Although the illustrated embodiment has been described above, the present invention is not limited to such a form.

  For example, in the above-described embodiment, the outer plate 15 and the inner plate 16 that are friction engagement members are formed of a magnetic material such as iron. This is because the wear powder is attached to the first magnet 22 and the end plate 15a (second magnet), thereby reducing the stroke of the piston 17 required until the pressing force is applied from the piston 17 to the end plate 15a. This is to prevent the wear powder from adhering to the other components of the friction engagement device 1.

  However, the friction engagement device of the present invention is not limited to such a configuration, and the friction engagement member may be formed of a material other than the magnetic material.

DESCRIPTION OF SYMBOLS 1 ... Friction engagement apparatus, 10 ... Case (housing | casing), 10a ... Outer peripheral side wall part, 10b ... End surface part, 10c ... Inner peripheral side wall part, 11 ... 1st clutch hub, 11a ... 1st boss | hub part, 11a1 ... Small diameter 11a2 ... large diameter part, 11b ... first annular part, 11c ... first guide part, 11c1 ... first groove part, 12 ... second clutch hub, 12a ... second boss part, 12b ... second annular part, 12c ... 2nd guide part, 12c1 ... 2nd groove part, 13 ... 1st ball bearing, 14 ... 2nd ball bearing, 15 ... Outer plate (1st friction engagement member), 15a ... End plate (2nd magnet), 16 ... inner plate (second friction engagement member), 17 ... piston, 17a ... groove, 17b ... projection, 17c ... bearing support, 18 ... O-ring, 19 ... oil chamber, 20 ... spring receiving part, 20a ... projection Receiving part, 1 ... return spring (biasing member), 22 ... first magnet, HC ... hydraulic control circuit, HS ... oil pressure sensor, I ... input shaft (input member), O ... output shaft (output member).

Claims (2)

An input member that is rotated by a driving force transmitted from a driving source;
A first friction engagement member that rotates integrally with the input member;
A second frictional engagement member arranged to overlap the first frictional engagement member in the axial direction;
An output member that rotates integrally with the second friction engagement member and outputs rotation;
A piston that is movable in an axial direction and applies a pressing force in a direction approaching the other to one of the first friction engagement member and the second friction engagement member;
An urging member for urging the piston in one axial direction;
A housing in which the piston is disposed;
An oil chamber is formed between the piston and the housing,
The piston is a friction engagement device that is pressed to the other side in the axial direction according to the hydraulic pressure supplied to the oil chamber,
A first magnet which is disposed on the first friction engagement member and the second friction engagement member side of the piston and is movable in the axial direction;
A second magnet that is arranged to face the first magnet on the first friction engagement member and the second friction engagement member side of the first magnet in the axial direction and is movable in the axial direction;
The friction engagement device, wherein the first magnet and the second magnet are arranged so that the same magnetic poles face each other. The friction engagement device according to claim 1,
The friction engagement device, wherein the first friction engagement member or the second friction engagement member is made of a magnetic material.