WO2005061917A1 - 多板クラッチ装置及びクラッチディスク組立体 - Google Patents
多板クラッチ装置及びクラッチディスク組立体 Download PDFInfo
- Publication number
- WO2005061917A1 WO2005061917A1 PCT/JP2004/017466 JP2004017466W WO2005061917A1 WO 2005061917 A1 WO2005061917 A1 WO 2005061917A1 JP 2004017466 W JP2004017466 W JP 2004017466W WO 2005061917 A1 WO2005061917 A1 WO 2005061917A1
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- WO
- WIPO (PCT)
- Prior art keywords
- plate
- clutch
- friction
- friction plate
- fixing
- Prior art date
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- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 claims abstract description 65
- 229910052799 carbon Inorganic materials 0.000 claims abstract description 65
- 239000002131 composite material Substances 0.000 claims abstract description 59
- 230000002093 peripheral effect Effects 0.000 claims abstract description 55
- 230000007246 mechanism Effects 0.000 claims abstract description 48
- 230000005540 biological transmission Effects 0.000 claims description 32
- 239000000463 material Substances 0.000 claims description 27
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 claims description 18
- 230000008878 coupling Effects 0.000 claims description 18
- 238000010168 coupling process Methods 0.000 claims description 18
- 238000005859 coupling reaction Methods 0.000 claims description 18
- 229910052742 iron Inorganic materials 0.000 claims description 9
- 238000003825 pressing Methods 0.000 claims description 8
- 230000000149 penetrating effect Effects 0.000 claims description 6
- 238000006243 chemical reaction Methods 0.000 claims description 4
- 230000004323 axial length Effects 0.000 claims description 3
- 238000005520 cutting process Methods 0.000 claims description 2
- PEDCQBHIVMGVHV-UHFFFAOYSA-N Glycerine Chemical compound OCC(O)CO PEDCQBHIVMGVHV-UHFFFAOYSA-N 0.000 claims 1
- 238000000034 method Methods 0.000 claims 1
- 239000002783 friction material Substances 0.000 description 15
- 238000010586 diagram Methods 0.000 description 11
- 230000000694 effects Effects 0.000 description 7
- 230000035939 shock Effects 0.000 description 7
- 229910000831 Steel Inorganic materials 0.000 description 6
- 230000001276 controlling effect Effects 0.000 description 6
- 239000010959 steel Substances 0.000 description 6
- 230000002159 abnormal effect Effects 0.000 description 4
- CREMABGTGYGIQB-UHFFFAOYSA-N carbon carbon Chemical compound C.C CREMABGTGYGIQB-UHFFFAOYSA-N 0.000 description 4
- 239000011203 carbon fibre reinforced carbon Substances 0.000 description 4
- 230000004048 modification Effects 0.000 description 4
- 238000012986 modification Methods 0.000 description 4
- 230000001105 regulatory effect Effects 0.000 description 4
- 238000010521 absorption reaction Methods 0.000 description 3
- 230000007423 decrease Effects 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000004904 shortening Methods 0.000 description 2
- 238000005728 strengthening Methods 0.000 description 2
- 229920000049 Carbon (fiber) Polymers 0.000 description 1
- 241000255925 Diptera Species 0.000 description 1
- 230000004308 accommodation Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 239000004917 carbon fiber Substances 0.000 description 1
- 239000003575 carbonaceous material Substances 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000009365 direct transmission Effects 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 239000000835 fiber Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/22—Friction clutches with axially-movable clutching members
- F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
- F16D13/385—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs double clutches, i.e. comprising two friction disc mounted on one driven shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/60—Clutching elements
- F16D13/64—Clutch-plates; Clutch-lamellae
- F16D13/644—Hub construction
- F16D13/646—Mounting of the discs on the hub
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/60—Clutching elements
- F16D13/64—Clutch-plates; Clutch-lamellae
- F16D13/68—Attachments of plates or lamellae to their supports
Definitions
- the present invention relates to a multi-plate clutch device and a clutch disk assembly, and more particularly to a multi-plate clutch device and a clutch disk assembly reinforced for high load.
- a multi-plate clutch device used for a racing car or the like is designed with emphasis on use under high load and durability.
- This type of multi-plate clutch device has a clutch disk assembly arranged in proximity to a flywheel on the engine side, and a pressure plate fixed to the flywheel for pressing the clutch disk assembly against the flywheel.
- a clutch cover assembly is provided.
- the clutch disc assembly has an annular friction coupling portion on the outer peripheral side, and the friction coupling portion includes a plurality of first friction plates and a second friction plate disposed between the plurality of first friction plates. And When the first and second friction plates are clamped between the flywheel and the pressure plate, torque is transmitted directly to the transmission input shaft via the clutch disc assembly (see, for example, Patent Document 1).
- the torque transmission capacity of the clutch device is determined by the biasing force on the pressure plate, the diameter of the friction plate (effective radius of the clutch), the material of the friction plate (friction coefficient), and the number of friction surfaces. For example, by increasing the urging force or the coefficient of friction or increasing the number of friction surfaces, the friction resistance increases and the torque transmission capacity also increases. In addition, increasing the effective radius of the clutch increases the torque transmission capacity.
- the friction coefficient can be increased by changing the material of the friction plate, and effects such as improvement in operability and durability can be expected by using a material in consideration of light weight and heat resistance. Conventional force Friction plates of various materials have been developed.
- carbon As a material of the friction plate of the multi-plate clutch device such as a racing car, for example, carbon there is known a composite material (carbon composite material) containing as a main component.
- a friction plate made of a carbon composite material is generally called a carbon friction plate.
- One of the characteristics of carbon composite materials is that they have a higher friction coefficient than conventional friction materials (for example, friction materials containing metal fibers). Therefore, when a carbon composite material with a high coefficient of friction is used, the frictional resistance generated on the friction surface increases, and the torque transmission capacity also increases as compared with conventional friction materials.
- the carbon composite material is lighter in weight than the conventional friction material, and the inertial force generated by rotational movement is smaller. Performance is improved.
- carbon composite materials have higher heat resistance and less deformation than conventional friction materials, and therefore have improved durability. In this way, by adopting carbon composite material as the friction material, the multi-plate clutch device for racing can be used under a high load and durability can be improved.
- Patent Document 1 Japanese Patent Application Laid-Open No. 2003-90355
- the clutch disc assembly has a first tubular portion fixed to the flywheel, and a second tubular portion disposed on the inner peripheral side of the first tubular portion, and is connected to the shaft. It is composed of a hub flange, and a drive plate and a driven plate as friction plates that respectively engage with the first tubular portion and the second tubular portion.
- a friction plate and an output-side member are connected by meshing gears, and the friction plate is movable in the axial direction (for example, see Patent Document 1).
- the friction plate and the output side member are connected by the meshing of the gears.
- a rattling noise also occurs.
- the clutch disk assembly having such a structure requires a mechanism for regulating the movement of the friction plate in the axial direction, and the structure around the mounting portion of the friction plate becomes complicated.
- the multi-plate clutch device for racing has drawbacks in operability and quietness (vibration absorption).
- these drawbacks are not a problem for a multi-plate clutch for racing. This is because the race driver who operates the multi-plate clutch device for racing has a higher level of operation skills than the general driver, and it is not necessary to reduce noise such as rattling noise at the race track.
- the complication of the structure is not particularly a problem if a high load is used for racing.
- a clutch device with a high load specification has a large torque transmission capacity and can be used with a high-power engine, and can exhibit higher performance than conventional passenger car clutch devices in various situations.
- the clutch device of high load specification has high durability, the replacement cycle of parts becomes longer, and the maintenance cost can be reduced. Further, if the complicated structure is simplified, the cost of the clutch device can be reduced, and it can be easily adopted not only for racing but also for passenger cars.
- a multi-plate clutch device reinforced for high loads has a great advantage to be mounted on passenger cars, and therefore it is necessary to improve operability, quietness, and vibration absorption for passenger cars. I have. It is also required to simplify the structure around the mounting portion of the friction plate.
- An object of the present invention is to improve the operability and quietness of a multi-plate clutch device reinforced for high loads.
- the multi-plate clutch device is for transmitting and shutting off the power of the input rotating body force on the engine side to the output rotating body, and is connected to the output rotating body and arranged close to the input rotating body.
- a clutch cover assembly connected to the input rotary body and having a pressure plate for pressing the clutch disk assembly against the input rotary body.
- the clutch disc assembly is connected to the output rotating body A hub, a friction connecting portion disposed on the outer peripheral side of the hub and held between the input rotating body and the pressure plate, and a damper mechanism for positively connecting the hub and the friction connecting portion in the rotational direction. ing.
- the friction connecting portion includes a ring member connected to the outer peripheral side of the damper mechanism, and a plurality of friction connecting portions disposed on the outer peripheral side of the ring member and engaged with the ring member so as to be relatively non-rotatable and relatively movable in the axial direction.
- a first friction plate, and a second friction plate disposed between the plurality of friction plates and engaged with the clutch cover assembly so as to be relatively non-rotatable and relatively movable in the axial direction.
- at least one of the first friction plates is made of a carbon composite material.
- the first friction plate has a high coefficient of friction and absorbs noise such as impact and rattling noise when the clutch is connected, even if carbon composite material is used. can do. Therefore, in this multi-plate clutch device, operability and quietness can be improved while strengthening for a high load.
- the carbon composite material is a composite material containing carbon as a main component.
- a carbon composite material is a composite material of carbon and another material. Carbon composite material).
- At least one of the input rotating body, the presser plate, and the second friction plate is formed of a carbon composite material.
- the member that frictionally engages with the first friction plate is made of a force-bonded composite material, like the first friction plate.
- the friction coefficient of carbon composite materials changes with temperature, and the range of variation tends to be larger than that of conventional friction materials. For example, the friction coefficient when sliding a carbon composite material and an iron-based steel material increases as the temperature increases, and decreases as the temperature decreases. On the other hand, the coefficient of friction between the carbon composite materials does not change much even when the temperature changes.
- this device can obtain various clutch characteristics.
- this device can obtain a higher friction coefficient than the conventional friction material, it can cope with a high load.
- the hub is provided around the entire circumference in claim 1 or 2. It has a flange portion projecting radially outward, and a plurality of housing portions formed by cutting out a part of the flange portion.
- the damper mechanism is arranged to be rotatable relative to the plurality of elastic members accommodated in the accommodating portion and to the flange portion with the flange portion sandwiched in the axial direction, and a window hole is provided at a position corresponding to the elastic member. And a pair of connection plates provided.
- the damper mechanism since the damper mechanism has the above-described structure, various torsional rigidity damper mechanisms can be obtained by changing the rigidity, quantity, and arrangement of the elastic members. Therefore, even when a carbon composite material is used as the friction material, shock and noise can be absorbed, and operability and quietness can be more reliably improved.
- a multi-plate clutch device is the multi-plate clutch device according to any one of the first to third aspects, wherein the ring member has a plurality of external teeth protruding outward in the radial direction and formed over the entire outer circumference.
- the first friction plate has a plurality of internal teeth formed over the entire inner circumference and engaged with the external teeth.
- the first friction plate can be engaged with the ring member such that the first friction plate cannot rotate relatively and can move relatively in the axial direction. Therefore, when a plurality of first friction plates are pressed against the input rotating body, the movement of the first friction plate in the axial direction is facilitated, so that the contact state of the friction surface is improved, and the friction between the input rotating body and the first friction plate is improved. Power can be reliably transmitted to the output rotating body. Further, when the pressing is released, the first friction plate can easily separate the mating friction material, so that the torque can be cut off quickly.
- the multi-plate clutch device is the multi-plate clutch device according to the fourth aspect, further comprising a protrusion disposed between the ring member forces and the plurality of first friction plates, and further projecting radially outward from the external teeth. ing.
- the damper mechanism may fall off in the axial direction. Therefore, by having the protruding portions on the external teeth, the relative movement of the ring member in the axial direction with respect to the first friction plate can be restricted, and the damper mechanism can be prevented from falling off.
- the clutch cover assembly according to any one of claims 1 to 5, wherein a plurality of annular clutch covers are arranged in the rotational direction to connect the input rotary body and the clutch cover. And a cover member.
- the second friction plate has a plurality of notches for engaging with the cover member.
- the second friction plate since the second friction plate has the cutout portion that engages with the cover member, the second friction plate is not rotatable relative to the clutch cover assembly and relatively movable in the axial direction. Can be combined. Therefore, when the plurality of first friction plates are pressed against the input rotating body, the second friction plate is easily moved in the axial direction, so that the power from the input rotating body is reliably transmitted to the output rotating body. be able to.
- the multi-plate clutch device is the fixing member according to any one of claims 3 to 6, wherein a part of the inner peripheral side of the ring member is fixed while being sandwiched between the outer peripheral sides of the pair of connecting plates. have.
- the fixing member is stepped to determine the distance between the connecting plates, the accuracy of the distance between the connecting plates is not good.
- the distance between the connecting plates can be determined by the axial length of the ring member by sandwiching a part of the inner peripheral side of the ring member between the connecting plates, so that the accuracy of the distance between the connecting plates is improved. It can easily be increased. Further, the ring member and the connection plate can be more securely fixed. Therefore, in this device, the strength of the damper mechanism is improved, so that the device can be used for high loads. Further, the hysteresis torque can be stabilized.
- the ring member has a plurality of first engagement portions projecting radially inward.
- the flange portion has a second engagement portion projecting radially outward and coming into contact with the first engagement portion when rotated by a predetermined relative angle.
- the fixing member since the fixing member is used as a stopper for the S flange portion, the fixing member may be damaged. Since this device has the first and second engagement portions, when the flange portion and the connection plate rotate by a predetermined relative angle when the damper mechanism is operated, the first and second engagement portions are provided. The joints come into contact and torque can be transmitted reliably. Therefore, compared to the conventional damper mechanism that receives torque only with the fixing member, the damper mechanism has Since the strength is improved, it can be used for high loads.
- the multi-plate clutch device according to the seventh or eighth aspect, wherein the fixing member has a cylindrical shape, a head provided at both ends of the body and having an outer diameter larger than the size of the body, It is provided between the trunk and one of the heads, has a larger outer diameter than the trunk, has a smaller outer diameter than the head, and has a stepped portion.
- the multi-plate clutch device wherein the fixing member has a cylindrical shape, a head provided at both ends of the body, and having a larger outer diameter than the body, according to claim 7 or 8,
- the tapered portion is provided between the portion and one of the heads, and has a tapered portion whose outer diameter gradually increases as the force on the same side is directed toward the head.
- the fixing member since the fixing member has a taper portion, the gap between the through-hole of the connecting plate can be reduced by increasing the accuracy of the tapered portion, and the ring member and the connecting plate can be more securely connected. Can be fixed to As a result, the damper mechanism can be used for high loads.
- the multi-plate clutch device according to claim 11 is the multi-plate clutch device according to any one of claims 1 to 10, wherein at least one of the input rotating body, the pressure plate, and the second friction plate is mainly made of an iron-based material. It is composed of
- At least one of the members that frictionally engages with the first friction plate also includes an iron-based material force, so that the carbon composite material and the iron-based steel material frictionally engage with each other.
- the friction coefficient between the carbon composite material and the iron-based steel material changes with temperature. Specifically, when a carbon composite material and an iron-based steel material are slid, the friction coefficient increases as the temperature of the friction surface increases, and the friction coefficient increases. The lower the surface temperature, the lower the coefficient of friction.
- various clutch characteristics can be obtained.
- this device can obtain a larger friction coefficient than a conventional friction material, it can cope with a high load.
- the multi-plate clutch device further comprises a release device according to any one of claims 1 to 11, wherein the release device engages the first urging member and elastically deforms the first urging member in the axial direction. I have.
- the release device releases the urging force of the first urging member against the pressure plate by moving toward the input rotator in the axial direction.
- this device when the release device moves toward the input rotary member in the axial direction, the urging force is released, that is, the clutch connection is released. As a result, this device can be applied to a so-called push-type multi-plate clutch device.
- the multi-plate clutch device further comprises a release device according to any one of claims 1 to 11, wherein the release device engages the first urging member and elastically deforms the first urging member in the axial direction. I have.
- the release device releases the urging force of the first urging member against the pressure plate by moving to the side opposite to the axial input rotating body side.
- this device the urging force is released, that is, the clutch connection is released by moving the release device to the side opposite to the input rotator in the axial direction.
- this device can be used for a so-called pull-type multi-disc clutch device.
- the multi-plate clutch device described in claim 14 is the push-pull device according to any one of claims 1 to 13, which presses the first friction plate required for power transmission between the input rotary member and the output rotary member. And a second biasing member having an elastic reaction force smaller than the pressure load.
- the multi-plate clutch device especially when used for racing, has the power to maintain, for example, a half-clutch state in order to increase the temperature of a friction member such as the first friction plate to increase the friction coefficient.
- a friction member such as the first friction plate
- this causes the temperature of not only the friction member but also the surrounding members to rise due to frictional heat. Since the peripheral member thermally expands in the axial direction due to the temperature rise, the urging force of the first urging member relatively increases. As a result, a phenomenon occurs in which the clutch torque sharply rises even though the depression amount of the clutch pedal is kept constant.
- This device has a second biasing member that has an elastic reaction force smaller than the pressing load on the first friction plate required for power transmission. Even if thermal expansion occurs in the axial direction, the second biasing member can absorb deformation due to thermal expansion. As a result, in this device, even if the half-clutch is held, the clutch torque does not suddenly rise, preventing the start of the vehicle against the driver's will and preventing abnormal wear of the first and second friction plates. be able to.
- the second urging member is disposed between the first urging member and the pressure plate.
- the second urging member is disposed between the first urging member and the pressure plate, for example, even when the pressure plate thermally expands in the axial direction due to frictional heat in a half-clutch state.
- the second urging member can absorb deformation due to thermal expansion.
- the multi-plate clutch device according to claim 16 is the multi-plate clutch device according to any one of claims 3 to 15, wherein at least one of the connection plates and the flange portion receives an axial load acting between the two members.
- An annular friction member is provided for receiving the friction member.
- This device has a friction member between the connecting plate and the flange, so that even if an axial load is applied between both members, the axial gap between the two members can be kept constant. It is possible to prevent both members from coming into contact with each other. In addition, since the friction member is provided, when the coupling plate and the flange portion rotate relative to each other, a hysteresis torque is generated between the two members, so that the torsional vibration can be more effectively absorbed.
- the multi-plate clutch device according to any one of the third to sixteenth aspects, wherein at least one of the connection plates and the flange portion has an axial urging force between the two members. It has an annular third biasing member for applying.
- the third urging member is provided between the connection plate and the flange portion, the relative positions in the axial direction of both members are stabilized. Also, in this device, the friction member is Since the flange portion can be urged in the axial direction, the relative position in the axial direction between the two members becomes more stable. In addition, since the third urging member is provided, the hysteresis torque can be reliably generated by the friction member, and the hysteresis torque can be adjusted by setting the urging force of the third urging member.
- the third biasing member is formed of a disc spring that is elastically deformable in the axial direction.
- the third urging member is formed of a disc spring, a desired urging force can be secured while shortening the axial gap size.
- the third biasing member is formed of a wave spring that is elastically deformable in the axial direction.
- the third urging member is formed of a disc spring, a desired urging force can be secured while shortening the axial gap size.
- a clutch disk assembly is for transmitting and shutting off the power of the flywheel on the engine side to the input shaft of the transmission, and comprises a carbon friction plate, a clutch disk body, and a plurality of clutch disks. And a fixture.
- the carbon friction plate is pressed against the flywheel.
- the clutch disc main body has a disk-shaped input portion connected to the outer periphery of the inner peripheral portion of the friction plate, and an output portion connected to the input shaft of the transmission.
- the plurality of fixtures directly connect the outer peripheral portion of the disk-shaped input portion and the inner peripheral portion of the friction plate.
- the carbon friction plate refers to a friction plate made of a carbon composite material.
- the carbon composite material is a composite material containing carbon as a main component, for example, a composite material of carbon and another material, or a carbon composite material. (Carbon-carbon composite material).
- the friction plate has a notch into which the fixing tool is inserted.
- the fixture has a flange, a trunk, and a fixing part.
- the flange abuts against the side surface of the friction plate to regulate the movement of the friction plate in the axial direction.
- the body is inserted into the notch of the friction plate, has a thickness corresponding to the thickness of the friction plate, and has a part of the end face abutting on the side surface of the disk-shaped input section.
- the fixing portion is formed at the opposite end of the collar portion, and is fixed to the disk-shaped input portion.
- the fixing tool since the fixing tool has the body, the coupling relationship between the friction plate and the clutch disk body can be adjusted by controlling the length of the body. That is, by making the length of the body of the fixing device equal to the thickness of the friction plate, the friction plate and the clutch disc body are completely fixed to each other and cannot be moved, and the length of the body is reduced. By making the friction plate longer than the thickness of the friction plate, the fixation of both becomes a fixation with a degree of freedom in the axial direction.
- the fixing tool is a rivet, and the fixing portion is fixed by force.
- the friction plate has a notch into which the fixture is inserted.
- the fixing device includes a first fixing device and a second fixing device.
- the first fixture has a body inserted into the notch of the friction plate.
- the second fixture is formed at the other end of the shaft, a shaft portion penetrating the first fixture in the axial direction, a flange formed at one end of the shaft portion and axially engaging with the friction plate. It has a disk-shaped input part and a fixed part engaged in the axial direction.
- the coupling relationship between the friction plate and the clutch disk body can be adjusted by controlling the length of the body.
- the length of the torso of the first fixing member equal to the thickness of the friction plate
- the friction plate and the clutch disc main body are completely fixed to each other and cannot be moved.
- the two are fixed with a degree of freedom in the axial direction.
- the relative rotation of the friction plate with respect to the disc-shaped input portion can be regulated by the shaft portion, the collar portion, and the fixing portion of the second fixture.
- the second fixing portion has the collar portion and the fixing portion, the relative movement in the axial direction between the disc-shaped input portion and the friction plate can be restricted.
- the fixing device includes a first fixing device and a second fixing device.
- the first fixture has a body inserted into the notch of the friction plate.
- the second fixing device includes: a shaft portion that penetrates the first fixing device and the disc-shaped input portion in the axial direction; a collar portion formed at one end of the shaft portion and axially engaging with one friction plate; A fixing portion formed at the other end of the shaft portion and engaging with the other friction plate in the axial direction;
- the coupling relationship between the two friction plates and the clutch disc body can be adjusted by controlling the length of the body.
- the friction plate and the clutch disc body are completely fixed to each other and cannot be moved.
- the fixation of both becomes fixation with a degree of freedom in the axial direction.
- the shaft, the flange, and the fixing portion can regulate the relative rotation of the friction plate with respect to the disk-shaped input portion.
- the second fixing member has the shaft portion, the collar portion, and the fixing portion, the relative movement in the axial direction between the disk-shaped input portion and the two friction plates can be restricted.
- the second fixing member is a rivet, and the fixing portion is fixed by force.
- the friction plate has a notch into which the fixture is inserted.
- the fixing device includes a first fixing device and a second fixing device.
- the first fixture is inserted into the notch of the friction plate and It has a body part having a corresponding thickness and a part of the end face abutting on the side surface of the disk-shaped input part, and a fixing part fixed to the disk-shaped input part.
- the second fixture has a flange portion axially engaged with the friction plate, and a connecting portion connecting the collar portion and the first fixture.
- the coupling relationship between the friction plate and the clutch disk body can be adjusted by controlling the length of the body.
- the length of the torso of the first fixing member equal to the thickness of the friction plate
- the friction plate and the clutch disc main body are completely fixed to each other and cannot be moved.
- the two are fixed with a degree of freedom in the axial direction.
- the body of the first fixing device is inserted into the notch of the friction plate, the relative rotation of the friction plate with respect to the disk-shaped input portion can be restricted by the shaft, the flange, and the fixing portion. it can.
- the first fixture has a fixing portion and the second fixture has a collar portion and a connecting portion, the axial relative movement between the disc-shaped input portion and the friction plate can be restricted. .
- the friction plate has a notch into which the fixture is inserted.
- the fixing device includes a first fixing device and a second fixing device.
- the first fixture has a body inserted into the notch of the friction plate.
- the second fixing member includes a flange portion axially engaged with the friction plate, a connecting portion penetrating the first fixing member in the axial direction and connecting the collar portion and the first fixing member, and a brim of the connecting portion.
- a fixing portion formed at an end opposite to the portion and connecting the first fixing tool and the disc-shaped input portion.
- the coupling relationship between the friction plate and the clutch disk body can be adjusted by controlling the length of the body.
- the length of the torso of the first fixing member equal to the thickness of the friction plate
- the friction plate and the clutch disc main body are completely fixed to each other and cannot be moved.
- the two are fixed with a degree of freedom in the axial direction.
- the body of the first fixture is inserted into the notch of the friction plate
- the flange, the connecting portion, and the fixing portion can regulate the relative rotation of the friction plate with respect to the disc-shaped input portion.
- the first and second fixing members can regulate the axial relative movement between the disc-shaped input portion and the friction plate.
- the body has an axial length greater than the thickness of the friction plate.
- the fixing tool since the fixing tool has the body, the coupling relationship between the friction plate and the clutch disk body can be adjusted by controlling the length of the body.
- the length of the torso of the fixing device equal to the thickness of the friction plate, the friction plate and the clutch disc body are completely fixed to each other and immovable, and the torso length is reduced.
- the fixation of both becomes a fixation with a degree of freedom in the axial direction.
- a clutch disc assembly according to claim 29, wherein the notch of the friction plate has a pair of parallel side surfaces extending in the radial direction, and the body of the fixing device has the following features. It has a pair of flat surfaces that can contact the pair of side surfaces.
- a clutch disk assembly according to claim 30 is the clutch disk assembly according to claim 29, wherein the pair of flat surfaces formed on the body of the fixing tool and the pair of side surfaces of the notch of the friction plate are provided. There is a gap between them!
- the clutch disc assembly according to claim 31 is arranged such that the fixing tool is sandwiched between the friction plate and at least one of the collar portion and the fixing portion in any one of claims 22 to 30. And an annular member.
- the fixing device since the fixing device has the annular member, even if the outer diameter of the collar portion is smaller than the circumferential width of the notch, the friction plate in the axial direction relative to the disk-shaped input portion is not removed. Movement can be reliably restricted.
- a clutch disk assembly according to a thirty-third aspect further comprises an annular connecting member for connecting a plurality of fixing tools according to the twenty-third aspect.
- the connecting member is arranged to be sandwiched between the friction plate and the flange.
- the fixing members are connected by the connecting members, the relative positions of the plurality of fixing devices are stabilized. Further, since the connecting member is sandwiched between the friction plate and the flange portion, the relative movement of the friction plate in the axial direction with respect to the disc-shaped input portion can be reliably restricted.
- the clutch disc assembly according to claim 34 wherein the clutch disc body is connected to the input shaft of the transmission, and the flange portion radially extends from the boss. And a disc-shaped input plate as a disc-shaped input portion provided on the side of the flange portion of the hub.
- the disc-shaped plate is disposed so as to be rotatable relative to a flange portion of the hub within a predetermined angle range.
- the clutch disk body further includes a damper portion that sexually connects the disk-shaped input plate and the flange portion of the hub in the circumferential direction.
- the operability and quietness of the multiple disc clutch device reinforced for high load can be improved.
- the structure around the friction plate mounting portion can be simplified.
- FIG. 1 is a longitudinal sectional view of a multiple disc clutch device according to a first embodiment.
- FIG. 2 is a cross-sectional view of a clutch disk assembly.
- FIG. 3 is a cross-sectional view of a stop pin 45.
- FIG. 4 is a sectional view of a stop pin 55.
- FIG. 5 is a longitudinal sectional view of a multi-plate clutch device for a push type.
- FIG. 6 is a longitudinal sectional view of a clutch disk assembly according to a second embodiment.
- FIG. 7 is a partial front view of the clutch disk assembly.
- FIG. 10 is a partial front view of the clutch disk assembly.
- FIG. 11 is a diagram showing a coupling portion between a friction plate and a clutch plate.
- FIG. 12 is a perspective view of a rivet after caulking.
- FIG. 13 is a perspective view of a rivet alone before caulking.
- FIG. 14 is a structural diagram around a fixture 360 according to a fourth embodiment.
- FIG. 15 is a detailed view of a first fixture 361.
- FIG. 16 is a structural diagram around a fixture 360 as a modification of the fourth embodiment.
- FIG. 18 is a structural diagram around a fixture 460 according to the fifth embodiment.
- FIG. 19 is a detailed view of a first fixture 461.
- FIG. 20 is a structural diagram around a fixture 460 as a modification of the fifth embodiment.
- FIG. 21 is a structural diagram around a fixture 560 of the sixth embodiment.
- FIG. 22 is a detailed view of a first fixing tool 561.
- FIG. 23 is a structural diagram around a fixture 560 as a modification of the seventh embodiment.
- FIG. 24 is a modified example of the first fixture.
- FIG. 1 is a longitudinal sectional view of a multi-plate clutch device as one embodiment of the present invention
- FIG. 2 is a transverse sectional view of a clutch disk assembly.
- the multi-plate clutch device 1 is used to transmit and cut off power from a flywheel 3 (input rotary member) connected to an engine crankshaft 2 to a transmission input shaft 4 (output rotary member).
- a flywheel 3 input rotary member
- OO indicates the rotation axis of the flywheel 3, the transmission input shaft 4, and the multiple disc clutch device 1.
- the multi-plate clutch device 1 mainly includes a clutch cover assembly 5 and a clutch disk assembly 6.
- the clutch cover assembly 5 includes a cover member 11, a clutch cover 10, a diaphragm spring 12, and a pressure plate 7.
- the cover member 11 is a member for connecting the flywheel 3 and the clutch cover 10, and a plurality of cover members 11 are arranged on the outer peripheral side of the flywheel 3.
- the cover member 11 has a bolt portion 11a, and is attached to the flywheel 3 by a nut lib.
- the cover member 11 is engaged with a notched portion 42a of a second friction plate 42 described later.
- the clutch cover 10 is an annular member, and is attached to the cover member 11 by bolts 11c. That is, the flywheel 3 and the clutch cover 10 are fixed via the cover member 11 so as not to rotate relatively.
- the diaphragm spring 12 is for urging the pressure plate 7 in the axial direction, and has an elastic annular portion 12a and a lever portion 12b.
- the elastic annular portion 12a is an outer peripheral portion of the diaphragm spring 12, and is a portion that comes into contact with the pressure plate 7 in the axial direction.
- the lever portion 12b is a plurality of tongue-shaped portions extending inward in the radial direction from the elastic annular portion 12a, and has a leading end connected to a release device (not shown).
- the diaphragm spring 12 can be elastically deformed in the axial direction by moving the release device in the axial direction.
- the pressure plate 7 is for pressing a friction coupling portion 40 of the clutch disk assembly 6 described later toward the flywheel 3, and is an annular member disposed between the flywheel 3 and the clutch cover assembly 5. It is.
- An annular cushioning plate 80 is disposed between the pressure plate 7 and the diaphragm spring 12.
- the cushioning plate 80 is, for example, a disc spring that can be elastically deformed in the axial direction.
- a projection 81 is provided on the diaphragm spring 12 side. Further, the cushioning plate 80 is in contact with the inner peripheral side projection 7a and the outer peripheral side projection 7b of the pressure plate 7, and can be attached to and detached from the outer peripheral side projection 7b by elastic deformation of the diaphragm spring 12 in the axial direction. ing.
- the elastic reaction force of the cushioning plate 80 is set smaller than the pressing load of the pressure plate 7. Therefore, even if the pressure plate 7 thermally expands in the axial direction due to frictional heat in the half-clutch state, for example, the cushioning plate 80 can absorb the deformation due to the thermal expansion. As a result, even if the half-clutch is held, it is possible to prevent the vehicle from starting unintentionally against the intention of the driver who does not suddenly increase the clutch torque and to suppress abnormal wear of the friction plate and the like.
- the pressure plate 7 can be moved in the axial direction by the biasing force of the diaphragm spring 12 via the cushioning plate 80 described above.
- the clutch disc assembly 6 is for transmitting and releasing power by frictionally engaging the flywheel 3, and is disposed between the flywheel 3 and the pressure plate 7.
- the structure of the clutch disk assembly 6 will be described in detail.
- the clutch disc assembly 6 is used for a clutch device of a vehicle, particularly for a multi-plate clutch device 1 of a vehicle that requires a high transmission torque as compared with the clutch size, and includes a spline hub 20, a damper mechanism 30, And a friction coupling portion 40.
- a friction plate described later and a ring member are connected in the form of a gear.
- the spline hub 20 is for fixing the clutch disc assembly 6 to the transmission input shaft 4, and includes a boss portion 21, a flange portion 22, and a force.
- the boss portion 21 is a cylindrical member having a spline hole 21a on the inner peripheral surface, and is engaged with the spline portion 4a of the transmission input shaft 4 so as to be relatively non-rotatable and relatively movable in the axial direction.
- the flange portion 22 is a substantially disk-shaped member that protrudes radially outward over the entire outer circumference of the boss portion 21.
- the flange portion 22 is provided with a plurality of housing portions 22a for housing a torsion spring 32 described later.
- the flange 22 corresponds to the housing 22a.
- a second engaging portion 22b protruding outward in the radial direction is provided at the designated position.
- the damper mechanism 30 is for absorbing shocks and vibrations transmitted from the friction connecting portion 40, and includes a torsion spring 32, a clutch plate 35 and a retaining plate 36 (a pair of connecting plates), and a friction plate. And a wave spring 34.
- the torsion spring 32 is for absorbing vibration in the rotational direction between the flange portion 22 and the clutch plate 35 and the retaining plate 36, and is provided in the housing portion 22a of the flange portion 22 so as to be expandable and contractible in the rotational direction. Is contained. In the present embodiment, six torsion springs 32 are arranged in the rotation direction.
- the clutch plate 35 and the retaining plate 36 are a pair of annular members, and are disposed so as to be rotatable relative to the spline knob 20 with the flange portion 22 sandwiched in the axial direction.
- the clutch plate 35 and the retaining plate 36 are provided with window holes 35a and 36a formed by notches at positions corresponding to the torsion spring 32, respectively.
- the rotation direction ends of the housing portion 22a and the window holes 35a and 36a are engaged with the end portion of the torsion spring 32 in the rotation direction. Therefore, when the spliner and the brake 20 and the clutch plate 35 and the retaining plate 36 rotate relative to each other, the torsion spring 32 is compressed in the rotational direction.
- the friction washer 33 and wave spring 34 are used to stabilize the sliding resistance (hysteresis torque) generated when the flange 22 contacts the clutch plate 35 and the retaining plate 36.
- These are annular members arranged between the plate 35 and the retaining plate 36, respectively.
- the absorption performance of the damper mechanism is determined by the elastic coefficient, stroke, number, and position in the radial direction of the torsion spring. For example, when the elastic coefficient of the torsion spring is increased, the torsional rigidity of the damper mechanism is also increased, so that it is possible to absorb the shock when the clutch is connected, but it is not possible to effectively absorb the small torsional vibration. Also, when the elastic coefficient of the torsion spring is reduced, the torsional rigidity of the damper mechanism is also reduced, so that it is possible to effectively absorb small torsional vibrations such as engine rotation fluctuations, but to absorb the shock when the clutch is connected. Can not. Therefore, the damper mechanism has low torsional stiffness and high torsional stiffness to absorb the shock and a wide range of torsional vibrations when the clutch is engaged. Is preferred.
- the damper mechanism 30 of the present embodiment has two levels of torsional rigidity.
- the housing portions 22a of the flange portion 22 are provided at six places.
- the housing portions 22a at three places have slightly longer lengths in the rotation direction, and a gap is provided between the rotation direction end of the housing portion 22a and the end of the torsion spring 32.
- the friction connection portion 40 is for frictionally engaging the flywheel 3 and the pressure plate 7, and includes a ring member 44, a stop pin 45 (fixing member), a first friction plate 41, and a second friction plate 42. Consists of
- the ring member 44 connects the damper mechanism 30 and the first friction plate 41.
- the ring member 44 is an annular member disposed on the outer peripheral side of the damper mechanism 30, more specifically, on the outer peripheral side of the flange portion 22, and is partially sandwiched between the clutch plate 35 and the retaining plate 36. In this state, it is fixed by the stop pin 45.
- the ring member 44 is a member for fixing a friction plate described later and the damper mechanism 30 so as not to rotate relative to each other, and has a first engagement portion 44a, external teeth 44b, and a projection 44c.
- the first engagement portion 44a is a plurality of protrusions protruding radially inward from the inner peripheral side of the ring member 44.
- the first engagement portion 44a is disposed between the second engagement portions 22b of the flange portion 22, and a gap is formed between the first engagement portion 44a and the second engagement portion 22b in the rotational direction. Is provided.
- the position of the first engagement portion 44a corresponds to the position of the stop pin 45!
- the external teeth 44b project radially outward formed over the entire outer periphery of the ring member 44. And a plurality of projections, which are engaged with a first friction plate described later.
- the protrusion 44c is a portion that protrudes further outward in the radial direction from the plurality of external teeth 44b, and is disposed between the pair of first friction plates 41.
- FIG. 3 shows a cross-sectional view of the stop pin 45.
- the stop pin 45 is of a rivet type, and includes a body 45a, a head 45b, and a stepped portion 45c.
- the body portion 45a is a portion that penetrates the clutch plate 35, the retaining plate 36, and the ring member 44 in the axial direction, and has a cylindrical shape.
- the head portion 45b is a portion for fastening the clutch plate 35 and the retaining plate 36 to the ring member 44 side, respectively.
- the head 45b is provided at both ends of the trunk 45a, and has a larger outer diameter than the trunk 45a.
- the stepped portion 45c is a portion that penetrates the hole 35b of the clutch plate 35, and is provided between the trunk 45a and one head 45b.
- the step 45c has a smaller outer diameter than the head 45b, which has a larger outer diameter than the trunk 45a.
- a normal rivet is inserted into a hole of a member with one head not formed, and the head is formed by forcing a torso projecting to the side opposite to the insertion side to form a head and connect the members. You. At this time, the body on the side to be squeezed is deformed by the applied force to increase the outer diameter, so that the outer peripheral surface of the rivet abuts the inner peripheral surface of the hole.
- the stop pin 45 is provided with the stepped portion 45c, the outer peripheral surface of the stop pin 45 and the hole 35b are formed on the side opposite to the side where the stepped portion 45c is strengthened by increasing the accuracy of the stepped portion 45c. Since the gap with the peripheral surface is reduced, the fastening strength is improved. Therefore, the strength of the damper mechanism 30 is increased, and the damper mechanism 30 can be used for high loads.
- FIG. 4 shows a cross-sectional view of the stop pin 55.
- the stepped portion 45c of the stop pin 45 is a tapered portion 55c whose outer diameter gradually increases as a force is applied from the trunk to the head.
- the first friction plate 41 frictionally engages with the flywheel 3, the pressure plate 7, and the second friction plate 42, and has an annular shape disposed on the outer peripheral side of the damper mechanism 30. It is a member.
- the first friction plate 41 has internal teeth 41a as a plurality of protrusions formed over the entire inner circumference.
- the internal teeth 41a are engaged with the external teeth 44b of the ring member 44, and the first friction plate 41 and the ring member 44 are relatively non-rotatable and relatively movable in the axial direction by the internal teeth 41a and the external teeth 44b. Has become.
- the second friction plate 42 is for frictionally engaging with the first friction plate 41, and is an annular member disposed between the pair of first friction plates 41.
- the number of the first friction plates 41 is two, the number of the second friction plates 42 is one.
- the second friction plate 42 has a plurality of notches 42a formed over the entire outer circumference. Since the notch portion 42a is engaged with the cover member 11 of the clutch cover assembly 5, the second friction plate 42 and the clutch cover assembly 5 engage with each other so as not to rotate relatively and to be relatively movable in the axial direction. ing.
- the pressure plate 7 and the clutch cover assembly 5 cannot rotate relative to each other and can move relative to each other in the axial direction. Is engaged.
- the first and second friction plates 41 and 42, the flywheel 3 and the pressure plate 7 employ a carbon composite material.
- the carbon composite material is a composite material containing carbon as a main component, for example, a composite material of carbon and another material or a composite material of carbon materials (carbon carbon composite material).
- the friction coefficient of the carbon composite material is larger in some materials than the friction coefficient of the conventional friction material, and tends to fluctuate greatly depending on the temperature between different materials.
- the coefficient of friction between carbon composite materials is stable with little fluctuation due to temperature. Therefore, by using a carbon composite material for all materials to be frictionally engaged, a stable high friction coefficient can be obtained, and the multi-plate clutch device 1 can be reliably reinforced for a high load. .
- the release device moves toward the flywheel 3 in the axial direction by operating the driver's clutch pedal, and the elastic annular portion 12a of the diaphragm spring 12 urges the pressure plate 7 toward the flywheel 3 in the axial direction. I do. Then, the pressure plate 7 is pressed toward the friction coupling portion 40, and the first and second friction plates 41, 42 are held between the rotating pressure plate 7 and the flywheel 3, and the frictional resistance is reduced at each contact surface. Occurs. Thus, the torque input to the flywheel 3 is transmitted to the first friction plate 41, the ring member 44, the clutch plate 35, and the retaining plate 36.
- the clutch plate 35 and the retaining plate 36 rotate by the input torque, they rotate relative to the stopped spline knob 20.
- the receiving portion 22a of the flange portion 22 has a longer length in the rotational direction at the three force points, first, the three torsion springs 32 are connected to the receiving portion 22a and the window holes 35a, 36a. Compressed between the ends in the rotation direction. As a result, the multi-plate clutch device 1 can absorb small torsional vibration when the clutch is engaged.
- the clutch release operation is performed by moving the release device toward the axial transmission by pedal operation.
- the force described in the pull type may be a push type as shown in FIG.
- the quietness of the multi-plate clutch device 1 is improved by the damper mechanism 30.
- the clutch disk assembly 106 is used in the multi-plate clutch device 1 and is a device for transmitting torque from a flywheel (not shown) on the engine side to a transmission input shaft (not shown).
- . 6 and 7, OO is the rotation axis of the clutch disk assembly 106.
- the clutch disk assembly 106 has a feature in a connection portion between the first friction plate 141 and the ring member 144 as shown in FIGS. Specifically, the first friction plate 141 of the clutch disk assembly 106 is directly connected to the ring member 144 by the fixing member 160 in a state where relative rotation and relative movement in the axial direction are restricted. .
- FIG. 8 shows a structural diagram around the fixture 160.
- a plurality of notches 105 are formed at predetermined regular intervals in the circumferential direction, as shown in FIG.
- the notch 105 is formed to have a predetermined depth and a predetermined width from the inner peripheral edge toward the outer peripheral side, and the pair of side surfaces 105a and 105b P is parallel to each other.
- the ring member 144 has a disk-shaped outer peripheral fixing portion 144a formed over the entire circumference.
- the two first friction plates 141 are arranged so that the inner peripheral portion sandwiches the outer peripheral fixing portion 144a.
- a second friction plate 142 is disposed on the outer peripheral side of the outer peripheral fixing portion 144a .
- the fixture 160 includes a first fixture 161, a second fixture 162, and a pusher 163.
- the first fixing members 161 are disposed as a pair on both sides in the axial direction of the outer peripheral fixing portion 144a, and have a substantially cylindrical body 167 inserted into the notch 105 of the first friction plate 141.
- the second fixing member 162 is a rivet, and includes a shaft portion 164, a flange portion 165, and a fixing portion 166.
- the shaft portion 164 is a portion that penetrates the first fixing tool 161 and the outer peripheral fixing portion 144a in the axial direction.
- the collar 165 is formed at one end of the shaft 164.
- the fixing portion 166 is formed at the other end of the shaft portion 164.
- the flange portion 165 and the fixing portion 166 are formed to be larger in diameter than the shaft portion 164, and a large-diameter washer 163 is provided between the collar portion 165 and the fixing portion 166 and the body portion 167. Each is sandwiched. Since the fixing portion 166 corresponds to the side where the rivet is tightened, the body portion 167 and the washer 163 are fixed to the outer peripheral fixing portion 144a by finally tightening the fixing portion 166. As a result, the first friction plate 141 is connected to the damper mechanism 30 via the ring member 144.
- the width (the length between the pair of flat surfaces 167a and 167b) of the body 167 of the first fixture 161 is set to be narrower than the circumferential width of the notch 105 of the first friction plate 141. And is inserted into the notch 105 with a predetermined gap. Further, the flat surfaces 167a and 167b are constituted by surfaces parallel to each other. As a result, the notch 105 and the body 167 of the first fixture 161 make surface contact instead of point contact, so that the surface pressure is reduced and the wear of the first friction plate 141 can be suppressed.
- the length of the body portion 167 is set longer than the thickness of the first friction plate 141, and the first friction plate 141 is fixed to the ring member 144 with a degree of freedom in the axial direction.
- the first friction plate 141 is made of carbon, and the fixture 160 and the clutch plate 135 are each formed of an iron-based material. This is effective in such cases. Also, remove the first friction plate 141 The first friction plate 141 and the second friction plate 141 can be easily disengaged from each other when the clutch is disengaged, because the first friction member 141 and the second friction plate 141 can be easily disengaged.
- the carbon friction plate refers to a friction plate made of a carbon composite material.
- a carbon composite material is a composite material containing carbon as a main component, for example, a composite material of carbon and another material, or a composite material of carbon fibers (carbon-carbon composite material). There is.
- the thickness of the outer peripheral fixing portion 144a is set smaller than the thickness of the second friction plate 142. Therefore, when the two first friction plates 141 are clamped between the flywheel (not shown) and the pressure plate (not shown) when the clutch is engaged, the outer peripheral fixing portion 144a causes the first friction plate 144a to engage. The friction engagement between the plate 141 and the second friction plate 142 is not hindered.
- the flange portion 165 and the fixing portion 166 are formed to have the same diameter as or a smaller diameter than the body portion 167. Further, a washer 163 having a larger diameter than the two portions 165 and 166 is provided between the flange portion 165 and the fixed portion 166 and the first friction plate 141. The outer diameter of the washer 163 is set to be larger than the circumferential width of the notch 105. Accordingly, the axial relative movement of the first friction plate 141 is reliably restricted without setting the outer diameters of the collar portion 165 and the fixed portion 166 large.
- the mechanism for restricting the axial movement of the first friction plate 141 is simplified, and the first friction plate 141 The structure around the mounting portion of 141 is simplified. Further, since the connection by the meshing of the gears is used, the rattling noise at the joint between the first friction plate 141 and the ring member 144 in the conventional device is further reduced.
- the multi-plate clutch device 1 in which the friction plate is composed of a pair of the first friction plate 141 and the second friction plate 142 is described.
- the present invention is also applicable to a single-plate clutch device.
- the clutch disc assembly 206 mainly includes a carbon friction plate 241 pressed against the flywheel on the engine side, a damper mechanism 230 to which the friction plate 241 is fixed, and a friction plate 241 and a damper mechanism 230. And a fixture 260 for connection.
- the structure other than the vicinity of the fixture 260 is the same as that of the above-described embodiment, and thus the detailed description is omitted.
- the carbon friction plate refers to a friction plate made of a carbon composite material.
- the carbon composite material is a composite material containing carbon as a main component, for example, a composite material of carbon and another material or a composite material of carbon (carbon-carbon composite material). is there.
- the fixture 260 is formed by rivets. Specifically, the fixture 260 is inserted into the notch 205 of the friction plate 241 and the hole 235a of the clutch plate 235 to directly connect the friction plate 241 to the outer periphery of the clutch plate 235.
- FIG. 11 and 12 show the fixture 260 after assembly
- FIG. 12 shows the fixture 260 before assembly (before swaging).
- the fixing tool 260 has a collar part 265, a body part 267, and a fixing part 266.
- the flange portion 265 has a larger diameter than the other portions, and the surface on the body portion 267 side is in contact with the side surface of the friction plate 241.
- the flange 265 is arranged so as to be located further inward than the inner peripheral end of the flywheel, the force protruding from the friction surface of the friction plate 241 toward the flywheel.
- the body portion 267 is formed by forming a pair of opposed flat surfaces 267a and 267b on a part of a portion formed continuously with the same diameter as the flange portion 265. Inserted into The width of the body 267 (the length between the pair of flat surfaces 267a and 267b) is set to be narrower than the width of the notch 205 of the friction plate 241. Has been inserted. Further, unlike the case of the second embodiment, the length of the body portion 267 may be set to be substantially equal to the thickness of the friction plate 241 or may be set to be longer than the thickness of the friction plate 241. good.
- the friction plate 241 When the length of the body portion 267 is set to be substantially equal to the thickness of the friction plate 241, the friction plate 241 is completely fixed and cannot move with respect to the clutch plate 235. If the length is set long, both will be fixed with a degree of freedom in the axial direction.
- the friction plate 241 Made of carbon, the fixture 260 and the clutch plate 235 are made of iron-based materials, and have different coefficients of thermal expansion.Effective in cases where the effects of thermal expansion cannot be ignored due to high temperatures It is.
- the fixing portion 266 has a smaller diameter than the body portion 267, and is inserted into the hole 235a of the clutch plate 235. By caulking the end of the fixing portion 266, the friction plate 241 and the clutch plate 235 are fixed to each other, and the movement of the friction plate 241 in the axial direction is restricted.
- the fixture 260 is formed by rivets, but may be the following embodiment.
- FIG. 14 shows a structural diagram around the fixture 360 of the present embodiment.
- the fixing device 360 includes a first fixing device 361 and a second fixing device 362.
- FIG. 15 shows a detailed view of the first fixture 361.
- the first fixture 361 has a substantially cylindrical body 367 inserted into the notch 305 of the friction plate 341. On the same month 367, flat surfaces 365a and 365b corresponding to the notch 305's Tsukuda J surfaces 305a and 305b are formed.
- the first fixture 361 is fixed to the clutch plate 335 by the second fixture 362 as shown in FIG.
- the second fixing member 362 is a rivet, and includes a shaft portion 364 penetrating the first fixing member 361, and a flange portion 365 and fixing portions 366 formed at both ends of the shaft portion 364.
- the flange portion 365 has an outer diameter larger than the width of the notch 305 in the circumferential direction, and a surface on the body portion 367 side is in contact with a side surface of the friction plate 341.
- the fixing portion 366 has a smaller diameter than the body portion 367, and is inserted into the hole 335a of the clutch plate 335.
- the first fixing member 361 is fixed to the clutch plate 335 by squeezing the end of the fixing portion 366. Since the length of the body 367 can be set according to the thickness of the friction plate 341 as in the third embodiment, the length of the body 367 is adjusted to connect the friction plate 341 to the clutch plate 335. It is possible to connect such that they can move relative to each other or cannot. With the fixture 360 described above, the same effects as in the third embodiment can be obtained.
- a washer 363 may be interposed between the flange portion 365 and the friction plate 341.
- the diameter of the flange portion 365 can be further reduced.
- a connecting member 370 instead of providing the washer 363, a connecting member 370 may be provided.
- the connecting member 370 is an annular member, and is for connecting a plurality of fixing tools 360 arranged in the circumferential direction.
- the connecting member 370 has a connecting hole 371 at a position corresponding to the fixture 360, and the shaft portion 364 of the second fixture 362 penetrates.
- the connecting member 370 is sandwiched between the trunk 367 and the flange 365. This stabilizes the relative positions of the plurality of fixtures 360, and reliably restricts the relative movement of the friction plate 341 in the axial direction with respect to the clutch plate 335 without providing a large outer diameter washer.
- the second fixture 362 is formed by rivets, but the following embodiment may be used.
- FIG. 18 shows a fixture 460 of the present embodiment.
- the fixing tool 460 includes a first fixing tool 461, a second fixing tool 462, and a pusher 463.
- FIG. 19 shows a detailed view of the first fixture 461.
- the first fixture 461 has a rivet structure in part, and has a generally cylindrical body 467 inserted into the notch 405 of the friction plate 441 and a fixed part formed at one end of the body 467. It has ⁇ 466.
- the flat surface 467a, 467b corresponding to the Tsukuda J surface 405a, 405b of the notch 405 is formed on the same month 467.
- the fixing portion 466 has a smaller diameter than the body portion 467 and is inserted into the hole 435a of the clutch plate 435.
- the fixing portion 466 shown in FIG. 19 shows a state before being reinforced.
- the second fixing tool 462 is a so-called screw, and has a collar portion 465 and a connecting portion 468.
- the flange portion 465 has a diameter substantially equal to that of the body portion 467, and has a hole 465a for screwing the second fixing tool 462 into the first fixing tool with a tool.
- the hole 465a is a hexagonal hole.
- the connecting portion 468 is a portion connecting the first fixture 461 and the collar portion 465, and is screwed into the screw hole 465e of the body portion 467.
- An annular washer 463 is sandwiched between the trunk 467 and the collar 465.
- the outer diameter of the washer 463 is set to be larger than the circumferential width of the notch 405.
- a connecting member 470 may be provided similarly to the fourth embodiment. Accordingly, the relative positions of the plurality of fixing tools 460 can be stabilized, and the relative movement in the axial direction of the friction plate 441 with respect to the clutch plate 435 can be reliably regulated without providing a large outer diameter washer.
- the first fixture 461 is described as a rivet, but the following embodiment may be used.
- FIG. 21 shows a fixture 560 of the present embodiment.
- the fixing tool 560 includes a first fixing tool 561, a second fixing tool 562, and a pusher 563.
- FIG. 22 shows a detailed view of the first fixture 561.
- the first fixture 561 has a generally cylindrical lumber 567 inserted into the notch 505 of the friction plate 541. In the same month 567, flat surfaces 567a and 567b are formed corresponding to the notches 505 and 505b of the notch 505!
- the second fixing tool 562 is a so-called screw, and has a collar portion 565, a connecting portion 568, and a fixing portion 566.
- the flange 565 has the same diameter as the trunk 567, and has a hole 565a into which the second fixing tool 562 is screwed.
- the hole 565a is a hexagonal hole.
- Both the connecting portion 568 and the fixing portion 566 are formed with screws on the outer peripheral side.
- the connecting portion 568 connects the first fixture 561 and the flange portion 565, and is screwed into the screw hole 567e of the body portion 567.
- the fixing portion 566 is a component for fixing the clutch plate 535 and the trunk portion 567, and is accumulated on the mosquito 535a of the clutch plate 535.
- An annular washer 563 is interposed between the lunar part 567 and the collar part 565.
- the outer diameter of the washer 563 is set to be larger than the circumferential width of the notch 505.
- a connecting member 570 may be provided similarly to the fourth and fifth embodiments. Accordingly, the relative positions of the plurality of fixing members 560 are stabilized, and the relative movement of the friction plate 541 in the axial direction with respect to the clutch plate 535 can be reliably regulated without providing a large outer diameter washer.
- Type of multi-plate clutch device Although the above embodiment has been described as a dry clutch device, the present invention is not limited to this.
- the torsional rigidity of the damper mechanism is described as two stages.
- the present invention is not limited to the present embodiment, in which a single-stage specification or multi-stage torsional rigidity may be provided.
- the housing portion 22a of the flange portion 22 has two lengths in the rotation direction.
- the window holes 35a and 36a of the clutch plate 35 and the retaining plate 36 are provided. The same effect can be obtained by setting the length in the rotation direction to two types.
- a force steel material or the like in which the materials of the flywheel 3, the pressure plate 7, and the second friction plate 42 are described as a carbon composite material may be employed.
- the coefficient of friction between the carbon composite material and the other material varies depending on the temperature.
- the coefficient of friction increases with increasing temperature and decreases with decreasing temperature. Therefore, when traveling in the city as a passenger car, the temperature does not rise so much, and the friction coefficient is almost the same as that of a conventional friction material.
- the friction heat generated on the friction surface increases the temperature and increases the friction coefficient.
- the torque transmission capacity becomes larger than when the temperature is low, so that a high load and high durability can be realized in the same manner as the multi-plate clutch device for racing.
- the friction coefficient increases and the torque transmission capacity increases, so that the friction surface slips and the torque transmission recovers.
- the trunk portions 367, 567 of the first fixtures 361, 561 have a substantially cylindrical shape, and the outer peripheral surface of the cylindrical member is partially flattened.
- the shape may be such as the first fixtures 391 and 591 manufactured from square timber force.
- the present invention is applicable to a multi-plate clutch device and a clutch disk assembly, particularly to a multi-disk clutch device and a clutch disk assembly reinforced for high load.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
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- Mechanical Operated Clutches (AREA)
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2004304128A AU2004304128B2 (en) | 2003-12-22 | 2004-11-25 | Multiple disk clutch device and clutch disk assembly |
US10/583,998 US20070119679A1 (en) | 2003-12-22 | 2004-11-25 | Multiplate clutch device and clutch disk assembly |
GB0613096A GB2424929A (en) | 2003-12-22 | 2004-11-25 | Multiple disk clutch device and clutch disk assembly |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003-425477 | 2003-12-22 | ||
JP2003425477A JP2005180650A (ja) | 2003-12-22 | 2003-12-22 | クラッチディスク組立体 |
JP2004-128389 | 2004-04-23 | ||
JP2004128389A JP2005308154A (ja) | 2004-04-23 | 2004-04-23 | 多板クラッチ装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005061917A1 true WO2005061917A1 (ja) | 2005-07-07 |
Family
ID=34712975
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2004/017466 WO2005061917A1 (ja) | 2003-12-22 | 2004-11-25 | 多板クラッチ装置及びクラッチディスク組立体 |
Country Status (4)
Country | Link |
---|---|
US (1) | US20070119679A1 (ja) |
AU (2) | AU2004304128B2 (ja) |
GB (1) | GB2424929A (ja) |
WO (1) | WO2005061917A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN111853079A (zh) * | 2020-06-09 | 2020-10-30 | 东风柳州汽车有限公司 | 一种增程器机电耦合缓冲装置 |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN104854363B (zh) * | 2012-12-20 | 2018-01-09 | 舍弗勒技术股份两合公司 | 离合器装置 |
WO2017142944A1 (en) * | 2016-02-16 | 2017-08-24 | Eaton Corporation | Tabbed friction plate clutch |
SI25556A (sl) * | 2017-11-08 | 2019-05-31 | Tajfun Planina Proizvodnja Strojev, D.O.O. | Torni kolut za prenos vrtilnega momenta pri sklopki ali zavori |
US11174903B1 (en) * | 2019-05-28 | 2021-11-16 | Logan Clutch Corporation | Clutch assembly and system |
Citations (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1524771A (en) * | 1922-10-21 | 1925-02-03 | Clarence G Wood | Clutch |
US1896025A (en) * | 1928-03-17 | 1933-01-31 | Packard Motor Car Co | Motor vehicle clutch |
JPS48104971U (ja) * | 1972-03-15 | 1973-12-06 | ||
JPS5473463U (ja) * | 1977-11-01 | 1979-05-25 | ||
JPS54167251U (ja) * | 1978-05-16 | 1979-11-24 | ||
JPS59133829A (ja) * | 1982-12-24 | 1984-08-01 | ル−ク・ラメレン・ウント・クツプルングスバウ・ゲゼルシヤフト・ミツト・ベシユレンクテル・ハフツング | クラツチ板、殊に自動車用のクラツチ板 |
JPS60205022A (ja) * | 1984-02-17 | 1985-10-16 | オ−トモ−チブ プロダクツ ピ−エルシ− | 摩擦クラツチ従動板 |
JPS63132127U (ja) * | 1987-02-20 | 1988-08-30 | ||
JPH02203029A (ja) * | 1988-12-09 | 1990-08-13 | Borg Warner Automot Gmbh | 摩擦ライニング支持体とハブを結合するスプリングコレットを備えた摩擦素子 |
JPH0468226U (ja) * | 1990-10-25 | 1992-06-17 | ||
GB2300233A (en) * | 1995-04-21 | 1996-10-30 | Fichtel & Sachs Ag | Friction clutch for an automobile |
JPH09177821A (ja) * | 1995-12-09 | 1997-07-11 | Fichtel & Sachs Ag | 炭素製プレッシャプレートを有する摩擦クラッチ |
JPH09250556A (ja) * | 1996-03-19 | 1997-09-22 | Exedy Corp | 多板クラッチ |
JPH10141387A (ja) * | 1996-09-11 | 1998-05-26 | Exedy Corp | 多板クラッチ |
JP2002181072A (ja) * | 2000-12-11 | 2002-06-26 | Akurosu:Kk | 摩擦単板クラッチ |
JP2002195290A (ja) * | 2000-10-18 | 2002-07-10 | Os Giken:Kk | 多板クラッチ装置 |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1742805A (en) * | 1926-01-19 | 1930-01-07 | Brown Lipe Gear Co | Clutch construction |
JPS5473463A (en) * | 1977-11-22 | 1979-06-12 | Sekisui Chem Co Ltd | Method of treating waste water containing starchy substances |
DE2845855A1 (de) * | 1978-10-20 | 1980-04-30 | Luk Lamellen & Kupplungsbau | Reibungskupplung, insbesondere fuer kraftfahrzeuge |
FR2600731B1 (fr) * | 1986-06-27 | 1990-12-07 | Valeo | Embrayage a volant amortisseur, notamment pour vehicule automobile. |
JPS63132127A (ja) * | 1986-11-21 | 1988-06-04 | Tdk Corp | 圧力センサ− |
US4846326A (en) * | 1987-11-27 | 1989-07-11 | Tilton Mclane | Carbon to carbon friction clutch |
IT1245969B (it) * | 1990-05-31 | 1994-11-07 | Valeo | Innesto a piu' dischi di frizione, in particolare per autoveicoli |
JPH0711338B2 (ja) * | 1990-07-09 | 1995-02-08 | 株式会社ノーリツ | 温水暖房機 |
DE69332562T2 (de) * | 1992-08-13 | 2003-07-10 | Tilton Engineering, Inc. | Kohlenstoff-kohlenstoff reibmechanismus |
US5927459A (en) * | 1993-03-19 | 1999-07-27 | Exedy Corporation | Modular clutch |
GB9506141D0 (en) * | 1995-03-25 | 1995-05-10 | Automotive Products Plc | A friction clutch plate assembly |
US5904234A (en) * | 1996-03-19 | 1999-05-18 | Exedy Corporation | Multi-plate dry clutch having hub movement limiting means |
CN1131745C (zh) * | 1998-08-28 | 2003-12-24 | 株式会社理光 | 连接构件的分解方法、分解装置、附件结构及其生产*** |
DE10064248A1 (de) * | 2000-12-22 | 2002-07-04 | Zf Sachs Ag | Graugusslegierung für ein Reibelement einer Reibungskupplung und Reibelement für eine Reibungskupplung |
DE10145638A1 (de) * | 2001-09-15 | 2003-04-10 | Porsche Ag | Kupplung, vorzugsweise Mehrscheibenkupplung |
-
2004
- 2004-11-25 WO PCT/JP2004/017466 patent/WO2005061917A1/ja active Application Filing
- 2004-11-25 GB GB0613096A patent/GB2424929A/en not_active Withdrawn
- 2004-11-25 US US10/583,998 patent/US20070119679A1/en not_active Abandoned
- 2004-11-25 AU AU2004304128A patent/AU2004304128B2/en not_active Ceased
-
2009
- 2009-12-24 AU AU2009251222A patent/AU2009251222A1/en not_active Abandoned
Patent Citations (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1524771A (en) * | 1922-10-21 | 1925-02-03 | Clarence G Wood | Clutch |
US1896025A (en) * | 1928-03-17 | 1933-01-31 | Packard Motor Car Co | Motor vehicle clutch |
JPS48104971U (ja) * | 1972-03-15 | 1973-12-06 | ||
JPS5473463U (ja) * | 1977-11-01 | 1979-05-25 | ||
JPS54167251U (ja) * | 1978-05-16 | 1979-11-24 | ||
JPS59133829A (ja) * | 1982-12-24 | 1984-08-01 | ル−ク・ラメレン・ウント・クツプルングスバウ・ゲゼルシヤフト・ミツト・ベシユレンクテル・ハフツング | クラツチ板、殊に自動車用のクラツチ板 |
JPS60205022A (ja) * | 1984-02-17 | 1985-10-16 | オ−トモ−チブ プロダクツ ピ−エルシ− | 摩擦クラツチ従動板 |
JPS63132127U (ja) * | 1987-02-20 | 1988-08-30 | ||
JPH02203029A (ja) * | 1988-12-09 | 1990-08-13 | Borg Warner Automot Gmbh | 摩擦ライニング支持体とハブを結合するスプリングコレットを備えた摩擦素子 |
JPH0468226U (ja) * | 1990-10-25 | 1992-06-17 | ||
GB2300233A (en) * | 1995-04-21 | 1996-10-30 | Fichtel & Sachs Ag | Friction clutch for an automobile |
JPH09177821A (ja) * | 1995-12-09 | 1997-07-11 | Fichtel & Sachs Ag | 炭素製プレッシャプレートを有する摩擦クラッチ |
JPH09250556A (ja) * | 1996-03-19 | 1997-09-22 | Exedy Corp | 多板クラッチ |
JPH10141387A (ja) * | 1996-09-11 | 1998-05-26 | Exedy Corp | 多板クラッチ |
JP2002195290A (ja) * | 2000-10-18 | 2002-07-10 | Os Giken:Kk | 多板クラッチ装置 |
JP2002181072A (ja) * | 2000-12-11 | 2002-06-26 | Akurosu:Kk | 摩擦単板クラッチ |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN111853079A (zh) * | 2020-06-09 | 2020-10-30 | 东风柳州汽车有限公司 | 一种增程器机电耦合缓冲装置 |
Also Published As
Publication number | Publication date |
---|---|
AU2009251222A1 (en) | 2010-01-28 |
AU2004304128A1 (en) | 2005-07-07 |
GB0613096D0 (en) | 2006-08-23 |
US20070119679A1 (en) | 2007-05-31 |
GB2424929A (en) | 2006-10-11 |
AU2004304128B2 (en) | 2009-11-12 |
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