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
  • F16D13/46—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs in which two axially-movable members, of which one is attached to the driving side and the other to the driven side, are pressed from one side towards an axially-located member
  • F16D13/48—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs in which two axially-movable members, of which one is attached to the driving side and the other to the driven side, are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member
• • 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
  • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
  • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
  • F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings

Definitions

• the present invention provides a so-called pull type in which a release lever is pulled to a transmission side by a release lever connected to a clutch pedal to perform a release operation. It relates to the clutch of this.
• a coil spring 100 that is arranged in an inclined state is used as a load generating member, and a retainer 1 is used.
• the spring force is transmitted to the plate 102, and the clamp plate is connected to the plate 106 through the retainer 110 ′ 2, and the solenoid 104.
• the structure is such that a press-contact force is applied to the sock 108 (Japanese Patent Publication No. 46-15046).
• a diaphragm spring 110 is used, and the diaphragm spring 110 is an annular projection.
• the outer periphery of the diaphragm spring 110 is fitted to 112 and is held by the clutch cover 116.
• the retainer 1 1 1 1 is connected to the flange 1 1 7 of the sleeve 1 1 3 via the thrust transmission member 1 1 8 through the cone spring. (1) They are pressed against each other with the spring force of 119.
• the level of (1) will be particularly large, and the engine speed will increase. Raising the vibration gradually reduces the vibration.
• the vibration will be reduced to one and the discomfort will increase.
• the present invention provides a clutch capable of preventing vibration caused by misalignment between a sleeve and a retainer in a so-called pull-type clutch.
• the purpose is to provide a service.
• the release bearing is pulled by the release lever connected to the clutch pedal so as to keep the release bearing away from the flywheel.
• the clutch disk is spline-fitted to the input shaft on the transmission side, and a sleeve is provided on the outer periphery of the input shaft. Attach the release bearing to the end of the sleeve on the transmission side, and attach the sleeve to the flywheel end of the sleeve in the radial direction of the sleeve.
• a load that forms a flange part that protrudes outward, and that transmits the sleeve force and the pressure contact force to the clutch disk to this flange part.
• a retainer for transmission is pressed against the retainer in a locked state, and a retainer and a sleeve are provided between the retainer and the flange.
• a retainer and a sleeve are provided between the retainer and the flange.
• a clutch cover is provided to cover the cover, and a spring member is disposed between the clutch cover and the retainer, and a spring cover is provided between the retainer and the pleated plate.
• a lever for transmitting the spring force of the spring member is provided between the retainer and the clutch cover to allow the retainer to move in the axial direction between the retainer and the clutch cover.
• This clutch features a connecting member that connects the retainers.
• the retainer and the sleeve are in contact with the spherical surface on the flange side and the spherical surface on the sleeve side, the retainer and the sleeve force ⁇ Even with the supra-alignment, the spherical surface and the spherical seat are in contact with each other around the circumference, and the vibration transmitted to the sleeve by the retainer is not generated.
• FIG. 1 is a longitudinal sectional view of the clutch to which the present invention is applied
• FIG. 2 is a view taken in the direction of the arrow in FIG. 1
• FIG. 3 is the spring force of the diaphragm spring.
• FIG. 4 is a longitudinal sectional view showing another embodiment of the connecting member
• FIG. 4a is a longitudinal sectional view showing another embodiment of the spherical surface
• FIG. 4c and 4d are longitudinal sectional views each showing still another embodiment
• FIG. 5 is a longitudinal sectional view showing a conventional example
• FIG. 6 is a longitudinal sectional view showing the prior art of the applicant. It is.
• FIG. 1 (a sectional view taken along line A-0-A in FIG. 2) showing a longitudinal sectional view of the clutch according to the present invention
• reference numeral 10 denotes a flywheel.
• Clutch disk 12, intermediate plate 14, and clutch disk 16 are pressed against the rear surface of flywheel 10 in order.
• a press plate 18 for pressing these is provided.
• Radially outward of the intermediate plate 14 is provided a pin 15 fixed to a flywheel 10, and the pin 15 is used to fly the pin 15.
• Wheel 10 and intermediate plate 14 are designed to rotate around the body.
• the clutch cover 20 is, for example, thick and thick.
• the clutch disks 12 and 16 are spline-fitted to the input shaft 22 of the subsequent transmission.
• the distal end of the input shaft 22 is pivotally supported at the center of the flywheel 10 via a pilot bearing 23.
• a cylindrical sleeve 24 is fitted around the outer periphery of the input shaft 22 in the radial direction so as to slide in the axial direction.
• a release bearing 26 is fixed with a snap ring 26a. .
• a bearing holder 28 covering the release bearing 26 is provided outside the release bearing 26.
• a pressure contact ⁇ 28 a is fixed to the rear end face of the bearing holder 28.
• a through-hole 28 b that penetrates the input shaft 22 is opened in the press contact 2 Sa.
• a thin bush 29 that fits the input shaft 22 in a freely rotatable manner into the sleeve 24 is fitted to the inner peripheral surface of the rear end of the sleeve 24.
• reference numeral 27 denotes a release lever connected to the clutch pedal, and the release lever 26 is used to pivot the release bearing 26. It moves in the direction.
• a flange portion 25 protruding outward in the radial direction of the sleeve 24 is formed, and the flange portion 25 is formed.
• a spherical surface 30 is formed on the rear end surface, and the spherical seat 33 of the retainer 32 is pressed against the spherical surface 30.
• the spherical surface 30 is formed as a spherical surface protruding rearward around the center 01 of the pilot bearing 23.
• the center of the spherical surface 30 is not limited to the center 0 1, but may be set to another position along the center ⁇ 0. Further, as shown by a two-dot line in FIG. 1, a concave spherical surface 30X may be fitted to the spherical seat 33X.
• the input shaft 22 that is supported by the pilot bearing 23 often has an angle around the center 01. Therefore, the center of the ⁇ center of the spherical surface 30 is Matching the mind O 1 is most preferred.
• the retainer 32 is biased forward by the cone spring 32b, and the cone spring 32b is It is held at 2a.
• the sleeve 24 is a forged product, for example.
• the retainer 32 is, for example, an artificial product, and is formed in a substantially annular shape. On the rear end face of the retainer 32, a press contact portion 34 is formed over the entire circumference, and an annular groove 36 is formed on the front end. In the radial direction of the retainer 32, three projections 38 are integrally formed on the outer peripheral portion at equal intervals in the circumferential direction, for example.
• a boss 40 is integrally formed on the inner surface of the clutch cover 20 corresponding to the projection 38.
• a pin 41 is provided between the boss 4 ⁇ and the projection 38, and the clutch cover 20 and the retainer 32 are integrally formed by the pin 41. They are connected to rotate. That is, the front end of the pin 41 is slidably fitted to the projection 38 via the DU bush 41a, and the rear end of the pin 41 is It is fixed to the boss part 40 by "force, staking".
• a substantially circular diaphragm spring 4 2 is provided between the clutch cover 20 and the projection 38. (Spring member) is provided.
• the outer periphery of the diaphragm spring 42 is held on the clutch cover 20 by protrusions 44 of the clutch cover 20.
• the projections 44 are formed in an annular shape over substantially the entire circumference except for the opening 52 of the clutch cover 20.
• the inner peripheral portion of the spring 42 is pressed against the press contact portion 34 of the retainer 32.
• a window hole 42 a (FIG. 2) through which the pin 41 is formed is formed in a portion of the diaphragm spring 42 corresponding to the pin 41. .
• the inner peripheral part of the diaphragm spring 42 is connected to the press contact part 34 by a mouth ruby 43 provided at a cross-sectional position different from that of Fig. 1 in the circumferential direction. It has been stopped.
• the mouth ruby 43 is fitted in a slit 45 of a diaphragm spring 42, as shown in FIG.
• the mouth ruby 43 and the slit 45 are 120 in the direction of the circle. It is formed at three places with an interval.
• a screw portion 20a is formed on the inner peripheral surface of the radially outer clutch cover 20 of the diaphragm spring 42.
• the screw portion 20a is combined with the substantially annular screw portion 48a of the azimuth ring 48.
• Protrusions 50 are formed on the rear end face of the adjusting ring 48 at, for example, 24 locations at equal intervals in the circumferential direction.
• the protrusion 50 is in the radial direction of the ring It is formed on the outer periphery.
• a window hole 52 is formed in the clutch cover 20 corresponding to the projection 50, and a lock plate 54 is formed in the window hole 52 with a bonnet 56. It is fixed. The lower end of the lock plate 54 in the figure is fitted with the protrusion 50, allowing the axial adjustment of the adjuster ring 48 in the axial direction.
• the lock plate 54 connects the adjuster ring 48 and the clutch cover 2 ⁇ integrally.
• the inner fulcrum 62 of the lever 60 is fitted into the annular groove 36, the outer fulcrum 64 is pressed against the front end face of the adjuster ring 48, and the middle fulcrum 66 is It is in pressure contact with the phenolic land 18 a of the pres- sure plate 18.
• the lever ratio between the inner fulcrum 62, the outer fulcrum 64, and the middle fulcrum 66 is set to L1: L2.
• the above-mentioned lever 60 is, for example, a metal part. As shown in FIG. 2, two cutting lines 6 S are formed on the outer periphery of the lever 60 in the radial direction, and the outer outer piece is formed. 70 is bent to form the outer peripheral fulcrum 64 and the intermediate fulcrum 66 (FIG. 1), and the central central piece 72 extending radially outward is used as an adjuster. It fits in the recess 48 b of the ring 48.
• a well-known strap plate 74 extending in the circumferential direction is provided between the outer peripheral portion of the pres- sure plate 18 and the clamp plate 20. It is located at four locations at equal intervals in the direction.
• an inertia brake 78 is inserted with the input shaft 22 fitted with the spline. Is installed.
• the inertia brake 78 has facings 80 and 82 on both end faces, and is provided between the facing 82 and the press-fitting 28a. Are separated by the release R r.
• the operation will be described. Since the sleeve 24 and the retainer 3 • 2 are continuously in contact with the spherical surface 30 and the spherical seat 33 over the entire circumference, the sleeve 24 and the retainer 3 • 2 are in contact with each other. In the case where the first and second members are eccentric so as to be displaced in the radial direction, the above-mentioned nozzle is of course. Even if the center line 0 of the sleeve 24 has a declination only by a small angle ⁇ around the center 01 of the bearing 23, the spherical surface 30. The spherical seat 33 absorbs the declination of the angle ⁇ , and the flange part 25 of the sleeve 24 and the retainer 32 come into smooth contact over the entire circumference. .
• the sleeve 24 and the retainer 32 are connected to the retainer 32 via the spherical surface 30 by the spring force of the cone spring 32b. Since it is integrated by pressing against the flange portion 25 of the sleeve 24, the sleeve 24 is circumferentially angled to the sleeve 24 as in the conventional case. There is no need to add a plane part, and the processing cost is low.
• the spring force P of the diaphragm spring 42 pushes the press-contact portion 34 of the retainer 132 forward.
• the spring force P is transmitted to the lever 60 from the inner peripheral fulcrum 62 of the annular groove 36 and is increased to about three times the lever ratio of L 1 : L 2, for example.
• the pressure is transmitted from the intermediate fulcrum 66 to the phantom drum land 18a as the pressure contact force of the clutch disks 12 and 16.
• the inner peripheral portion of the diaphragm spring 42 is stopped by the press-contact portion 34 of the retainer 32 by a mouthpiece rubin 43, and the diaphragm spring is stopped. Musspring 4 2 and retainer 3 4 Spin on the body.
• the spring characteristic of the diaphragm spring 42 is, as shown by the characteristic 90 in FIG. 3 showing the relationship between the amount of deflection D and the spring force P, the clutch spring. Since it is convex upward in the range of the waist allowance Wr corresponding to the wear amount of the discs 12 and 16, the diaphragm spring 4 2 force and other spring force P is larger than the characteristic 92 in the case of the conventional coil spring 1 (Fig. 5), and is larger than that of the press plate 18. The press-contact force to the chips 12 and 16 is increased compared to the conventional case.
• the characteristic 92 reduces the spring force P from the set load P1 to the weight load P2.
• the load at the time of setting P1 and the load at the way-in load P3 are reduced only, and the clutch disks 12 and 16 are worn.
• the so-called way-in load at the time of contact increases.
• these characteristics 9 0 As a result, the release force required at the time of release is reduced, so that the depression force of the clutch pedal is also reduced.
• the release bearing 26 is moved backward by the release lever 27, and the release bearing 26 is released.
• the sleeve 24 slides.
• the retainer 32 held by the snap ring 32 a is moved to the position of the diaphragm spring 42.
• the diaphragm spring 42 becomes in the state of R in FIG.
• the inner fulcrum 62 of the lever 60 moves rearward about the outer fulcrum 64, and the intermediate fulcrum 66 also moves rearward.
• the plate 18 is moved rearward by the spring force of the strap plate 74, and the pressure contact of the clutch disks 12 and ⁇ 6 is released.
• the sleeve 24 and the retainer 32 are continuous over the entire circumference by the spherical surface 30 and the spherical seat 33.
• the pilot bearing 23 Centering on the center 0 1 of the sleeve 2 4 The sphere 30 and the spherical seat 33 can absorb the angle of the angle a :, and the flange part 25 of the sleeve 24 can be absorbed by the spherical part 30 and the spherical seat 33.
• the retainer 32 can be brought into smooth contact with the entire circumference.
• the sleeve 24 and the retainer 32 do not come into contact with each other only in a part of the circumferential direction. In this way, it is possible to reliably prevent the vibration from being generated between the clutch pedal and the transmission of the vibration to the clutch pedal.
• the present invention is not limited to the above-described one embodiment.
• the front end of the pin 41 is press-fitted into the retainer 32, or Alternatively, the rear end of the pin 41 may be freely fitted to the D bush 4 la provided on the boss 40.
• a substantially annular friction member made of, for example, a sintered alloy is provided between the flange portion 25 and the retainer 132.
• the pusher 84 is mounted by itself, for example, by press-fitting or other means, and a spherical surface 30 is formed on the rear end face of the friction pusher 84. If the spherical surface 30 wears out over a long period of use, the friction You may be able to exchange 8 4.
• the present invention is not limited to the case where the connecting member for connecting the clutch cover 2 ⁇ and the retainer 32 is a pin 41, and the tab 10 in FIG. It can also be applied to a clutch that is connected by another connecting member such as 5th grade.
• a tab 86 integral with the clutch cover 20 is formed, and this tab 86 is attached to the retainer 32.
• the retainer 32 is allowed to slide in the axial direction with the protrusion 87, and the clutch cover 20 and the retainer 32 are connected in the circumferential direction. It may be connected to.
• the diaphragm spring 42 has a hole 85 through which a tab 86 is passed.
• the diaphragm spring 42 is held by the stationary bin 88 and the two wire rings 89. You can do it.
• a stud bin 88, a wire ring 89, and a pin 41 may be combined.
• the spring member of the present invention is not limited to the above-described diaphragm spring 42 having a substantially circular shape as described above. You can also use Pring 1 ⁇ ⁇ .

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Mechanical Operated Clutches (AREA)

Applications Claiming Priority (2)

Publications (1)

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ID=17221123

Family Applications (1)

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Cited By (1)

Families Citing this family (17)

Citations (2)

Family Cites Families (11)

• 1986
  • 1986-10-21 JP JP61251324A patent/JPS63106429A/ja active Granted
• 1987
  • 1987-10-05 WO PCT/JP1987/000746 patent/WO1988003233A1/ja unknown
  • 1987-10-05 US US07/221,828 patent/US4890708A/en not_active Expired - Lifetime

Patent Citations (2)

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