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
  • F16D13/58—Details
  • F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
  • F16D13/71—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members in which the clutching pressure is produced by springs only
• • 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
  • F16D13/583—Diaphragm-springs, e.g. Belleville
  • F16D13/585—Arrangements or details relating to the mounting or support of the diaphragm on the clutch on the clutch cover or the pressure plate

Definitions

• the present invention relates to a clutch cover assembly in which a spring member for pressing a push plate is disposed outside the cutter cover.
• reference numeral 10 denotes a flywheel of the engine, and a clutch is provided between the flywheel 10 and the press plate 12. Tied disk 14 is sandwiched.
• the plastic plate 12 is surrounded by a metal cover 16, and a ring member 18 having an annular plate shape is provided outside the clutch cover 6.
• 0 lever 2 For example, 0 is arranged at equal intervals in the circumferential direction of the clutch, for example, at four locations.
• the bearings 24 are concentric with the input shaft 22. The peripheral end is pressed.
• the spring member 18 is supported by the inner peripheral portion of the clutch cover 16 in the conventional example shown in FIG.
• the clutch cover 16 is easily bent by the reaction force of the spring member 18, and the movement of the tip of the lever 20 is reduced by the amount of the bent of the clutch cover 16.
• the moving amount of the press plate 12 with respect to the moving amount of the lever 20, that is, the release efficiency is reduced.
• the present invention can improve the release efficiency and reduce the spring force of a spring member in a clutch cover assembly in which an annular ⁇ -shaped spring member is disposed outside the clutch cover. It is an object of the present invention to provide a clutch cover assembly that can set a large lever ratio for boosting and can shorten the axial length.
• a substantially annular spring member is disposed outside a clutch force bar surrounding a press plate, and the spring plate is formed by the spring member.
• the spring member is constituted by a diaphragm spring that exerts a spring force in a direction opposite to the pres- sure plate.
• the outer periphery of the diaphragm spring is supported by the clutch cover to form a fulcrum for receiving the spring reaction force of the diaphragm spring.
• a lever for spring force booster which is pivotally supported by the clutch cover with the inner position in the radial direction from the spring force transmitting portion of the shearing center as the center of rotation, is arranged in the radial direction.
• the radially inward spring force acting point of the lever is provided radially inward from the fulcrum of the diaphragm spring, and the radially outward spring force acting point of the lever is defined.
• the distance between the center of rotation of the lever and the point of application of the outer spring force is equal to the distance between the center of rotation and the inner side spring. It is characterized in that it is set at a position that is shorter than the distance from the point of action, and that the spring force of the diaphragm spring is boosted with the lever. This is a clutch cover assembly.
• the lever only needs to transmit the spring force of the diaphragm spring to the pres- sure plate while boosting it. And the length in the axial direction is short.
• FIG. 1 is a longitudinal sectional partial view of the clutch of the first embodiment employing the present invention
• FIG. 2 is a longitudinal sectional partial view of the second embodiment
• FIG. 2a is a section a of FIG.
• FIG. 2b is an enlarged view of FIG. 2
• FIG. 3b is a longitudinal sectional view showing a conventional example.
• FIG. 1 which is a longitudinal sectional view of a clutch for a large vehicle adopting the present invention
• portions denoted by the same reference numerals as those in FIG. 3 indicate the same or corresponding portions.
• a substantially annular pres- sure plate 12 continuous over the entire circumference with the center line 0 as a center is a press-type clutch force. It is surrounded by the no. 16 and is connected to the flywheel 10 at the outer periphery of the clutch cover 16.
• the clutch force bar 16 is also formed in a substantially annular shape that is continuous over the entire circumference.
• a diaphragm spring 30 is arranged, and the diaphragm spring 30 is disposed.
• the pin 32 is fitted into the notch 31 radially extending from the inner periphery of the ring 30 to stop the diaphragm spring 30 from rotating.
• Pin 32 is fixed to the inner periphery of the clutch force bar .16-.
• the outer periphery of the diaphragm spring 30 ⁇ 3 3 is the inclination of the clamp 16 It is in pressure contact with the slope 34 over the entire circumference, so that the reaction force Q of the diaphragm spring 30 is received by the slope 34.
• the inclined surface 34 is formed as a conical surface that is inclined forward as it approaches radially inward at the radially intermediate portion of the clutch cover 16.
• the inner peripheral part 35 of the diaphragm spring 30 is pressed against the lens bearing 24 (FIG. 3), and the inner peripheral part is pressed.
• a well-known i-type is used in which the spring force P of the diaphragm spring 30 is eliminated by pushing 3 5 forward to the position of 2 4 a.
• levers 40 are arranged at equal intervals in the circumferential direction of the clutch cover 16, and the lever 40 is freely rotatable about the shaft 41. It is supported by a shaft.
• the shaft 41 extending in a direction perpendicular to the plane of the paper of FIG. 1 is supported by two lip portions 42 at both ends. That is, one end of the shaft 41 is supported by a lip portion 42 shown in the figure, and the other end of the shaft 41 is formed by a lip portion 42 ( (Not shown).
• the lip portion 42 is formed by cutting and raising a part of the clutch cover 16.
• the clip cover 16 has a window hole.
• An inner protrusion 44 is formed at the radially inner periphery of the lever 40, that is, at the upper end in FIG. Reference numeral 4 4 is in pressure contact with the diaphragm spring 30.
• An outer protrusion 46 is formed at the lower end of the lever 40, and the outer protrusion 46 is pressed against the film land portion 45 of the press plate 12. are doing.
• the distance B from the center 01 to the outer protrusion 46 is set to be much shorter than the distance A from the center 01 of the shaft 41 to the inner protrusion 44.
• the lever ratio of 0 has been increased. Accordingly, the spring force P of the diaphragm spring 30 acting on the inner protrusions 44 is boosted by the lever ratio A: B, and the spring force W from the outer protrusions 46. Is transmitted to the fork land section 45.
• a distance d is provided between the outer periphery ⁇ 33 and the inner protrusion 44, and the effective radius of the diaphragm spring 30 is c.
• One end of the strap plate 50 which extends in the circumferential direction of the clutch, that is, in the direction perpendicular to the plane of the paper, is re-mounted on the outer periphery of the push plate 12.
• the other end of the strap plate 50 is fixed to the clamp plate 16.
• the inner peripheral portion 35 of the diaphragm spring 30 becomes When pushed forward, the spring force P of the diaphragm spring 30 is no longer generated, and the diaphragm spring 30 has an inner projection 4 4. Leave. In this state, naturally, the spring force W transmitted to the file land 45 also disappears, and the clutch disk 14 is moved to the flywheel 1. Pressing force in the 0 direction is not applied to the press-fit force of the plate 1--2. It is pulled to. Therefore, the clutch disk 14 is sandwiched between the flywheel 10 and the press plate 12. The connection is released.
• the diaphragm spring 30 Since the diaphragm spring 30 is located outside the clutch cover 16, the diaphragm spring 30 has a relatively low temperature outside air. It is hard to be affected by heat when cooled.
• the outer peripheral edge 33 of the diaphragm spring 30 is supported by the inclined surface 34, and the third inner peripheral edge of the clutch cover 16 supports the reaction force Q.
• the clutch force Since the support point of the diaphragm spring 30 moves outward in the radial direction of the bar 16, the plate fixed to the flywheel 10 on the outer periphery is moved. The amount of deflection due to the reaction force Q of the shear rate 12 is reduced. As a result, the amount of forward movement of the inner protrusion 44 during the clutch release is increased as compared with the conventional case, and the so-called clutch cutting efficiency (release effect) is increased. Rate) is improved.
• the lever 40 is not directly rotated by the bearing bearing 24 as in the conventional case, but rather is a fan-shaped spring that uses the spring force of the diaphragm spring 30. Since it only needs to be transmitted to the Ramland part 45, the lever ratio of A: B is large. Therefore, a large spring force W is generated by a small spring force P. Also, the release load of the release bearing 24, that is, the depression force of the clutch pedal is light.
• the axial thickness of the lever 40 is reduced, and the diaphragm spring 30 is attached to the inclined surface 34 of the clutch cover 16 inclined forward. Since the outer peripheral edge 33 of the clutch is pressed, the axial dimension of the entire clutch is reduced, which is compact.
• FIG. 2 shows a second embodiment of the automotive clutch according to the present invention, in which the diaphragm spring 30 is stopped by a bracket 60.
• the bracket 60 is an annular member that is continuous over the entire circumference of the clutch, and has an annular protrusion 62 that presses against the diaphragm spring 30.
• the claw 64 protrudes at a position corresponding to the notch 31.
• a film land part 45 to which the outer protrusion 46 of the lever 40 is pressed against is shown.
• a spacer 66 may be interposed on the end surface of the outer protrusion 46 so that the height of the outer protrusion 46 is adjusted by the thickness of the spacer 66.
• Fig. 2b which is an enlarged view of a part b in Fig. 2, the entire circumference is provided between the outer peripheral edge 33 of the diaphragm spring 30 and the inclined surface 34.
• a continuous ring 70 may be interposed across the entire length.
• the diaphragm spring that exerts the spring force P in the direction opposite to the pres- sure plate.
• the spring member is composed of the diaphragm 30, and the outer periphery of the diaphragm spring 30 is supported by the clutch cover 1, and the diaphragm spring is formed.
• the fulcrum for example, the outer peripheral edge 33
• the spring force transmitting portion for example, the fan
• Lever section 45 Lever for spring force booster 40 supported on clutch cover 16 with radially inward orientation as center of rotation Are arranged in the radial direction, and the radially inward spring force application point (for example, the inner projection 44) of the lever 40 is connected to the outer peripheral edge 3 of the diaphragm spring 30.
• Three Ri is provided radially inward, a radius of lever one 4 0
• the distance B between the center of rotation 01 of the lever 40 and the point of application of the outward spring force is defined by the point of application of the outward spring force (the outer protrusion 46) in the direction.
• the diaphragm spring 30 Since the diaphragm spring 30 is located outside the clutch cover 16, the diaphragm spring 30 has a relatively low temperature. It is cooled by the outside air and becomes less affected by heat, and the life of the diaphragm spring 30 can be extended.
• the outer periphery ⁇ 33 of the diaphragm spring 30 is supported by the inclined surface 34, and the reaction force Q is supported by the innermost periphery of the clutch cover 16.
• the support point of the diaphragm spring 30 moves outward in the radial direction of the clutch spring 16, so that the flywheel
• the bending amount due to the reaction force Q of the fixed pres- sure plate 12 can be reduced. Therefore, the amount of forward movement of the inner protrusion 4 during the clutch release is greater than in the conventional case, and the so-called clutch cutting efficiency (release efficiency) is reduced. improves.
• the spring 40 uses the spring force of the diaphragm spring 30 as a fan. Since it is only necessary to transmit the signal to the drum land section 45, the lever ratio of A: B can be increased. . Accordingly, a large spring force w can be generated with a small spring force P, and the release load of the release bearing 24, that is, the depression force of the clutch pedal is also reduced. it can .
• the inner projection 44 of the lever 40 has a reduced thickness in the axial direction, and it has a frontward force and is inclined to the inclined slope 34 of the clutch cover 16 that is inclined. Since the outer peripheral edge 33 of the spring 30 is pressed, the axial dimension of the entire clutch can be reduced, and the compactness can be achieved.

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

Priority Applications (1)

Applications Claiming Priority (2)

Publications (1)

Family

ID=18033057

Family Applications (1)

Country Status (2)

Citations (2)

• 1986
  • 1986-12-29 JP JP61312757A patent/JPS63172024A/ja active Granted
• 1987
  • 1987-12-14 WO PCT/JP1987/000978 patent/WO1993013327A1/ja unknown

Patent Citations (2)

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