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
  • F16D13/583—Diaphragm-springs, e.g. Belleville
• • 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
  • F16D25/00—Fluid-actuated clutches
  • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
  • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
  • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
  • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
  • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae

Definitions

• the present invention relates to a disc spring used for absorbing a shock generated when a clutch of a multi-plate clutch mechanism of a transport machine is engaged, and more particularly to a disc spring provided with teeth for preventing relative rotation with respect to a clutch drum.
• a disc spring used for absorbing a shock generated when a clutch of a multi-plate clutch mechanism of a transport machine is engaged, and more particularly to a disc spring provided with teeth for preventing relative rotation with respect to a clutch drum.
• FIG. 7 is an enlarged side sectional view showing a configuration of a multi-plate clutch mechanism 100 to which a conventional disc spring 200 is applied.
• the multi-plate clutch mechanism 100 includes a clutch drum 101 having a substantially bottomed cylindrical shape, and a plurality of spline grooves 101A extending in the axial direction are formed in the circumferential direction on the inner peripheral surface thereof.
• a cylindrical clutch hub 102 Inside the clutch drum 101 is provided a cylindrical clutch hub 102 whose rotational axis position coincides with it, and on its outer peripheral surface, a plurality of spline grooves 102A extending in the axial direction are formed in the circumferential direction! / Speak.
• a driven plate 103 that fits in the spline groove 101A of the clutch drum 101 and a drive plate 104 that fits in the spline groove 102A of the clutch hub 102 have an axis line They are alternately arranged at a predetermined interval so as to be movable in the direction.
• a piston 105 is provided on the bottom surface side of the clutch drum 101 so as to be movable in the axial direction.
• a hydraulic chamber 106 is formed between the piston 105 and the clutch drum 101.
• a disc spring 200 having a circular disc shape with a hole formed in the center is provided between the driven plate 103 on the bottom side of the clutch drum 101 and the piston 105.
• the disc spring 200 is arranged such that the outer peripheral edge surface is supported by the driven plate 103 and the inner peripheral edge back surface is supported by the piston 105.
• the piston 105 driven by the hydraulic pressure causes the bottom surface of the clutch drum 101 to pass through the disc spring 200. Press the driven plate 103 on the side. Then, the driven plate 103 on the bottom side moves to the opening side of the clutch drum 101, the friction surfaces of the driven plate 103 and the drive plate 104 facing each other engage, and the clutch is engaged. At this time, the disc spring 200 absorbs a shock generated when the clutch is engaged by elastically deforming so as to be substantially flat from the disc shape.
• the disc spring 200 since the disc spring 200 has a circular shape, the disc spring 200 easily rotates relative to the clutch drum 101 when the clutch mechanism 100 rotates. For this reason, there is a problem that the disc spring 200 frequently collides with the inner wall of the clutch drum 101, and as a result, the inner wall of the clutch drum 101 is damaged.
• a plurality of teeth 311 are formed on the outer periphery of a circular dish-shaped main body 310 having a hole 310A formed at the center.
• Disc springs 300 have been proposed (for example, Patent Document 1 and Patent Document 2).
• the main body 310 is installed inside the clutch drum 101 so that the teeth 311 of the disc spring 311 are engaged with the spline groove 101A on the inner peripheral surface of the clutch drum 101. Relative rotation can be prevented.
• Patent Document 1 Japanese Patent Application Laid-Open No. 2001-295860
• Patent Document 2 JP-A-9-329155
• the side part of the tooth 311 Since the length L of the straight portion 31 IB is reduced, the fitting area force S of the tooth 311 with the spline groove 101A is reduced. For this reason, the contact surface pressure between the tooth 311 and the spline groove 101A increases, and wear of the spline groove 101A by the tooth 311 increases.
• the disc spring 300 since the disc spring 300 is required to have high durability in order to cope with the increase in guaranteed mileage of automobiles in recent years, the above problems are serious.
• the present invention provides a disc spring that can reduce the generated stress at the root portion of the tooth when the clutch is engaged, as well as the wear of the spline groove due to the tooth.
• the purpose is that.
• a disc spring according to the present invention is a disc spring disposed between a second member and a third member provided to be movable in the axial direction inside a cylindrical first member, and is circular.
• the teeth that fit into the grooves formed on the inner peripheral surface of the first member are formed on the outer peripheral portion of the dish-shaped main body so as to protrude radially outward. It is characterized in that a stress relaxation part is formed by cutting out the root of a tooth in a substantially arc shape in at least one radial direction.
• the root portion of the tooth is provided in the radial direction because the root portion of the tooth is provided with a stress relief portion formed by cutting out the root portion of the tooth in a substantially arc shape in at least one of the circumferential direction and the radial direction. It can have a large radius of curvature R without protruding outward.
• FIG. 6 is a diagram for explaining the relationship between the magnitude of the radius of curvature R of the root portion of the tooth and the stress generated therewith regarding various forms of the disc spring of the present invention, and curve (a) shows the conventional disc.
• the curve (b) represents the characteristics of the spring (hereinafter referred to as a disc spring a), and the curve (b) represents the disc spring of the present invention (hereinafter referred to as a disc spring b) having a stress relief portion formed by cutting out the root of the tooth in an arc shape in the radial direction.
• the disc spring b of the present invention includes a stress relief portion formed by a notch V in the radial direction in the root portion of the tooth in the radial direction.
• a notch V in the radial direction in the root portion of the tooth in the radial direction.
• the disc spring c of the present invention includes a stress relaxation portion formed by cutting out the root portion of the tooth in a substantially arc shape in the circumferential direction. Therefore, the radius of curvature of the root portion of the tooth is higher than that of the conventional disc spring a. Even if R is set large, interference between the teeth and the spline groove does not occur as in the case of the disc spring b of the present invention. Therefore, in the disc spring b of the present invention, the radius of curvature R of the root portion of the tooth can be set to a large value as indicated by the R point as compared with the conventional disc spring a.
• the generated stress is remarkably small when the root portion of the tooth has the same radius of curvature R as the disc spring b of the present invention.
• the stress generated at the root of the teeth when the clutch is engaged can be greatly reduced.
• the disc spring b of the present invention since the straight portion of the side surface portion of the tooth is longer than the disc spring c of the present invention, the fitting area with the tooth spline groove is increased, and the tooth and spline groove The contact surface pressure can be reduced. Thereby, compared to the disc spring c, it is possible to further reduce the wear of the spline groove due to the teeth when the clutch drum rotates.
• the stress relief portion has a shape in which the stress relief portions of the disc spring b and the disc spring c are combined. Therefore, as shown by the curve (d), the disc spring b And approximately the characteristics of the disc spring c can be obtained.
• the disc spring d of the present invention can have a larger value of the radius of curvature R as shown by the point S as compared with the conventional disc spring a, so that the root portion of the tooth can be applied when the clutch is fastened. The generated stress can be reduced.
• the stress relief part of the above-mentioned disc spring b has a first arc-shaped arc part in which one end part is smoothly connected to the outer peripheral part of the main body and one end part smoothly in the other end part of the first arc part. It can have a circular arc-shaped second circular arc portion that is connected and smoothly connected to the boundary with the side surface portion of the tooth at the other end portion.
• the first arc portion can have a larger curvature radius R than the second arc portion.
• the boundary between the first arc portion, the stress relaxation portion, and the tooth side portion connected to the outer peripheral portion of the main body by the second arc portion having a smaller radius of curvature R than the first arc portion. are smoothly connected to each other, so that the straight portion of the side surface portion of the tooth can be lengthened as compared with the case where the stress relaxation portion is constituted by one arc portion. Therefore, it is possible to further reduce the wear of the spline groove due to the teeth when the clutch drum rotates.
• the above-mentioned stress relief portion of the disc spring c has an arc-shaped third arc portion in which one end portion is smoothly connected to the outer peripheral portion of the main body, and one end portion on the other end portion of the third arc portion.
• a straight portion extending smoothly inward in the radial direction and one arc-shaped first end smoothly connected to the other end of the straight portion and the other end smoothly connected to the side surface of the tooth.
• the root portion of the tooth is provided with a stress relaxation portion.
• the stress relief part causes The generated stress can be reduced. Even when the shape of the spline groove of the clutch drum is sharp, interference between the teeth and the spline grooves during rotation of the clutch drum can be prevented, thus reducing wear of the spline grooves by the teeth. Effects such as
• FIG. 1 is a diagram showing a configuration of a disc spring according to a first embodiment of the present invention, in which (A) is a plan view, (B) is a side sectional view taken along line BB in (A), (C) is a partially enlarged view of (B).
• FIG. 2 is a diagram showing a configuration of a clutch mechanism to which the disc spring of FIG. 1 is applied, (A) is an enlarged side sectional view, and (B) is an exploded view.
• FIG. 3 is a partially enlarged view showing the configuration of a disc spring according to a second embodiment of the present invention.
• FIG. 4 is a partially enlarged view showing the configuration of a disc spring according to a third embodiment of the present invention.
• FIG. 5 is a partially enlarged view showing the configuration of a disc spring according to a fourth embodiment of the present invention.
• FIG. 6 is a diagram for explaining the relationship between the magnitude of the radius of curvature R of the root portion of the tooth and the stress generated therewith regarding various forms of the disc spring of the present invention.
• FIG. 7 is a side sectional view showing a configuration of a multi-plate clutch mechanism to which a conventional disc spring is applied.
• FIG. 8 A diagram showing the configuration of another conventional disc spring, (A) is a plan view, (B) is a side sectional view taken along line B-B in (A), and (C) is a diagram in (A). It is a partial enlarged view.
• FIG. 1 is a diagram showing a configuration of a disc spring 1 according to a first embodiment of the present invention, where (A) is a plan view, (B) is a side cross-sectional view taken along line BB in (A), (C ) Is a partially enlarged view of (A).
• the disc spring 1 includes a main body 10 having a circular dish shape, and a circular hole 10A is formed at the center of the main body 10.
• a plurality of (for example, six) teeth 11 having a substantially rectangular shape and projecting radially outward are formed at equal intervals in the circumferential direction on the outer peripheral portion of the main body 10.
• the tooth 11 when the tooth 11 is applied to the clutch mechanism 100 described below, the tooth 11 has a function of preventing the disc spring 1 from rotating relative to the clutch drum 101.
• the teeth to which the present invention is applied are not limited to the teeth 11 shown in FIG. 1, but can be applied to teeth of various shapes.
• the present invention can be applied to a tooth having a shape extending along the outer peripheral surface of the main body 10 without being bent with respect to the outer peripheral surface of the main body 10.
• the number of teeth 11 is set to 6. The number of teeth is not limited to this, and the number can be set arbitrarily.
• a stress relaxation portion 12 is formed by being cut out in a substantially arc shape in the circumferential direction.
• the stress relaxation portion 12 has a function of relaxing stress concentration generated at the root portion of the tooth 11 when the clutch is engaged.
• the stress relieving portion 12 has arcuate arc portions 12A to 12C in which the outer peripheral portion side force of the main body 10 is also formed in order toward the side surface portion side of the tooth 11.
• One end of the arc portion 12A (first arc portion) is smoothly connected to the outer peripheral portion of the main body 10.
• One end of the arc portion 12B (second arc portion) is smoothly connected to the other end portion of the arc portion 12A.
• the arc portion 12C is smoothly connected to the other end portion of the arc portion 12B, and the other end portion of the arc portion 12C is smoothly connected to the side surface portion of the tooth 11.
• the arc portion 12A has a radius of curvature R that is about twice as large as the arc portion 12B, for example.
• FIG. 2 shows the configuration of the clutch mechanism 100, where (A) is an enlarged side sectional view and (B) is an exploded view. In FIG. 2B, illustration of the clutch hub 102 is omitted.
• Clutch mechanism 100 is a wet multi-plate clutch used in, for example, an AT car of an automobile.
• the clutch mechanism 100 includes a clutch drum 101 (first member) having a substantially bottomed cylindrical shape.
• a plurality of spline grooves 101A extending in the axial direction are formed at equal intervals in the circumferential direction on the inner peripheral surface.
• a cylindrical clutch hub 102 whose rotational axis line coincides with it is provided, and on its outer peripheral surface, a plurality of spline grooves 102A extending in the axial direction are equally spaced in the circumferential direction. Is formed.
• a disk-shaped driven plate 103 (second member) having a circular hole formed at the center thereof and a drive plate 104 are spaced apart by a predetermined distance. Alternatingly arranged.
• the driven plate 103 a plurality of teeth are formed on the outer peripheral edge at equal intervals in the circumferential direction, and are fitted into these tooth force S spline grooves 101A.
• the driven plate 103 cannot rotate relative to the clutch drum 101 but can move in the axial direction.
• the drive plate 104 a plurality of teeth are formed on the inner peripheral edge at equal intervals in the circumferential direction, and these teeth are fitted in the spline groove 102A. As a result, the drive plate 104 cannot move relative to the clutch hub 102 but can move in the axial direction.
• a piston 105 (third member) is arranged on the bottom surface side of the clutch drum 101 so as to be movable in the axial direction. Between the bottom surface of the clutch drum 101 and the piston 105, a hydraulic chamber 106 in which hydraulic oil is supplied is formed. The piston 105 is driven in the axial direction by the working oil supplied to the hydraulic chamber 106. One end of a return spring 107 that is expanded and contracted by pressure applied thereto is fixed to the opening side surface of the piston 105. The other end of the return spring 107 is fixed to a spring retainer 108 provided on the clutch drum 101. The return spring 107 urges the piston 105 toward the bottom surface of the clutch drum 101.
• the disc spring 1 is disposed between the driven plate 103 and the piston 105 on the bottom side of the clutch drum 101.
• the teeth 11 are spline-fitted into the spline grooves 101A
• the outer peripheral surface of the main body 10 is supported by the driven plate 103
• the inner peripheral edge of the main body 10 is supported.
• the rear surface of the part is arranged so as to be supported by the piston 105.
• the disc spring 1 can move in the axial direction, V, which cannot rotate relative to the clutch drum 101.
• a driven plate 103 and a drive plate 104 are arranged on the axis line.
• a retaining plate 109 for restricting movement in the direction by a predetermined amount or more is arranged.
• a plurality of teeth are formed on the outer peripheral edge at equal intervals in the circumferential direction, and these teeth are fitted in the spline groove 101A.
• the retaining plate 109 cannot move relative to the clutch drum 101 but can move in the axial direction.
• a snap ring 110 is arranged to prevent the retaining plate 109 from coming off. The snap ring 110 is locked in a ring groove formed at the opening side end of the clutch drum 101.
• the disc spring 1 absorbs a shock generated when the clutch is fastened by elastically deforming so as to be substantially flat from the disc shape.
• the stress generated in the root portion of the tooth 11 when the disc spring 1 is elastically deformed is reduced by the stress relaxation portion 12.
• the stress relieving portion 12 does not protrude outward in the radial direction, interference between the teeth 11 and the spline groove 101A when the clutch drum 101 rotates is prevented.
• the root portion of the tooth 11 is cut out in a substantially arc shape in the circumferential direction.
• the root portion of the tooth 11 can have a large radius of curvature R without protruding outward in the radial direction.
• the stress relaxing portion 12 reduces the stress generated at the root of the tooth 11 when the clutch is engaged. can do. Even if the shape of the spline groove 101A of the clutch drum 101 is sharp, the interference between the teeth 11 and the spline groove 101A during rotation of the clutch drum 101 can be prevented. Wear can be reduced. Therefore, since it can have high durability, it can cope with an increase in the guaranteed driving distance of the automobile.
• the stress relaxation portion 12 is connected to the outer peripheral portion of the main body 10 by an arc portion 12B having a smaller radius of curvature R than the arc portion 12A, and the arc portion 12A, the stress relaxation portion 12, and the side surfaces of the teeth.
• the straight portion of the side surface of the tooth 11 can be made longer than in the case where the stress relaxation portion is composed of one arc portion. Therefore, wear of the spline groove 101A due to the teeth 11 when the clutch drum 101 is rotated can be further reduced.
• FIG. 3 shows a configuration of the disc spring 2 according to the second embodiment of the present invention, and is a partially enlarged view including the teeth 11 of the disc spring 2.
• the same components as those in the first embodiment are denoted by the same reference numerals, and descriptions of the configurations and operations thereof are omitted.
• FIG. 2 instead of forming the stress relaxation portion 12 by cutting the root portion of the tooth 11 in a substantially arc shape in the circumferential direction as in the first embodiment, FIG. As shown in FIG. 2, the stress relaxation portion 22 is formed by cutting out the root portion of the tooth 11 in the radial direction in a substantially arc shape.
• the stress relieving portion 22 has arc portions 22A and 22B having an arc shape. One end of the arc portion 22A is smoothly connected to the outer peripheral portion of the main body 10. One end portion of the arc portion 22B is smoothly connected to the other end portion of the arc portion 22A, and the other end portion is smoothly connected to the side surface portion of the tooth 11.
• the stress relaxation part 22 is formed by notching the root part of the tooth 11 in the radial direction, the straight part of the side part of the tooth 11 can be lengthened. But Therefore, compared to the first embodiment, the wear of the spline groove 101A due to the teeth 11 can be further reduced.
• FIG. 4 shows a configuration of the disc spring 3 according to the third embodiment of the present invention, and is a partially enlarged view including the teeth 11 of the disc spring 3.
• a stress relaxation portion 32 having an arc portion 32A (third arc portion), a straight portion 32B, and an arc portion 32C (fourth arc portion) is formed.
• the arc portion 32A, the straight portion 32B, and the arc portion 32C are formed in order in the direction toward the side surface portion of the outer peripheral side force tooth 11 of the main body 10.
• the arc portion 32 A has an arc shape, and one end thereof is smoothly connected to the outer peripheral portion of the main body 10.
• the straight line portion 32B is linear in cross section and extends substantially inward in the radial direction. One end portion of the straight portion 32B is smoothly connected to the other end portion of the arc portion 32A. One end portion of the arc portion 32C is smoothly connected to the other end portion of the linear portion 32B, and the other end portion of the arc portion 32C is smoothly connected to the side surface portion of the tooth 11.
• the linear portion 32B is formed between the circular arc portion 32A and the circular arc portion 32C, compared with the second embodiment, in the press work when manufacturing the disc spring 3, the die The durability of the components corresponding to the root of the tooth 11 can be improved.
• FIG. 5 shows a configuration of the disc spring 4 according to the fourth embodiment of the present invention, and is a partially enlarged view including the teeth 11 of the disc spring 4.
• the arc portion 42A having substantially the same shape as the stress relaxation portion 22 of the second embodiment and the arc portion 42A are smoothly connected.
• a stress relaxation portion 42 having an arc portion 42B having a shape substantially equivalent to the stress relaxation portion 12 of the first embodiment is formed at the root portion of the tooth 11.
• substantially intermediate characteristics between the disc spring 1 of the first embodiment and the disc spring 2 of the second embodiment can be obtained.
• the present invention has been described with reference to the first to fourth embodiments, the present invention is not limited to the first to fourth embodiments, and various modifications are possible.
• the disc spring of the present invention is applied to a wet multi-plate clutch used in an AT car of an automobile, but the present invention is not limited to this.
• the disc spring of the present invention can be applied to a multi-plate clutch mechanism of a transport machine such as a construction machine or a motorcycle.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Mechanical Operated Clutches (AREA)
• Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
• Springs (AREA)

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Publications (1)

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Citations (4)

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• 2005
  • 2005-02-10 JP JP2005035247A patent/JP4917754B2/ja not_active Expired - Fee Related
• 2006
  • 2006-02-10 WO PCT/JP2006/302348 patent/WO2006085610A1/ja not_active Ceased
  • 2006-02-10 US US11/883,948 patent/US8091873B2/en not_active Expired - Fee Related
  • 2006-02-10 DE DE602006021147T patent/DE602006021147D1/de not_active Expired - Lifetime
  • 2006-02-10 CN CN2006800046210A patent/CN101115936B/zh not_active Expired - Fee Related
  • 2006-02-10 EP EP06713491A patent/EP1852622B1/en not_active Ceased
  • 2006-02-10 EP EP06713494.0A patent/EP1852623B1/en not_active Ceased
  • 2006-02-10 US US11/883,875 patent/US7971690B2/en not_active Expired - Fee Related
  • 2006-02-10 CN CN2006800044554A patent/CN101115935B/zh not_active Expired - Fee Related
  • 2006-02-10 WO PCT/JP2006/302351 patent/WO2006085613A1/ja not_active Ceased

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