[go: up one dir, main page]

WO1989008792A1 - Disque amortisseur - Google Patents

Disque amortisseur Download PDF

Info

Publication number
WO1989008792A1
WO1989008792A1 PCT/JP1989/000254 JP8900254W WO8908792A1 WO 1989008792 A1 WO1989008792 A1 WO 1989008792A1 JP 8900254 W JP8900254 W JP 8900254W WO 8908792 A1 WO8908792 A1 WO 8908792A1
Authority
WO
WIPO (PCT)
Prior art keywords
plate
side plate
torsion spring
window hole
output
Prior art date
Application number
PCT/JP1989/000254
Other languages
English (en)
Japanese (ja)
Inventor
Yasuyuki Hashimoto
Takuji Yoshimura
Syogo Ohga
Original Assignee
Kabushiki Kaisha Daikin Seisakusho
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP5582588A external-priority patent/JPH01229123A/ja
Priority claimed from JP3141988U external-priority patent/JPH01135233U/ja
Priority claimed from JP1988033461U external-priority patent/JPH0631228Y2/ja
Priority claimed from JP1988038836U external-priority patent/JPH0543294Y2/ja
Priority claimed from JP8477788U external-priority patent/JPH0640989Y2/ja
Application filed by Kabushiki Kaisha Daikin Seisakusho filed Critical Kabushiki Kaisha Daikin Seisakusho
Priority to DE19893990204 priority Critical patent/DE3990204T1/de
Priority to DE3990204A priority patent/DE3990204C2/de
Publication of WO1989008792A1 publication Critical patent/WO1989008792A1/fr

Links

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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/1232—Wound springs characterised by the spring mounting
    • F16F15/12346—Set of springs, e.g. springs within springs
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/1232—Wound springs characterised by the spring mounting
    • F16F15/1234—Additional guiding means for springs, e.g. for support along the body of springs that extend circumferentially over a significant length
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/1238—Wound springs with pre-damper, i.e. additional set of springs between flange of main damper and hub

Definitions

  • the present invention relates to a damper disk.
  • the object of claim 1 of the present application is to separate the output side plate inside and outside, thereby ensuring low rigidity and low hysteresis torque at the time of idling to reduce idle noise, and to further reduce the noise.
  • claims 2, 3, 4, and 5 provide the friction spring between the float body and the window hole as small as possible when the torsion springs are arranged in series via the float. It is also intended to do so.
  • the output side plate is separated into the flange of the hub and the intermediate plate outside the hub, and By making one plate with two plate members, manufacturing can be facilitated.
  • the car-side plate is separated into a flange integral with the spline hub and an intermediate plate on the outer periphery thereof, and the intermediate plate is arranged between a pair of input-side side plates.
  • the intermediate plate and the intermediate plate are brought into contact via the second-stage friction member, and the intermediate plate and the flange of the output side hub are brought into contact via the first-stage friction member having a low coefficient of friction.
  • a first-stage torsion spring having a small spring constant is disposed in the 0th window and the corresponding 1st window of the intermediate plate, and the flange and the intermediate plate are connected via the first-stage torsion spring.
  • the second stage torsion spring 5 with a large spring constant is connected to the second window of the intermediate plate and the window of the side plate corresponding to the second window to transmit torque.
  • Place at least two in series with the hole ⁇ A circumferentially movable float body is interposed between the two second-stage torsion springs arranged in a row, and the intermediate plate and side plate are interposed via the second-stage torsion spring. Are connected so that torque can be transmitted.
  • the hub and intermediate plate are relatively twisted to compress the first-stage torsion spring having a small spring constant, and a low-hysteresis torque is generated by the first-stage friction member. This can reduce idle noise.
  • the second-stage torsion spring At low speed, the second-stage torsion spring is compressed, and at the same time, a relatively high hysteresis torque is generated by the second-stage friction member.
  • the second stage torsion spring is connected in series via a float Since it is arranged at a relatively low torsional stiffness, it can cover a wide range of torsional angles, thereby reducing muffled noise during low-speed running.
  • a tongue spring arrangement window hole is formed in each of the pair of input side plates and the output side plate between the side plates, and the same window hole is formed.
  • At least two torsion springs are arranged in series, and the torsion spring connects the side plate and the output side plate so that torque can be transmitted.
  • a float body movable in the circumferential direction is interposed between the torsion springs, and the float body is formed of a light plastic material with a low friction coefficient.
  • the two torsion springs in series are compressed, and at the same time the body between the torsion springs moves in the circumferential direction. Fretting hardly occurs even if it touches the radially outer edge of the float.c In addition, since it is light, the centrifugal force at the time of rotation is also small, and it is not unnecessarily necessary depending on the movement of the float. There is no increase in stable hysteresis torque.
  • a plurality of torsion spring arrangement windows are formed in a pair of input side plates and an output plate between the side plates, respectively, and a radius of the output plate is formed.
  • the outer peripheral edge in the direction is formed so that the radially outer edge of the window hole is closed, and at least two torsion springs are connected in series to each window hole in the output plate.
  • the torsion spring connects the side plate and the output side plate so that torque can be transmitted, and a circumference is provided between two serial torsion springs in each window hole.
  • the floats that can move in the directions are interposed, and the side surfaces of the floats are integrally connected by an annular connector.
  • a plurality of transmission spring arrangement window holes are formed in a pair of input side plates and an output plate between the side plates, respectively.
  • the outer peripheral edge in the radial direction is formed in an annular shape so that the radially outer end of the window hole is closed, and at least two transition springs are provided in each window hole of the output plate. It is arranged in series, and the side plate and output side plate are connected so that torque can be transmitted by the torsion spring, and moves in the direction of the circle between two series of torsion springs in each window hole.
  • a guide plate is fixed on the rain side surface of each float body in the axial direction, with a possible float body interposed, and an annular connecting body that connects between the guide plates is provided at the inner peripheral end of each guide plate. They are integrally formed.
  • a plurality of window holes for torsion spring arrangement are formed in a pair of input side plates and an output plate between the side plates, respectively, and each window of the output side plate is formed.
  • At least two springs are arranged in series, and the side spring and the output plate are connected so that torque can be transmitted by the torsion springs.
  • a float body that can move in the circumferential direction is interposed between the toe-shock springs, and each float body is pinned to an annular connecting body that is located radially inward from the float body. 0 is swingably connected via
  • the flange of the hub and the intermediate annular body are connected so that torque can be transmitted through the torsion spring, and torque is transmitted between the intermediate plate and the side plate via the second-stage torsion spring with a large spring constant.
  • a pair of left and right thick annular intermediate plate members are superimposed and joined by rivets, and a second stage torsion is applied to the outer peripheral portion of the plate between the sub-plates.
  • Window for the spring Forming a first-stage torsion spring receiving and expanding portion at the inner peripheral end of the intermediate plate, and a torque-connecting string consisting of concave and convex portions between the flange of the hap and the flange of the hap.
  • expanding part Friction members are arranged between the shaft and the side plate, and between the expanded portion and the flange of the hub.
  • Fig. 1 is a side view of a damper disk to which claims 1, 2 and 6 of the present application are applied, with a part cut away.
  • Fig. 2 is a cross-sectional view taken along the line ⁇ in Fig. 1;
  • Fig. 4 is a cross-sectional view of III-III, Fig. 4 is an enlarged side view of the float body,
  • Fig. 5 is a V-V cross-sectional view of Fig. 4
  • Fig. 6 is a torsional characteristic diagram, and
  • Fig. 7 is claims 1 and 3.
  • Fig. 8 is a cross-sectional view of Fig. 7 with the ⁇ - ⁇ cross section,
  • Fig. 9 is a cross section of IX-K of Fig. 7, and Fig.
  • FIG. 10 is a book Side view of the damper disk to which claims 1 and 4 are applied, partially cut away
  • FIG. 11 is a sectional view taken along the line XI-XI of FIG. 10
  • FIG. Fig. 13 is a cross-sectional view of the applied damper disk, cut away as shown in Fig. 13.
  • Fig. 13 is a cross-sectional view of XBT-xm in Fig. 1, Fig. 15 shows another embodiment applying claim 1 It is a surface view.
  • FIG. 3 is a longitudinal sectional view (m-IE sectional view of FIG. 1) of a dambar disk to which claims 1, 2 and 6 of the present application are applied, and a pair of input side plates 1 are mutually connected. They are arranged at regular intervals in the axial direction and are connected to each other by rivets 2 at their outer peripheral ends.
  • the cushioning plate 4 is fixed to the outer edge of the side plate by the rivet 2 and the input cuffing 3 is fixed to both sides of the cushioning plate 4.
  • Pretzia I It is clamped between the plates and torque is input.
  • Output plates 6 and 11 are arranged between both side plates 1, and the output plates 6 and 11 are intermediate plates between the flange 11 integrated with the output hub 10 and the outer peripheral side.
  • the annular intermediate plate 6 is formed of a first pair of members, is formed to be thick, overlaps with each other, and is integrally connected by the rivet 7.
  • a plurality of enlarged portions 6a that open in the axial direction are formed at the inner peripheral end portion of the intermediate plate 6.
  • the flange 11 of the output side hub 10 is arranged in the enlarged portion 6a.
  • the output hub 10 is, for example, spline-fitted for output.
  • a second-stage friction member 13 having a large friction coefficient is disposed between the inner peripheral portion of the intermediate plate 6 and the inner peripheral portion of the side plate 1, and the inner peripheral portion of the intermediate plate 6 and the flange are disposed.
  • a first-stage friction member 12 having a small friction coefficient is arranged between the flanges 11.
  • a window hole (notch) 16 for the first-stage spring is formed in the flange 11, and a corresponding first window hole 17 is formed in the enlarged portion 6 a of the intermediate plate 6.
  • the first-stage torsion spring 21 having a small spring constant is disposed in the windows 16 and 17 so as to be freely compressible in the circumferential direction. That is, the first-stage torsion spring 21 comes into contact with the circumferential edge of the window hole 16 of the flange 11 via the end stoppers 22, and the spring receivers 22 are both axially And is in contact with the circumferential edge of the first window hole 17 of the plate 6.
  • FIG. 2 is a cross-sectional view of a portion different from that of FIG. 1 (a cross-sectional view taken along the line ⁇ in FIG. 1).
  • a hole 18 is formed, and a window hole 19 is formed in the side plate 1 corresponding to the second window hole 18.
  • a second-stage torsion spring 23 is disposed in the holes 18 and 19 so as to be freely compressible in the
  • three second window holes 18 are formed at equal intervals in the circumferential direction, and two two-stage tj torsion springs 23 are provided in one window hole 18.
  • the float bodies 25 are arranged in series in the circumferential direction, and are freely movable in the circular direction between the second-stage torsion springs 23 in one window hole 18.
  • the two-stage E1 torsion spring 23 is of a parent-child spring type, and has a child coil spring 27 inside.
  • the window holes 16 of the flange 11 are also formed in three places at intervals in the circumferential direction, and a recess 30 is formed in the portion between the window holes of the flange 11, while the intermediate plate 6 is formed.
  • a protrusion 32 protruding into the recess 30 is formed in the recess 30.
  • the circumferential gap dl between the recess 30 and the protrusion 32 regulates the range of the first-stage torsion angle.
  • Float body 25 is made of hard resin with low coefficient of friction, such as polyamide resin, and is light in weight, formed in a trapezoidal shape that becomes thinner toward the center of the clutch,
  • the outer peripheral end ⁇ 2 c is in contact with the radially outer edge 18 c of the second window hole 18 ⁇ on both axial sides of the float body 25, as shown in FIG.
  • the plate 35 is fixed by pins 36, and both outer and inner ends of the guide plate 35 in the radial direction both extend to both side portions of the intermediate plate 6, thereby Float body 25 is prevented from falling off in the axial direction.
  • the guide plate 35 is formed in a substantially inverted triangular shape 5 as shown in FIG. 4, and the spring receiving contact of the torsion spring is flush with the spring receiving surface M of the float body 25.
  • N Extending portions 35a extending in both circumferential directions are formed at radially outer ends of the guide plates 35, respectively.
  • As the material of the guide plate 35 for example, an iron plate is used, thereby improving the strength against the spring pressure.
  • Pin 36 is made of metal.
  • a concave portion is formed in the flange 11 of the hub 10 and a convex portion is formed in the intermediate plate 6, but the convex portion is formed in the flange 11.
  • a portion may be formed, and a recess may be formed in the intermediate plate 6.
  • the intermediate plate 6 and the side plate 1 are integrally twisted, for example, in the same direction as the rotation direction R with respect to the flange 11 in FIG. Compress 1
  • the first-stage friction member 12 between the intermediate plate 6 and the flange 11 in FIG. 2 is rubbed, so that a small hysteresis torque is generated.
  • the 2nd stage compression of the torsion spring 23 also moves the float body 25 in FIG. 1 in the circumferential direction, and the outer peripheral edge 25 c of the float body 25 in the radial direction and the outside of the window hole 18.
  • the side edge ⁇ 18 c rubs, but 0 Since the rotor body 25 itself is made of a polyamide resin having a low coefficient of friction, there is almost no fretting, and since it is light, there is little centrifugal force.
  • Fig. 6 shows a torsional characteristic diagram.Hysteresis torque is extremely small in the first-stage torsion angle range 0 to 01, and relatively large in the second-stage torsion angle range ⁇ ⁇ 1 to ⁇ . High hysteresis torque H is generated.
  • FIGS. 7 to 9 The embodiment shown in FIGS. 7 to 9 is a damper disk to which claims 1 and 3 are applied.
  • the three floats 25 are connected on both sides in the axial direction by a ring-shaped connector 37.
  • a pair of annular connecting bodies 37 are arranged on the outer sides in the free direction of both side plates 1, and a portion corresponding to the floating body 25 is located at the center in the axial direction. It is fixed to the side of the guide plate 35 using the rivet 36.
  • the annular connector 37 is made of, for example, an iron plate.
  • connecting body 37 is arranged on the side of the float body 25, it also serves as a protective cover for the second-stage torsion spring 23.
  • FIGS. 10 and 11 The embodiment shown in FIGS. 10 and 11 is a damper disk to which claims 1 and 4 are applied.
  • the three floats 25 are supported by guide plates 35, respectively, and the inner peripheral ends of the guide plates 35 are integrally connected by an annular connecting member 47.
  • the two connecting bodies 47 do not contact the force ⁇ disposed between the widened portion 6 a of the intermediate plate 65 and the side plate 1, and the plates 1 and 6.
  • Other structures are the same as those in FIGS. 1 to 5 of the first embodiment, and the same parts are denoted by the same reference numerals.
  • the float body 25 in FIG. 07 moves in the circumferential direction due to the compression of the second stage G-section 23, and the three float bodies 25 are annularly connected. Since they are integrally connected by the body 47, the float body 25 does not protrude outward in the radial direction. Therefore, there is no concern that the unnecessary and unstable hysteresis torque due to the friction between the radial outer edge 25a of the float body 25 and the peripheral edge 18a of the window hole 18 will increase. Since the connecting body 47 and each guide plate 35 are integrally formed, the number of parts And reduce weight.
  • FIGS. 12 to 14 is a damper disk to which claims 1 and 5 of the present application are applied.
  • the three floats 25 and the support plate 35 are movably connected to the annular connector 37 via pins 38.
  • the annular connector 37 is disposed radially inward of the float 25 and integrally has protruding pieces 37a protruding outward at three places of force.
  • a pin hole 3 is formed at the radially inner end of the cylindrical plate 25 and the servo plate 35 as shown in the lower half of FIG.
  • Pin 3 8 is ⁇ so the pin holes 3 9 such as float member 2 5 having a radius direction ye, c annular connecting the both end portions are fixed to the projecting piece 3 7 a of the annular body 3 7
  • the body 37 is made of, for example, an iron plate.
  • FIG. 15 shows a damper disk to which claim 1 is applied.
  • the hub 10 and the intermediate flange 41 have substantially the same width as the flange 11, and a pair of thin sub-plates fixed to both sides of the intermediate flange 41. It has 4 2.
  • Other structures are the same as in FIGS. 1 to 5.
  • the output side plate is separated into the flange 11 and the intermediate plate 6, so that low rigidity and low hysteresis torque characteristics can be obtained during riding.
  • the idling noise can be reduced, and two second-stage torsion springs 23 are arranged in series in the same window hole.
  • a wide screw angle can be taken when driving at low speed, and relatively small rigidity is sufficient. The torque can be secured and the muffled sound of low-speed running can be reduced.
  • the float body 25 interposed between the two torsion springs 23 is formed of a light plastic material having a low coefficient of friction. Even when the float body 25 is in contact with the end of the window hole 18 during compression of the spring, fretting hardly occurs, and the centrifugal force is small due to its light weight. Therefore, the movement of the float 25 There is no need to worry about an unstable hysteresis torque increase, and the above-mentioned abnormal noise prevention effect can be kept good.
  • the float body 25 interposed between the two torsion springs 23 is integrally connected by the annular connecting body 537 (47), This prevents the radially outward protrusion due to the centrifugal force, so that the float body 25 does not rub against the end of the window hole 18 during compression of the torsion spring. Therefore, there is no need to worry about an increase in the movement of the float body 25 (unstable hysteresis torque caused by this movement), and the above-described effect of preventing abnormal noise can be kept good.
  • the radially outer end of the output side plate (between plates 6) is formed annularly so that the radially outer edge of the window hole 18 is closed. Since it is formed, the strength of the output 5-side plate can be maintained high while two torsion springs are arranged in one window hole 18, and durability is improved.
  • the connecting body 37 serves as a protective cover for the torsion spring 23, and the torsion spring 23 is provided. Can be protected from outside.
  • the guide plate 35 and the connecting body 47 are formed as an integral body as in claim 4, and the connecting body 47 is arranged on the inner peripheral side of the float body 25, the number of parts can be reduced. And prevent weight increase.
  • the float body 25 is swingably connected to the annular connecting body 37 via the 5-pin 38 as in claim 5, even if the spring load of the torsion spring 23 is imbalanced, it is adjusted to that.
  • the flow By the swinging movement of the body 25, the compression operation of the spring 23 is stabilized, and a smoother torsional performance can be exhibited.
  • the imbalance of the spring load can be absorbed by the swing of the float body 25 around the pin 38, so that the durability of the connection between the annular connector 37 and the float body 25 is improved.
  • the width of the connection portion can be narrowed, whereby a large storage space for the springs 23 can be secured, and a sufficiently wide torsional angle range can be maintained.
  • a pair of left and right thick annular 0-shaped intermediate plate members are overlapped and riveted. 7 to form a first-stage torsion spring storage expanded portion 6a at the inner peripheral end, and a torque direct-connecting screw consisting of an uneven portion between the hub 10 and the flange 11 of the hub 10.
  • a pair of thick intermediate plates 6 are provided, and an expanded portion 6a is formed at the inner peripheral end, and the expanded portion 6a and the side plate Hysteresis torque is stabilized by disposing the friction members 13 and 12 between the flanges 11 respectively.
  • the damper disk of the present invention can obtain a wide range of torsion angles and a stable hysteresis torque, and is therefore most suitable for a damper disk of an automobile ITJ.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

Disque amortisseur présentant un plateau de sortie (6) située entre une paire de plateaux latéraux (1), deux ressorts de torsion (23) disposés en série dans des passages cylindriques ménagés dans chacun desdits plateaux, et des flotteurs (25) disposés entre les deux ressorts de torsion de sorte que ces flotteurs puissent se déplacer dans le sens de la circonférence. Afin d'améliorer les caractéristiques de torsion du disque amortisseur, la plaque de sortie (6) est divisée en des organes internes et externes, ou alors les flotteurs (25) sont reliés par un connecteur annulaire (37) de sorte qu'il ne puisse se déplacer vers l'extérieur, ou encore les flotteurs (25) sont réalisés en une résine présentant un faible coefficient de friction.
PCT/JP1989/000254 1988-03-09 1989-03-08 Disque amortisseur WO1989008792A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE19893990204 DE3990204T1 (de) 1988-03-09 1989-03-08 Daempfungsscheibe
DE3990204A DE3990204C2 (de) 1988-03-09 1989-03-08 Dämpfungsscheibe

Applications Claiming Priority (10)

Application Number Priority Date Filing Date Title
JP63/55825 1988-03-09
JP5582588A JPH01229123A (ja) 1988-03-09 1988-03-09 ダンパーディスク
JP63/31419U 1988-03-09
JP3141988U JPH01135233U (fr) 1988-03-09 1988-03-09
JP63/33461U 1988-03-14
JP1988033461U JPH0631228Y2 (ja) 1988-03-14 1988-03-14 ダンパーディスク
JP1988038836U JPH0543294Y2 (fr) 1988-03-23 1988-03-23
JP63/38836U 1988-03-23
JP63/84777U 1988-06-27
JP8477788U JPH0640989Y2 (ja) 1988-06-27 1988-06-27 ダンパーディスク

Publications (1)

Publication Number Publication Date
WO1989008792A1 true WO1989008792A1 (fr) 1989-09-21

Family

ID=27521333

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP1989/000254 WO1989008792A1 (fr) 1988-03-09 1989-03-08 Disque amortisseur

Country Status (2)

Country Link
DE (1) DE3990204C2 (fr)
WO (1) WO1989008792A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112733070A (zh) * 2021-01-25 2021-04-30 江铃汽车股份有限公司 利用低速扭转灵敏控制低速轰鸣以及变速箱敲击声的方法

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010053934B4 (de) 2009-12-21 2022-10-06 Schaeffler Technologies AG & Co. KG Vorrichtung zur Dämpfung von Schwingungen
DE102011080447A1 (de) * 2011-08-04 2013-02-07 Zf Friedrichshafen Ag Massenelement für einen Rupftilger

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5496651A (en) * 1977-12-27 1979-07-31 Borg Warner Vibration damper assembly
JPS58112739U (ja) * 1982-01-27 1983-08-02 株式会社大金製作所 振動ダンパ−組立体
JPS59147925U (ja) * 1983-03-23 1984-10-03 株式会社大金製作所 多段ヒステリシストルク発生型ダンパ−デイスク
JPS59200817A (ja) * 1983-04-16 1984-11-14 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 クラツチ円板
JPS603328U (ja) * 1983-06-20 1985-01-11 株式会社　大金製作所 捩り振動ダンパ−組立体
JPS6163019U (fr) * 1984-09-29 1986-04-28
JPS6258416B2 (fr) * 1979-06-05 1987-12-05 Borg Warner

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2574573A (en) * 1949-12-09 1951-11-13 Kaiser Frazer Corp Vibration dampener
FR2496210A1 (fr) * 1980-12-16 1982-06-18 Valeo Dispositif amortisseur de torsion, notamment pour disque de friction d'embrayage de vehicule automobile
JPS60112727U (ja) * 1984-01-05 1985-07-30 株式会社　大金製作所 ダンパ−デイスク
DE8514735U1 (de) * 1985-05-18 1992-12-24 LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl Torsionsschwingungsdämpfer
IT1185932B (it) * 1985-09-18 1987-11-18 Automotive Products Borg & Bec Disco condotto di frizione

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5496651A (en) * 1977-12-27 1979-07-31 Borg Warner Vibration damper assembly
JPS6258416B2 (fr) * 1979-06-05 1987-12-05 Borg Warner
JPS58112739U (ja) * 1982-01-27 1983-08-02 株式会社大金製作所 振動ダンパ−組立体
JPS59147925U (ja) * 1983-03-23 1984-10-03 株式会社大金製作所 多段ヒステリシストルク発生型ダンパ−デイスク
JPS59200817A (ja) * 1983-04-16 1984-11-14 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 クラツチ円板
JPS603328U (ja) * 1983-06-20 1985-01-11 株式会社　大金製作所 捩り振動ダンパ−組立体
JPS6163019U (fr) * 1984-09-29 1986-04-28

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112733070A (zh) * 2021-01-25 2021-04-30 江铃汽车股份有限公司 利用低速扭转灵敏控制低速轰鸣以及变速箱敲击声的方法

Also Published As

Publication number Publication date
DE3990204C2 (de) 1999-09-02

Similar Documents

Publication Publication Date Title
US4591348A (en) Damper disc with self-aligning spring seats
US4557702A (en) Damper disc assembly for clutch
US6461243B1 (en) Coil spring assembly and damper mechanism
JPH0317061Y2 (fr)
JPH05280554A (ja) 円板アセンブリ
US6209701B1 (en) Damper disk assembly
JPS6141021A (ja) ト−シヨンスプリング直列配置型ダンパ−デイスク
JPH09504597A (ja) 二質量フライホイール
US4533338A (en) Damper disc
JPS6049125A (ja) ダンパ−デイスク組立体
EP0696694B2 (fr) Disque absorbeur de couple de rotation
US4690660A (en) Damper disc
WO1990013755A1 (fr) Disque amortisseur
JPH0141849B2 (fr)
US6332843B1 (en) Damper disk assembly
US5322474A (en) Spring dampened damper disc having first and second stage torsion springs
US6336867B1 (en) Damper mechanism and damper disk assembly
JPH0240125B2 (fr)
JP2001304341A (ja) シート部材、弾性部材組立体及びダンパー機構
WO1989008792A1 (fr) Disque amortisseur
JP3731236B2 (ja) トーションダンパ
JPH01145429A (ja) クラッチディスク
KR100470424B1 (ko) 댐퍼 기구
JPH0343494B2 (fr)
JPH0543294Y2 (fr)

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): DE US

RET De translation (de og part 6b)

Ref document number: 3990204

Country of ref document: DE

Date of ref document: 19900315

WWE Wipo information: entry into national phase

Ref document number: 3990204

Country of ref document: DE