GB2160296A - Apparatus for compensating for rotational impulses - Google Patents

Apparatus for compensating for rotational impulses Download PDF

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Publication number
GB2160296A
GB2160296A GB08514928A GB8514928A GB2160296A GB 2160296 A GB2160296 A GB 2160296A GB 08514928 A GB08514928 A GB 08514928A GB 8514928 A GB8514928 A GB 8514928A GB 2160296 A GB2160296 A GB 2160296A
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United Kingdom
Prior art keywords
damping device
disks
flange
further damping
axially
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
GB08514928A
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GB2160296B (en
GB8514928D0 (en
Inventor
Paul Maucher
Oswald Friedmann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
LuK Lamellen und Kupplungsbau GmbH
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LuK Lamellen und Kupplungsbau GmbH
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Publication of GB8514928D0 publication Critical patent/GB8514928D0/en
Publication of GB2160296A publication Critical patent/GB2160296A/en
Application granted granted Critical
Publication of GB2160296B publication Critical patent/GB2160296B/en
Expired legal-status Critical Current

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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
    • F16F15/131—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 the rotating system comprising two or more gyratory masses
    • F16F15/133—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 the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F16C25/08—Ball or roller bearings self-adjusting
    • F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring to preload the bearing
    • 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
    • F16F15/131—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 the rotating system comprising two or more gyratory masses
    • F16F15/13164—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 the rotating system comprising two or more gyratory masses characterised by the supporting arrangement of the damper unit
    • 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
    • F16F15/131—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 the rotating system comprising two or more gyratory masses
    • F16F15/139—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 the rotating system comprising two or more gyratory masses characterised by friction-damping means
    • F16F15/1397—Overload protection, i.e. means for limiting torque
    • 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
    • F16F15/30—Flywheels
    • F16F15/302—Flywheels comprising arrangements for cooling or thermal insulation
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/55—Flywheel systems
    • 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
    • F16F2222/00—Special physical effects, e.g. nature of damping effects
    • F16F2222/02—Special physical effects, e.g. nature of damping effects temperature-related
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/16—Mechanical energy storage, e.g. flywheels or pressurised fluids

Landscapes

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

Abstract

The invention relates to an apparatus for compensating for rotational impulses, especially torque variations in an internal combustion engine, by means of at least two gyratory masses (3,4) which are arranged coaxially with respect to each other and are capable of limited relative rotation against the action of a damping device (13). The gyratory mass (3) may be connected to the internal combustion engine and the mass (4) to the input part (10) of a gearbox. The damping device consists of circumferentially acting force accumulators and/or frictional or sliding means, and at least one further damping device (14) is provided, in addition to the said damping device, in the torque transmission path between the gyratory masses. Both damping devices each have, at least two disks (37,38; 24,25) arranged in axially spaced-apart relationship, each set of disks being fixed for rotation with a different one of the gyratory masses, and a common intermediate flange (29) which is operative between both pairs of disks being provided for the transmission of torque between the first damping device and the further damping device. <IMAGE>

Description

SPECIFICATION Apparatus for compensating for rotational impulses The invention relates to an apparatus for compensating for rotational impulses, especially torque variations in an internal combustion engine, by means of at least two gyratory masses which are arranged coaxially with respect to each other and are capable of limited relative rotation against the action of a damping device, one of which gyratory masses may be connected to the internal combustion engine and the other to the input part of a gearbox, the damping device consisting of circumferentially acting force accumulators and/or frictional or sliding means, and at least one further damping device being provided, in addition to the aforesaid damping device, in the torque transmission path between the gyratory masses.
The basic object of the present invention is to improve such apparatuses, especially in regard to the design or construction, the resistance to wear and the operation thereof and furthermore to increase the range of possible applications thereof. In addition, an economical manufacture of such apparatuses is to be ensured.
According to the invention this is achieved, in an apparatus of the kind initially referred to, in that both the first-mentioned damping device and also the further damping device have, in each case, at least two disks arranged in axially spaced-apart relationship, each set of disks is fixed for rotation with a different one of the gyratory masses, and a common intermediate flange, which is operative between the disks of both pairs of disks, is provided for the transmission of torque between the first damping device and the further damping device. It may moreover be appropriate if the intermediate flange radially overlaps both pairs of disks; and, in order to ensure a particularly favourable overall length, it may be particularly suitable if one of the sets of disks is located at least substantially radially inwardly of the other and the flange radially overlaps both sets of disks.
A particularly advantageous construction of the apparatus can be obtained if the input part of the further damping device is formed by the set of disks which is connected to the first gyratory mass, and the output part thereof is formed by the intermediate flange which also forms the input part of the first damping device, the output part of the latter being formed by the two disks that are connected to the second gyratory mass. It may moreover be advantageous if, with a view to the possibility of relative rotation of the two gyratory masses, a positive connection can be provided between the intermediate flange and the radially inner set of disks and/or between the intermediate flange and the radially outer set of disks.Such a positive connection can be obtained by forming shaped impact surfaces on the flange as well as on the group or groups of disks which cooperate with one another.
According to a further feature of the invention, it may be appropriate if the two disks of the first damping device are fixed for rotation with the second gyratory mass, which may be connected to the input part of a gearbox, and the two disks of the further damping device are fixed for rotation with the first gyratory mass which is connected to the internal combustion engine. It may instead, however, be advantageous if the two disks of the first damping device are fixed for rotation with the first gyratory mass and the two disks of the further damping device are fixed for rotation with the second gyratory mass.
A particularly simple construction of the further damping device can be obtained if the intermediate flange is clamped axially between the two disks of the further damping device so that a slip-imparting torque is provided for. Moreover, it may be advantageous, depending on the magnitude of the slip imparting torque if the flange and the two disks of the further damping device are in direct frictional engagement with one another. For by far the greater number of applications it is, however, suitable to provide a frictional or sliding lining between at least one of the disks of the further damping device and the flange, so that, by fitting appropriate friction or sliding linings, the slip-imparting torque can be made to suit the application concerned at any given time.
The axial clamping of the flange between the two disks of the further damping device may be ensured in a particularly simple manner by arranging that one disk of the further damping device is axially fixedly located with respect to one of the gyratory masses and the other disk is axially displaceable with respect to the said one disk. Moreover, the axially fixedly located disk may appropriately lock the other disk aganst rotation. This rotational locking between the two disks of the further damping device may be obtained in an advantageous manner by providing at least one of the disks with axial projections which engage in recesses in the other disk.Moreover, a particularly simple construction can be obtained if these projections are constituted by lugs which are formed integrally on at least one of the disks, extend axially and project axially into recesses provided in the outer circumference of the other disk. Depending on the application concerned, it may be appropriate for the axially fixedly located disk and/or the axially displaceable disk to carry these projections. Furthermore, it may be advantageous if the axial projections are provided on the radially outer circumference of at least one of the disks of the further damping device, so that they can extend axially over the outside of the intermediate flange. The axially fixed connection of at least one of the disks of the further damping device to one of the gyratory masses may be effected according to a further feature of the invention by means of a riveted connection.
In order to produce a slip-imparting torque between the two disks of the further damping device and the intermediate flange, it may be particularly advantageous for the axially displaceable disk of the further damping device to be urged axially in the direction towards the other disk by means of a force accumulator. By suitably constructing the force accumulator, the slip-imparting torque of the further damping device can be varied and made to suit the particular application concerned. It may moreover be appropriate if the force accumulator which acts on the axially displaceable disk is supported against the gyratory mass to which the axially fixedly located disk is secured.
The force accumulators may with advantage be formed by a plate-like element which may be slit or open at its circumference, the outer circumference thereof being surrounded by a shoulder of the gyratory mass against which it is supported. Such plate-spring-like elements which are slit or open at their circumference can be produced in a particularly simple manner by rolling a strip of material. Moreover, such a plate-like element can be fitted in a simple manner in the groove or shoulder surrounding it.
According to a further feature of the invention, the axial projections which are provided on at least one of the disks of the further damping device for preventing rotation thereof may extend through cut-out openings in the flange. These cut-out openings may advantageously be formed in the outer circumference of the flange and, if desired, be open towards the outside. It may be particularly suitable if at least an amount of play corresponding to the maximum possible angle of rotation of the further damping device is provided in the circumferential direction between the cut-out openings and the projections. Furthermore, it may be appropriate if at least some of the axial projections come into contact with the edges of the cut-out openings in the flange for the purpose of limiting the angle of rotation of the further damping device.These abutment edges for the projections on at least one of the disks of the further damping device may with advantage be constituted by radial projections which are formed on the outer periphery of the flange. Thus, the angle of rotation of the further damping device may be limited by engagement of the projections on the flange with axial projections on at least one of the disks of the further damping device.
According to a further development of the invention, it may be suitable if axially aligned openings are provided in the two disks of the further damping device for the reception of force accumulators which are compressible between these disks and the flange. It may moreover be appropriate if these force accumulators are operative in the end parts of the angle of rotation of the further damping device. Such force accumulators may advantageously serve as stop members for limiting the angle of rotation of the further damping device. By this means a violent impact is obviated for example between the projections on the flange and the two disks of the further damping device in the end parts of the angle of rotation of the said further damping device, and therefore noises can be avoided. It may be suitable if the force accumulators are constituted by coil springs and/or rubber blocks.
It may moreover be suitable if the force accumulators are located, in the circumferential direction between the projections on the flange and can be acted upon directly by these projections.
According to an additional feature of the invention, it may be particularly economical if the friction lining which is operative between the flange and at least one of the disks of the further damping device is constituted by separate segments of frictional or sliding material which are affixed to the projections on the flange. Furthermore, it may be advantageous if the flange is guided concentrically by at least one of the gyratory masses.
A particularly advantageous construction of the apparatus can be obtained if at least one of the gyratory masses has an annular projection which extends axially in the direction towards the other gyratory mass and radially within which are arranged the further damping device and the first damping device. It may moreover be suitable, if the projection extends axially over the further damping device, since the plate-spring-like element, which acts against the axially displaceable disk of the further damping device. can then be supported axially and radially, in a manner which is advantageous for most applications, in a groove provided in the open end part of the annular projection. For other applications, it may, however, be suitable if the axially fixedly located disk of the further damping device is fixed against the end of the annular projection which extends axially over the damping device, so that an annular space can be formed between the gyratory mass provided with the projection and the said disk, into which annular space the flange can extend radially and within which the axially displaceable disk of the further damping device can be accommodated. It may moreover be suitable if the first gyratory mass, which is connected with the crankshaft of an internal combustion engine, is provided with the pro jection. In the construction first described, it may furthermore be suitable if the platespring-like element of the further damping device is clamped between the first gyratory mass and the axially displaceable disk of the further damping device.
According to a further development of the invention, for the purpose of concentrically guiding the flange, the projections formed on the outer periphery of the flange are radially supported against the axial annular projection on the said one gyratory mass. By means of such a construction, it is possible to prevent the operation of the first damping device being impaired by extraneous friction. This is particular advantageous for those parts of the rotation of the first damping device in which the torque transmitted between the two gyratory masses is relatively low. It may furthermore be suitable if a frictional or sliding lining is provided between the annular projection on the relevant gyratory mass and the projections on the flange, which lining is made use of for the radial centring of the flange.A particularly advantageous construction of the apparatus can be obtained if at least some of the projections on the flange are each engaged over by a cap composed of frictional and/or sliding material, which on the one hand ensures the radial guiding of the flange and on the other hand is clamped so as to produce a frictional torque between the disk of the further damping device and the flange. Moreover the cap s -onsidered in a circumferential direction-may have formed on their ends resiliently deformable abutment regions which can cooperate with stops so as to limit the angle of rotation of the friction damping device.
According to an additional feature of the invention. in order to centre the flange. at least some of its projections--considered in a circumferential direction-may each be straddled by a stirrup-shaped guide shoe which is supported against an axial projection on the relevant gyratory mass, the side limbs of the stirrup-shaped guide shoe or guide stirrup being advantageously capable of cooperating with stops so as to limit the rotational play in the further damping device. These stops may.
for example, be formed by connecting means extending axially between the two disks. or instead, as already described. by force accumulators accommodated in openings in the two disks of the further damping device. or again by stops provided on the projection of the relevant gyratory mass. Furthermore. it may be advantageous if circumferential play is present between the side limbs of the guide stirrups and the projections on the flange. It may also be appropriate if a force accumulator is provided between the side limbs of the guide stirrup and the projections on the flange. Such force accumulators may advantageously be composed of a resilient material.
such as rubber. These force accumulators prevent too violent an impact being produced in the end parts of the movement of the further damping device. so that noise can be eliminated.
In order to limit the possible angle of rotation between the two gyratory masses, it may furthermore be advantageous for stops to be provided between the flange and the second gyratory mass for limiting the range of angular movement of the first damping device. It may moreover be appropriate if the stops are constituted by spacing bolts which on the one hand interconnect the disks of the first damping device and on the other hand connect them with the second gyratory mass and which extend axially through openings in the flange. It may moreover be suitable if the angle of rotation of the first damping device is limited by impact of the spacing bolts against the end parts of the openings in the flange.
Advantageously, the openings in the flange may be so formed and arranged that the flange has on its inner circumference radial teeth which engage between the spacing bolts. It may moreover be advantageous if the teeth are produced by forming cut out recesses in the radially inner part of the flange.
The rotation of the flange with respect to the corresponding gyratory mass can thus be limited by impact of the spacing bolts which interconnect the two disks of the first damping device against the teeth on the flange.
According to a further constructional possibility of the invention. the disks of the further damping device may be axially fixed with respect to each other by spacing means. such as spacing bolts. and at least one of the said disks may have between the spacing bolts a circumferentially extending. resiliently flexible, prestressed bulge which resiliently urges the flange in the direction towards the other disk.
In such a construction of the further damping device. a separate force accumulator is not necessary for resiliently urging the two disks of the further damping device towards each other. In such a construction. it is furthermore advantageous if the spacing bolts provided between the two disks of the further damping device serve at the same time for securing the disks to one of the gyratory masses.
Furthermore, it may be advantageous if the further damping device Is so constructed that the disks that are provided one on each side of the flange are clamped against the said flange by circumferentially distributed spring stirrups or clamps. It may moreover be appropriate if the stirrups or clamps engage axially over the flange and two disks of the further damping device and. by means of radially extending limbs. engage axially behind the disks and urge them in respective directions towards the flange. The side limbs of the stirrups or clamps moreover may advantageously extend radially inwardly.
Furthermore, it may be advantageous if one of the gyratory masses has axial projections which engage in openings in the disks of the further damping device which are located adjacent of the flange, so as to lock the said disks rotationally. Moreover, it may be particularly advantageous if projections formed on the circumference of the flange engage radially between the axial projections-consi- dered in a circumferential direction-and force accumulators, which are accommodated in openings in the disks of the further damping device, serve as end stops for the projections on the flange for limiting the angle of rotation of the further damping device.Furthermore, it may be suitable if at least some of the openings of the accommodation of the force accumulators in one of the disks are so circumferentially offset with respect to the axially opposite openings in the other disk that the force accumulators accommodated in the axially oppositely located openings urge the disks circumferentially against the projections which extend through the openings in the disks. By this means noise is avoided. It may be appropriate if the axial projections are constituted by bolts or pins which are fixed to one of the gyratory masses.
According to a further construction of the invention, it may be advantageous if the flange has, in the region between the disks of the further damping device, axial openings in which are accommodated friction blocks or friction linings that are clamped between the disks of the further damping device. For many applications it may be appropriate if the openings in the flange extend axially completely through it and a friction block of greater thickness than that of the flange extends through each of these openings. It may moreover be advantageous if the friction blocks are axially slidable in their openings. but are guided so as to prevent radial and/or circumferential displacement thereof.
For many applications it may, however, be appropriate if each of the axial openings accommodates a pair of friction blocks arranged in tandem, between which is provided a force accumulator, such as for example a plate spring, which resiliently urges the friction blocks against the disks of the further damping device. In order to facilitate easy assembly of the apparatus. it may moreover be advantageous if the pair of friction blocks and the force accumulator located between them and held together axially by connecting means which, however, permit a limited amount of axial displacement of the two friction blocks with respect to each other against the action of the force accumulator provided between them.
When friction blocks are used in the further damping device, it may be particularly advantageous if the flange has blind bores that are directed towards each other, for the accommodation of the friction blocks and if the intermediate partition wall, which is formed in the flange between the two blind bores that are directed towards each other has an opening through which extends a connecting means interconnecting the two oppositely located friction blocks, a force accumulator, such as a plate spring, being arranged between at least one of the friction blocks and the intermediate partition wall and serving for resiliently loading the friction blocks between the disks of the further damping device and the connecting means furthermore permitting a limited axial displacement of the oppositely located friction blocks against the action of the force accumulator.
According to a further feature of the invention it may be particularly advantageous if the first damping device is located radially inwardly of the further damping device.
The invention will be explained in more detail with reference to Figs. 1 to 11, in which: Figure 1 shows, in section. an apparatus according to the invention, Figure 2 is a partial elevational view according to the arrow II of the apparatus shown in Fig. 1, Figure 3 shows. in section, a possible construction of a further damping device for an apparatus according to the invention.
Figures 4 and 5 show another possible construction of a further damping device for an apparatus according to the invention, Fig.
5 being a section on the line V-V of Fig. 4, Figure 6 shows another possible construction of a further damping device for an apparatus according to the invention, Figures 7 and 8, as well as Figures 9 and 10, shows further possible constructions of other damping devices for an apparatus according to the invention, Fig. 8 showing one disk of a pair of disks of the further damping device in the dismantled condition and Fig. 9 a section on the line IX-IX of Fig. 10, Figure 11 shows an additional possible construction of a further damping device for an apparatus according to the invention.
The apparatus shown in Figs. 1 and 2 for compensating for rotational impulses is provided with a flywheel 2 which is subdivided into two gyratory masses 3 and 4. The first gyratory mass 3 is connected to a crankshaft 5 of an internal combustion engine (not otherwise shown) by means of fixing screws 6. A friction clutch 7 is connected by means (not specifically shown) to the second gyratory mass 4. Between the pressure plate 8 of the friction clutch 7 and the gyratory mass 4 there is provided a clutch disk 9 which is mounted on the input shaft 10 of a gearbox (not otherwise shown). The pressure plate of the friction clutch 7 is urged in the direction towards the gyratory mass 4 by a diaphragm spring 1 2 which is rockably mounted on a clutch cover plate 11.By operating the fric tion clutch 7, the gyratory mass 4 and therewith also the flywheel 2 can be coupled to and uncoupled from the input shaft 10 of the gearbox. A first damping device 1 3 as well as a second damping device 14 connected in series therewith are provided between the gyratory mass 3 and the gyratory mass 4, which damping device permit a limited relative rotation between the two gyratory masses 3 and 4.
The two gyratory masses 3 and 4 mounted for relative rotation by means of a bearing assembly 1 5. The bearing assembly 1 5 comprises a rolling bearing in the form of a tworow angular contact ball bearing 1 6 with a divided inner race ring 1 7. The outer race ring 1 6a of the rolling bearing 1 6 is mounted in a bore 1 8 in the gyratory mass 4 and the inner divided race ring 1 7 of the rolling bearing 1 6 is mounted on a central hollow cylindrical journal pin 1 9 provided on the gyratory mass 3 and extending axially away from the crankshaft 5.
The two partial race rings 1 7a, 1 7b of the inner race ring 1 7 are axially spring-loaded by means of a force accumulator in the form of a plate spring 20. In order to secure the partial race ring 1 7b in position, an abutment disk 21 is fixed against the end 1 9a of the journal pin 1 9 by means of screws 21 a. This abutment disk 21 projects radially outwardly of the journal pin 1 9 and the partial race ring 1 7b is supported against it. The plate spring 20 between the partial race ring 1 7a and the gyratory mass 3 urges the partial race ring 1 7a axially in the direction towards the partial race ring 1 7b, since it is supported by its radially outer parts against the gyratory mass 3 and act by means of radially inner parts thereof against the partial race ring 1 7a.As a result of this construction, the rolling bodies of the bearing assembly 1 6 are held under load between the rolling tracks adjacent to them. In order to ensure that the bearing remains under load even while the friction clutch 7 is being operated, the plate spring 20 exerts a force which is greater than the maximum force that is required to operate the friction clutch 7. It has proved to be advantageous for the force exerted by the plate spring 20 to be chosen so as to be approximately twice as great as the maximum force required to disengage the friction clutch 7.
The gyratory mass 3 has on the radially outer part thereof an axial annular projection 22 which forms a chamber 23 in which the first damping device 1 3 as well as the further damping device 14 are mainly accomodated.
The input part of the further damping device 14 is formed by a set of disks 24, 25 which are arranged in axially spaced-apart relationship and are fixed for rotation with the gyratory mass 3. The annular disk 25 is secured against the end surface 22a of the projection 22 by means of rivets 26 and axially delimits the chamber 23 by means of its inwardly projecting part 25a. The disk 24 which is housed in the chamber 23 has axial projections which are constituted by lugs 24a formed integrally on the outer circumferential part thereof. In order to prevent rotation of the disk 24 with respect to the disk 25, the lugs 24a engage in openings 27 in the disk 25. The openings 27 and the lugs 24a are so shaped and arranged that a possibility of axial displacement of the disk 24 with respect to the disk 25 is provided for.Radial projections 28 on the flange 29 are clamped between the two disks 24 and 25, since a force accumulator in the form of a plate spring 30 located axially between the disk 24 and the gyratory mass 3 urges the disk 24 in the direction towards the disk 25. For this purpose, the plate spring 30 is supported by its radially outer part against the pressure plate 3 and by its radially inner part against the disk 24. The outer circumferential part of the plate spring 30 is gapped or split, i.e. its annular basic body is severed at one position, and is supported radially at its radially outer periphery against an annular shoulder 31 on the gyratory mass 3. Between the projections 28 of the flange 29 and each of the two disks 24 and 25, friction linings are provided in the form of individual lining segments 32 stuck to the projections 28.In the region between the projections 28 of the flange 29 openings 33, 34 are formed in the disks 24 and 25 which are in axial alignment and accommodate force accumulators 35. In the example shown.
these force accumulators are constituted by coil springs 35, but hard rubber springs for example could be used instead. The force accumulators 35 serve as end stops for the projections 28 of the flange 29 and consequently limit the angle of rotation of the further damping device 1 4. By means of the damping action of the force accumulators 35 an excessively hard impact at the end parts of the angular movement of the further damping device is avoided.
As is clear more particularly from Fig. 2, in which the further damping device is shown in an intermediate position. there is provided between the force accumulators 35 and the projections 28 an amount of play 36 + 36a which increases the possible angular rotational movement between the disks 24, 25 which form the input part and the flange 29 which forms the output part of the further damping device 1 4 by the amount through which the force accumulators 35 are compressed.
The flange 29 which forms the output part of the further damping device 1 4 constitutes at the same time the input part of the first damping device 1 3. The first damping device 1 3 has a further set of disks, namely the two disks 37, 38 which are arranged one on each side of the flange 29 and are connected together in axially spaced-apart relationship by spacing bolts 39 so as to be fixed for rotation with each other and are connected to the gyratory mass 4, the two disks 37, 38 are surrounded radially outwardly by the annular disks 24, 25 of the further damping device 14. Moreover, in the example shown, the disks 37 and 24, as well as the disks 38 and 25, are arranged at least approximately in common planes.Openings 37a, 38a and 29a, in which force accumulators in the form of coil springs 40 are received, are formed in the disks 37, 38 and in the part of the flange 29 which is located radially inside the projections 28. The force accumulators 40 oppose relative rotation between the flange 29 and the two disks 37, 38.
The first damping device 1 3 has in addition a friction device 1 3a which is operative over the whole of the possible angle of rotation between the two gyratory masses 3 and 4.
The friction device 1 3a is located axially between the disk 37 and the gyratory mass 3 and includes a force accumulator 41, constituted by a frusto-conical plate spring. which is held clamped between the disk 37 and a thrust ring 42. so that the friction ring 43 arranged between the thrust ring 42 and the gyratory mass 3 is spring-loaded. The force exerted by the plate spring 41 against the disk 37 is taken via the bearing assembly 16.
The thrust ring 42 is provided with projections 42a which engage round the heads of the spacing bolts 39 so that the thrust ring is fixed for rotation with the gyratory mass 4.
At its inner periphery the flange 29 has inwardly open recesses 44 through which the spacing bolts 39 extend axially. These recesses form radially-inwardly projecting teeth 45 which---considered in a circumferential direction--engage between the spacing bolts 39 and cooperate with them as stops for limiting the extent of angular movement of the first damping device 1 3.
The openings 37a, 38a in the two disks 37, 38 and the openings 29a in the flange 29, as well as the coil springs (40) provided in them, are so arranged around the circumference of the first damping device 1 3 and so dimensioned that a multi-stage damping characteristic is obtained.
In order to obtain at least approximately concentric guiding of the flange 29 with respect to the axis of rotation 47 and hence also with respect to the gyratory masses 3 and 4, the flange 29 is supported by its radial projections 28 against the inner boundary surface 22b of the axial projection 22 of the flywheel 3.
The apparatus according to the present embodiment is so constructed and arranged that, starting from a rest position shown in Fig. 2, when a torque variation occurs, first of all the gyratory mass 3 is rotated together with the two disks 24, 25 and the flange 29 relatively to the second gyratory mass 4 and the pair of disks 37, 38, against the action of the springs 40, whereupon, as a result of the openings of different sizes in the flange 29 and in the pair of disks 37, 38, a progressive increase in the damping action takes place. This relative rotation continues until the torque produced by the stressing of the said springs attains a value equal to the torque which can be transmitted by the further damping device 14.
On continuation of the relative movement in this direction the further damping device then begins to slip, so that no relative rotation of the flange 29 with respect to the second gyratory mass takes place until the springs 35 come to lie against the edges of the projections 28. The projections 28 produce a further relative rotation of the flange, together with the first gyratory mass 3, with respect to the second gyratory mass 4, the springs being further compressed until the teeth 45 come into contact with the bolts 39.
As is clear particularly from Fig. 2, the projections 28 in the embodiment shown are so formed that they come into contact with the springs 35 so as to limit the maximum angle of rotation of the further damping device 14. By suitably varying the shapes of the impact surface of the projections 28 it would be made possible for the lugs 24a to be made use of additionally. In such an embodiment the impact surfaces concerned of the projections 28 must be so arranged in relation to the force accumulators 35 and the lugs 24aconsidered in a circumferential direction-that the force accumulators first take up the torsional impulses and then. together with the lugs 24a. limit the extent of rotation between the two disks 24, 25 and the flange 29.Furthermore, it would be possible to let the force accumulators 35 be dispensed with and to utilize only the lugs 24a for limiting the angle of rotation between the input part and the output part of the further damping device.
In the constructional variant shown in Fig.
3, the disk 1 25. which is connected by means of a rivet connection 1 26 to the first gyratory mass 103 so as to be fixed for rotation therewith, has axially projecting lugs 1 25a formed on its radially outer part. The lugs 1 25a extend in the direction towards the second gyratory mass 104 and engage axially in recesses 1 27 which are formed in the outer circumference of the disk 1 24. The recesses 127 and the lugs 1 25a are so shaped and arranged in relation to each other that the disk 1 24 is circumferentially fixed with respect to the disk 125, but it nevertheless capable of adjustment axially.Between the two disks 1 24 and 1 25. which form the intput part of the further damping device 11 4 there is a flange 1 29 which constitutes the output part of the further damping device 114. A friction lining 1 32 is provided between the flange 129 and each of the disks 124. 125. The flange 1 29 forms at the same time the input part of the first damping device 113, the output part of which is once again formed by two disks 137, 1 38 which are fixed for rotation with each other as well as with the gyratory mass 104 by spacing bolts 139.The further damping device 114 and the first damping device 11 3 are once again arranged radially within an axial projection 1 22 of the gyratory mass 103. A groove 131 is formed in the radially inner boundary surface of the projection 1 22 near the free end of the latter, in which groove a plate spring 1 30 is supported both axially and radially. In order to faciliate assembly thereof. this plate spring 1 30 is slit or formed with recesses in its outer circumference.The plate spring 130, by means of its radially inner part, urges the disk 1 24 axially in the direction towards the disk 125, so that the flange 1 29 is clamped axially between these two disks and the slip-imparting torque which can be transmitted by the further damping device is determined by the axial force and the coefficient of friction between the friction lining 1 32 and the flange.
In the constructional variant of a further damping device 214 shown in Figs. 4 and 5 friction or sliding linings 248 are arranged between the radially inner boundary surface 222b of the axial projections 122 on the gyratory mass 203 and the projections 228 on the flange 221. The flange 229 is guided concentrically with respect to the gyratory mass 203 by these friction or sliding linings 248. The friction or sliding linings 248 form, in the constructional example shown, the bases of caps 249 which are fitted over the projections 228 and straddle the latter. The lateral parts 250, 251 of the caps 249 are axially clamped between the projections 228 of the flange 229 and the disks 224, 225 of the further damping device 214 which are located one on each side of the flange. so as to produce a frictional moment.The axial clamping is ensured by a plate spring 232 which acts against the disk 225 and is supported axially against the gyratory mass 203.
In order to retain the caps 249 radially against the action of centrifugal force. the lateral parts 250, 251 have, on the sides thereof facing the projections 228, arcuateshaped bulges 250a, 251a which engage in correspondingly shaped arcuate grooves 1 52 in the projections 228. In order to enable the caps 249 to be slid onto the projections 228 by virtue of their inherent elasticity, the bulges 250a, 251as-seen in a circumferential direction cxtend only over a part of the length of the grooves 252 or of the projections 228.The parts 253, 254 of the caps 249 which are important circumferentially form resilient or shock-absorbing contact regions which cooperate with stops 255, that are fixed for rotation with the gyratory mass 203, for limiting the angle of rotation of the further damping device 214. The stops 255 are formed by pins or bolts which are anchored in the gyratory mass 203 and extend axially through bores 256 so as to ensure that the disks 224, 225 are kept fixed for rotation with the said gyratory mass.
In the constructional variant shown in Fig.
6, stirrup-shaped guide shoes 349 are provided on the projections 328 of the flange 329 for centering the flange 329 with respect to the gyratory mass 303. The stirrup-shaped guides 349 engage over the projections 328, the radially extending side limbs of these stirrup-shaped guides cooperating with stops 355, which are fixed for rotation with the gyratory mass 303, for limiting the angle of rotation of the further damping device 314.
As in the constructional variant shown in Figs.
4 and 5 the stops 355 are formed by pins or bolts which are anchored in the gyratory mass 303 and extend axially through the disks of the further damping device which are arranged one on each side of the flange 329.
The part 349a which interconnects the two limbs 353 and 354 of each stirrup-shaped guide 349 is guided between the radially inner boundary surface 322b of the axial projection 322 on the gyratory mass 303 and the radially outer boundary surfaces of the projections 328. The stirrup-shaped guides 349 have---considered in a circumferential direction-a greater extent than the projections 328, so that an amount of play X is present between the latter on each side of these projections 328 and the side limbs 353 354 of the stirrup-shaped guides 349. Force accumulators in the form of hard rubber blocks 357 are provided in the free spaces formed by the play X. These hard rubber blocks 357 produce a damping of the projections between the side limbs 353 354 and the stops 355.The shoes 349 may be composed of metal or of a friction or sliding material.
In Figs. 7 and 8, the two disks 424, 425 are rigidly connected to each other as well as to the gyratory mass 403 by spacing means in the form of spacing bolts 455. Radial projections 428 on a flange 429 engage between the two disks 424. 425, friction linings 432 being provided between the projections 428 and the two disks 424, 425.
As is apparent from Fig. 8, the disk 425 has a circumferentially extending undulation 425a between the fixing holes 455a for the spacing bolts 455, which undulation 425a is prestressed, as shown in Fig. 7, when the disk 425 is assembled. As a result of this prestress, the flange 429 or the projections 428 thereof is or are axially clamped between the disks 424, 425, so that. when a relative rotation occurs, a suitable frictional torque is produced. In order to restrict the angle of rotation of the further damping device 414, force accumulators 435, against which the projections 428 on the flange 429 come into contact, are once again provided in openings in the disks 424, 425.
In the embodiment shown in Figs. 9 and 10, the disks 524, 525 provided one on each side of the flange 529 of the further damping device 514 are resiliently clamped against this flange 529 by spring stirrups or spring clamps 530 which are distributed around the circumference, friction rings 532 being interposed between the said disks 524, 525 and the said flange 529. The stirrups or clamps 530 engage axially over both the flange 529 and the two disks 524 and 525 and press against the said disks 524, 525 by means of radially inwardly extending resiliently flexible limbs 530a, 530b. In order to fix the disks 524, 525 rotationally, axial projections in the form of bolts 555 provided on the gyratory mass 503 extend axially through holes 555a, 555b made to accommodate them in the disks 524, 525.Openings 533, 534 for the reception of force accumulators 535 provided in the disks 524, 525 cooperate with the projections 528 on the flange 529 for limiting the angle of rotation of the further damping device 514.
As is clear from Fig. 10, in the assembled condition of the disks 524 and 525, the openings 533 in the disk 524 are offset circumferentially by an amount Y with referecne to openings 534 in the disk 525, so that the force accumulators 535 are axially stressed in one direction or asymmetrically.
This asymmetrical stressing the force accumulators 535 once again causes the disks 524, 525 to be resiliently urged circumferentially against the bolts 555 which extend through the holes 555a, 555b. The operation of the further damping device 514 is substantially improved as a result of this stressing, since, due to it, play, for example between the holes 555a, 555b in the disks 524, 525 and the bolts 555 can be compensated for, so that a damping effect is always present when relative rotation occurs.
In the constructional form shown in Fig. 11 of a further damping device 614, the flange 629 has, in the region between the disks 624 and 625 which form the input part of the further damping device 614, blind bores 656.
657 which are directed axially towards each other and in which disk-shaped friction pads 658, 659 respectively are inserted. The partition wall part 660 of the flange 629 that is left between the two blind bores 656 and 657 is formed with an opening 661 through which extends a connecting means in the form of a rivet 662 interconnecting the pair of axially oppositely located friction pads 658, 659. A prestressed plate spring 663 provided between the friction pad 658 and the partition wall part 660 produces an axial spreading or forcing apart of the two friction pads 658 and 659 so that these friction pads are pressed against the corresponding disks 624, 625 with which they are in frictional engagement.
The connecting rivet 662 is so dimensioned that, starting from the assembled position shown in Fig. 11 of the two friction pads 658, 659, it permits a limited axial displacement of these friction pads 658, 659 away from each other. This capability of limited axial displacement of the two friction pads makes possible on the one hand an equalization of the wear of the two friction pads 658, 659 and on the other hand ensures that, when the further damping device 614 has not yet been assembled, the friction pads 658, 659 as well as the plate spring 663 are axially fixedly located on the flange 629, so that the assembly of the apparatus or of the further damping device 61 4 is substantially facilitated. During the assembly of the apparatus or of the further damping device 614, the two friction pads 658 and 659 are axially clamped between the two disks 624, 625 against the action of the plate spring 663.
As can be further appreciated from Fig. 11, the friction pad 659 is directly supported axially against the partition wall part 660, whereas there is an axial empty space between the friction pad 658 and the partition wall part 660, so that the friction pad 658 can be displaced axially in the blind bore 656 against the action of the plate spring 663

Claims (70)

1. Apparatus for compensating for rotational impulses, especially torque variations in an internal combustion engine. by means of at least two gyratory masses which are arranged coaxially with respect to each other and are capable of limited relative rotation against the action of a damping device. one of which gyratory masses may be connected to the internal combustion engine and the other to the input part of a gearbox, the said damping device consisting of circumferentially acting force accumulators and/or frictional or sliding means, and at least one further damping device being provided. in addition to the said damping device, in the torque transmission path between the gyratory masses, characterised in that both the first-mentioned damping device (13, 11 3) and also the further damping device (14, 114. 214, 314, 414, 514, 614) have. in each case. at least two disks (37+38. 137 + 138; 24 + 25, 124 + 125, 224 + 225, 424 + 425, 524 + 525, 624 + 625) arranged in axially spaced-apart relationship, each set of disks is fixed for rotation with a different one of the gyratory masses (3,4; 103,104; 203; 303; 403; 503). and a common intermediate flange (29, 129, 229, 329, 429. 529. 629), which is operative between the discs of both pairs of disks, is provided for the transmission of torque (11, 13) between the first and further damping device (14, 114. 214. 314, 414, 514, 614).
2. Apparatus for compensating for rotational impulses according to claim 1, characterised in that the intermediate flange (29, 129, 229, 329, 429, 529, 629) radially overlaps both pairs of disks (37 + 38, 137+138; 24+25, 124+ 125 224 + 225, 424 + 425, 524 + 525, 624 + 625).
3. Apparatus for compensating for rotational impulses according to one of claims 1 or 2, characterised in that one of the sets of disks (37 + 38, 137 + 138) is located at least substantially radially inwardly of the other (24 + 25, 124 + 125, 224 + 225 424 + 425, 524 + 525, 624 + 625) and the flange (29, 129, 229, 329, 429, 529, 629) radially overlaps both sets of disks (37 + 38, 137+138; 24+25, 124+125.
224 + 225, 424 + 425, 524 + 525, 624 + 625).
4. Apparatus for compensating for rotational impulses according to one of claims 1 to 3, characterised in that the input part of the further damping device (14, 114, 214, 314,414, 514, 614) is formed by the set of disks (24 + 25, 124 + 125, 224 + 225, 424 + 425, 524 + 525, 624 + 625) which is connected to the first gyratory mass (3, 103) and the output part thereof is formed by the intermediate flange (29, 129, 229, 319, 429, 529, 629) which also forms the input part of the first damping device (13, 11 3), the output work of the latter being formed by the two disks (37, 38; 137, 138) that are connected to the second gyratory mass.
5. Apparatus for compensating for rotational impulses according to one of claims 1 to 4, characterised in that a positive connection can be provided between the intermediate flange (29, 129, 229, 319, 429. 529, 629) and the radially inner set of disks (37 + 38; 1 37 + 138) and/or between the intermediate flange (29, 129, 229, 329, 429, 529, 629) and the radially outer set of disks (24 + 25, 124 + 125, 224 + 225, 424 + 425, 524 + 525, 624 + 625).
6. Apparatus for compensating for rotational impulses according to one of claims 1 to 5, characterised in that the pair of disks (37 + 38; 1 37 + 138) of the first damping device (13, 11 3) is fixed for rotation with the second gyratory mass (4, 104) and the pair of disks (24, 25; 124, 125; 224, 225; 424, 425; 524, 525; 624, 625) of the further damping device (14. 114, 214, 314, 414, 514, 614) with the first gyratory mass (3, 103, 203, 303, 403, 503).
7. Apparatus for compensating for rotational impulses according to one of claims 1 to 3 or 5, characterised in that the pair of disks of the first damping device is fixed for rotation with the first gyratory mass and the pair of disks of the further damping device with the second gyratory mass.
8. Apparatus for compensating for rotary impulses according to one of the preceding claims 1 to 7, characterised in that the flange (29, 129, 229, 329, 529, 629) is clamped axially between the pair of disks (24, 25; 124, 125; 224, 225;, 424, 425; 524, 525; 624, 625) of the further damping device (14, 114, 214, 314, 414, 514, 614).
9. Apparatus for compensating for rotary impulses according to claim 8, characterised in that a frictional or sliding lining (32, 1 32.
249, 432, 532, 658, 659) is provided between one of the disks (24. 25; 1 24, 125; 224, 225; 424, 425; 524, 525; 624. 625) of the further damping device (14, 114, 214, 314, 414, 514, 614) and the flange (29, 129, 229. 329. 429, 529, 629).
10. Apparatus for compensating for rotary impulses according to one of claims 1 to 9, characterised in that one disk (25, 125) of the further damping device (1 4, 114) is axially fixedly located with respect to one (3, 103) of the gyratory masses (3, 4; 103, 104) and the other disk (24, 124) is axially displaceable with respect to the said one disk (25, 125).
11. Apparatus according to claim 1 0, characterised in that the axially fixedly located disk (25, 125) secures the other disk (24, 124) against rotation.
12. Apparatus according to claim 10 or 11, characterised in that, in order to secure it against rotation, at least one (24. 125) of the disks (24. 25, 124, 125) of the second damping device (14, 114) has axial projections (24a; 125a) which engage in recesses (27, 127) in the other disk (25, 124).
1 3. Apparatus according to claim 12, characterised in that the projections (24a, 125a) are constituted by lugs (24a. 125a) which are formed integrally on at least one of the disks (24, 25, 124, 125), extend axially and project axially into recesses (27, 127) provided in the outer circumference of the other disk.
14. Apparatus according to claim 12 or 13, characterised in that the axially fixedly located disk (125) carries the projections (125a).
1 5. Apparatus according to claim 12 or 13, characterised in that the axially displaceable disk (25) carries the projections (25a).
16. Apparatus according to one of claims 1 2 to 15, characterised in that the axial projections (24a, 125a) are provided on the radially outer circumference of at least one of the disks (24, 25. 124, 125) of the further damping device (14, 114).
1 7. Apparatus according to at least one of claims 1 to 16, characterised in that the axially fixed connection of at least one (25, 125, 424, 425) of the disks (24, 25, 124, 125, 424, 425) of the further damping device to one (3, 1 03. 403) of the gyratory masses (3, 4, 103, 104, 403) is obtained by means of a riveted connection.
18. Apparatus according to one of claims 9 to 17, characterised in that the axially displaceable disk (24, 125, 225, 524, 525) of the further damping device (14, 114, 214, 514) is urged axially in the direction towards the other disk (25, 124, 224, 525, 524) by means of a force accumulator (30, 130, 232, 530).
1 9. Apparatus according to one of claims 1 6 to 18, characterised in that the force accumulator (30, 130) which acts on the axially displaceable disk (24, 124) is supported against the gyratory mass (3, 103) to which the axially fixedly located disk (25, 125) is secured.
20. Apparatus according to claim 19, characterised in that the force accumulator (30, 130) is formed by a plate-spring-like element (30, 130).
21. Apparatus according to claim 20, characterised in that the plate-like element (30, 130) is slit or open at its circumference, the outer circumference of this element being surrounded by a shoulder (31, 131) of the gyratory mass (3, 103) against which it is supported.
22. Apparatus according to one of claims 1 2 to 21, characterised in that the axial projections (24a, 125a) extend through cutout openings in the flange (29, 129).
23. Apparatus according to claim 22, characterised in that at least an amount of play corresponding to the possible angle of rotation of the further damping device is present in the circumferential direction between the cut-out openings and the projections (24 a, 125a)
24. Apparatus according to claim 22 or 23, characterised in that at least some of the axial projections (24a, 125a) come into contact with the edges of the cut-out openings in the flange (29, 1 29) for the purpose of limiting the angle of rotation of the further damping device (14, 114).
25. Apparatus according to one of claims 1 to 24, characterised in that the flange (29, 229, 329, 429, 529) has on its outer periphery radial projections (28, 228, 328, 428, 528) which limit the angle of rotation of the further damping device (14, 214, 314. 414, 514).
26. Apparatus according to claim 25, characterised in that the radial projections (28) come into contact with axial projections (24a) of at least one (24) of the disks (24, 25) of the further damping device (14).
27. Apparatus according to one of claims 1 to 26, characterised in that axially aligned openings (33, 34; 533, 534) are provided in the two disks (24 + 25, 124 + 125, 424 + 425, 524 + 525) of the further damping device (14,114,214,414, 514) for the reception of force accumulators (35, 435, 535) which are compressible between these disks and the flange (29, 129, 429, 529).
28. Apparatus according to claim 27, characterised in that the force accumulators (35, 435. 535) are operative in the end parts of the angle of rotation of the further damping device.
29. Apparatus according to one of claims 27 or 28, characterised in that the force accumulators (35, 435, 535) serve as stop members for limiting the angle of rotation of the further damping device.
30. Apparatus according to one of claims 27 to 29, characterised in that the force accumulators (35, 435, 535) are constituted by coil springs.
31. Apparatus according to one of claims 27 to 29, characterised in that the force accumulators are constituted by rubber blocks.
32. Apparatus according to one of claims 27 to 31, characterised in that the force accumulators (35, 435, 535) are located, in the circumferential direction, between the projections (28, 428, 528) on the flange (29, 429. 529) and can be acted upon by them.
33. Apparatus according to at least one of claims 1 to 32, characterised in that the friction lining which is operative between the flange (29) and at least one of the disks (24, 25) of the further damping device (14) is constituted by separate segments (32) of frictional or sliding material which are affixed to the projections (28) on the flange (29).
34. Apparatus according to one of claims 1 to 33, characterised in that the flange (29.
229, 329) is guided concentrically by at least one (3, 203, 303) of the gyratory masses.
35. Apparatus according to one of claims 1 to 34, characterised in that at least one (3, 103, 203, 303, 503) of the gyratory masses has an annular projection (22, 122, 222.
322) extending axially in the direction towards the other gyratory mass (4, 104), radially within which are arranged the further damping device (14, 114, 214, 314, 414, 514, 614) and the first damping device (13.
113).
36. Apparatus according to claim 31.
characterised in that the projection (22, 122, 222, 322) extends axially over the further damping device (14, 114, 214, 314, 514, 614).
37. Apparatus according to at least one of the preceding claims. characterised in that the plate-like element (130), which acts against the axially displaceable disk (124) of the further damping device (114), is supported axially and radially in a groove (131) provided in the open end part of the annular projection (122).
38. Apparatus according to claim 35 or 36, characterised in that the axially fixedly located disk (25) of the further damping device (14) is fixed against the end (22a) of the projection (22), so that an annular space (23) is formed between the gyratory mass (3) which is provided with the projection (22) and the said disk (25), the flange (29) projects into the said annular space and the axially displaceable disk (24) of the further damping device (14) is accommodated in the same.
39. Apparatus according to one of claims 35 to 38, characterised in that the first gyratory mass (3, 103, 203, 303, 503) is provided with the projection (22, 122, 222, 322).
40. Apparatus according to at least one of the preceding claims, characterised in that the plate-like element (30) of the further damping device (14) is clamped between the first gyratory mass (3) and the axially displaceable disk (24) of the further damping device (14).
41. Apparatus according to at least one of the preceding claims, characterised in that, for the purpose of concentrically guiding the flange (29, 229, 329), the projections (28, 228, 328) of the flange are radially supported against the axial annular projection (22, 122, 322) on the said one gyratory mass (3, 203, 303).
42. Apparatus according to claim 37, characterised in that a frictional or sliding lining (248. 349a) is provided between the annular projection (222, 322) and the projections (28, 228) on the flange (29, 229).
43. Apparatus according to claim 41 or 42, characterised in that at least some projections (228) on the flange (229) are each engaged over by a cap (249) composed of frictional and/or sliding material, which on the one hand ensures the radial guiding of the flange (229) and on the other hand is clamped so as to produce a frictional torque between the disks (224, 225) of the further damping device (214).
44. Apparatus according to claim 43, characterised in that the caps (249+consi- dered in a circumferential direction-have formed on their ends resiliently deformable abutment regions (253. 254) which cooperate with stops (255) so as to limit the angle of rotation of the further damping device (214).
45. Apparatus according to one of the preceding claims. characterised in that, in order to centre the flange (329), at least some of its projections (328)--considered in a circumferential direction-are each straddled by a stirrup-shaped guide shoe (349) which is supported against the projection (322) of the gyratory mass (303).
46. Apparatus according to claim 45, characterised in that the side limbs (353, 354) of the guide stirrup (349) cooperate with stops (355), so as to limit the rotational play in the further damping device (314).
47. Apparatus according to claim 45 or 46, characterised in that circumferential play (X) is present between the side limbs (353, 354) of the guide stirrup (349) and the projections (328).
48. Apparatus according to one of claims 45 to 47, characterised in that a force accumulator (357) is provided between the side limbs (353, 354) of the guide stirrup (349) and the projections (328).
49. Apparatus according to claim 48.
characterised in that the force accumulators (357) are composed of a resilient material, such as rubber.
50. Apparatus according to at least one of the preceding claims, characterised in that stops (39, 139) are provided between the flange (29, 129) and the second gyratory mass (4, 104) for limiting the range of angular movement of the first damping device (13, 113).
51. Apparatus according to claim 50, characterised in that the stops are constituted by spacing bolts (39, 1 39) which on the one hand interconnect the disks (37, 38; 137, 138) of the first damping device (13, 113) and on the other hand connect them with the second gyratory mass and which extends axially through openings (44) in the flange (29, 129).
52. Apparatus according to claim 51, characterised in that the angle of rotation of the first damping device (13, 113) is limited by impact of the spacing bolts (39, 139) against the end parts of the opening (44) in the flange (29, 129).
53. Apparatus according to one of claims 50 to 52, characterised in that the flange (29) has on its inner circumference radial teeth (45) which engage between the spacing bolts (39).
54. Apparatus according to claim 53, characterised in that the teeth (45) are produced by forming cut out recesses (44) in the radially inner part of the flange (29).
55. Apparatus according to at least one of the preceding claims. characterised in that the flange (29. 129, 229. 329, 429, 529, 629) is rotatable to a limited extent with respect to the second gyratory mass (4, 104).
56. Apparatus according to at least one of claims 1 to 55, characterised in that the disks (424, 425) of the further damping device (414) are axially fixed with respect to each other by spacing means (455). such as spacing bolts, and at least one (425) of the said disks (424, 425) has between the spacing means (455) a circumferentially extending resiliently flexible prestressed bulge (425a) which resiliently urges the flange (429) in the direction towards the other disk (424).
57. Apparatus according to claim 56.
characterised in that the spacing bolts (455) serve at the same time for securing the disks (424. 425) to one (403) of the gyratory masses.
58. Apparatus according to at least one of the preceding claims, characterised in that the disks (524, 525) of the further damping device (514), which are provided one on each side of the flange (529) are clamped against the said flange (529) by circumferentially distributed spring stirrups (530) or clamps.
59. Apparatus according to claim 58, characterised in that the stirrups or clamps (530) engage axially over the flange (529) and the two disks (524, 525) of the further damping. device (514) and by means of radially extending limbs 530a, 530b engage axially behind the disks (524, 525) and urge them in respective directions towards the flange (529).
60. Apparatus according to at least one of the preceding claims, characterised in that one (503) of the gyratory masses has axial projections (555) which engage in openings (555a, 555b) in the disks (524, 575) of the further damping device (514), which are located on one side of the flange (529), so as to lock the said disks rotationally.
61. Apparatus according to claim 60, characterised in that projections (528) formed on the circumference of the flange (529) engages radially between the axial projections (555)considered in a circumferential direction-and force accumulators (535), which are accommodated in openings (533, 534) in the disks (524, 525) of the further damping device (514), serve as end stops for the projections (528) of the flange (529) for limit ing the angle of rotation of the further damping device.
62. Apparatus according to claim 60 or 61, characterised in that at least some of the openings (534) for the accommodation of the force accumulators (535) in one of the disks (525) are so circumferentially offset with respect to the axially opposite openings (533) in the other disk (524) that the force accumulators (535) accommodated in the oppositely located openings (533, 534) urge the disks (524, 525) circumferentially against the projections (555) which extend through the openings (555a, 555b) in the disks (524. 525).
63. Apparatus according to one of claims 60 to 62, characterised in that the axial projections are constituted by bolts (555) or pins which are fixed to one (503) of the gyratory masses.
64. Apparatus according to at least one of the preceding claims, characterised in that the flange (629) has, in the region between the disks (624, 625) of the further damping device (614), axial openings (656, 657) in which are accommodated friction blocks (658.
659) that are clamped between the disks (624, 625) of the further damping device (614).
65. Apparatus according to claim 64, characterised in that the openings extend axially completely through the flange and a friction block having a thickness greater than that of the flange extends through each of the said openings.
66. Apparatus according to claim 64 or 65, characterised in that the friction blocks (658) are axially slidable in their openings, but are guided so as to prevent radial and/or circumferential displacement thereof.
67. Apparatus according to one of claims 64 to 66, characterised in that each of the axial openings (656, 657) accommodates a pair of friction blocks (658, 659) arranged in tandem, between which is provided a force accumulator, such as for example, a plate spring (663) which resiliently urges the friction blocks (658, 659) agaist the disks of the further damping device (614).
68. Apparatus according to claim 67, characterised in that the pair of friction blocks (658, 659) and the force accumulator (663) located between them are held together axially by connecting means (662) which, however, permit a limited amount of axial displacement of the two friction blocks (658, 659) with respect to each other against the action of the force accumulator (663).
69. Apparatus according to one of claims 64 and 66 to 68, characterised in that the flange (629) has blind bores (656, 657), which are directed axially towards each other, for the accommodation of friction blocks (658, 659), the intermediate partition wall (660) in the flange (629) between the two blind bores (656. 657) which are directed axially towards each other having an opening through which extends a connecting means (662) interconnecting the two oppositely located friction blocks (658, 659), a force accumulator. such as a plate spring (663), being arranged between at least one (658) of the friction blocks (658, 659) and the intermediate partition wall (660). which force accumulator resiliently loads the friction blocks (658, 659) between the disks (624, 625) of the further damping device (614) and the connecting means (662) furthermore permitting a limited axial displacement of the oppositely located friction blocks (658, 659) against the action of the forcer accumulator (663).
70. Apparatus according to one of claims 1 to 69 characterised in that the first damping device (13, 113) is located radialy inwardly of the further damping device (14, 114, 214, 314, 414, 514. 614).
GB08514928A 1984-06-12 1985-06-12 Apparatus for compensating for rotational impulses Expired GB2160296B (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3421709 1984-06-12
DE3425159 1984-07-07

Publications (3)

Publication Number Publication Date
GB8514928D0 GB8514928D0 (en) 1985-07-17
GB2160296A true GB2160296A (en) 1985-12-18
GB2160296B GB2160296B (en) 1987-12-23

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
GB08514928A Expired GB2160296B (en) 1984-06-12 1985-06-12 Apparatus for compensating for rotational impulses

Country Status (3)

Country Link
DE (1) DE3520853C2 (en)
FR (3) FR2565650B1 (en)
GB (1) GB2160296B (en)

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US4947706A (en) * 1986-09-05 1990-08-14 Toyota Jidosha Kabushiki Kaisha Flywheel with a torsional damper
US4950205A (en) * 1987-09-14 1990-08-21 Toyota Jidosha Kabushiki Kaisha Flywheel with a torsional damper
US4950204A (en) * 1987-08-28 1990-08-21 Toyota Jidosha Kabushiki Kaisha Flywheel with a torsional damper
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US5032107A (en) * 1987-12-14 1991-07-16 Toyota Jidosha Kabushiki Kaisha Flywheel device with a torsional damper
US5083981A (en) * 1988-12-08 1992-01-28 Fichtel & Sachs Ag Two-mass fly-wheel for a motor vehicle
US5088964A (en) * 1988-12-15 1992-02-18 J. M. Voith Gmbh Viscous damper assembly for a flywheel assembly including friction plates
US5156067A (en) * 1988-04-01 1992-10-20 Toyota Jidosha Kabushiki Kaisha Torsional damper type flywheel device
US5168773A (en) * 1989-09-20 1992-12-08 Ab Volvo Flywheel device for an internal combustion engine
US5209139A (en) * 1989-09-20 1993-05-11 Ab Volvo Flywheel for an internal combustion engine
FR2687442A1 (en) * 1992-02-14 1993-08-20 Valeo Double damping flywheel, particularly for a motor vehicle
FR2688564A1 (en) * 1992-03-10 1993-09-17 Valeo Double damping flywheel, particularly for motor vehicles
DE4303371A1 (en) * 1992-02-20 1993-10-28 Valeo Rotary vibration damper having two coaxial parts for vehicle - has single friction unit axially clamped between friction faces and having anti-wear means to prevent sliding contact.
FR2690721A1 (en) * 1992-04-30 1993-11-05 Valeo Double moving shock absorber for automobile vehicles - comprises first, second masses with friction device mounted within second mass engaging with some play with head of fixing screw implanted radially below anti-friction member
FR2690722A1 (en) * 1992-04-30 1993-11-05 Valeo Double damping flywheel, especially for a motor vehicle.
US5269199A (en) * 1988-04-01 1993-12-14 Toyota Jidosha Kabushiki Kaisha Torional damper type flywheel device
FR2700191A1 (en) * 1986-07-05 1994-07-08 Luk Lamellen & Kupplungsbau Device for damping vibrations.
FR2721984A1 (en) * 1994-06-30 1996-01-05 Valeo SHOCK ABSORBER, AND CLUTCH IN PARTICULAR FOR A MOTOR VEHICLE EQUIPPED WITH SUCH A STEERING WHEEL
US5620373A (en) * 1992-03-18 1997-04-15 Aisin Seiki Kabushiki Kaisha Torque variation absorbing device
GB2315840A (en) * 1993-06-19 1998-02-11 Luk Lamellen & Kupplungsbau Flywheel device
US5759105A (en) * 1993-06-25 1998-06-02 Valeo Double damped flywheel having friction device for ease of assembly and calibration, especially for motor vehicles
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GB2169380B (en) * 1984-12-27 1989-10-11 Nissan Motor Power transmission device for motor vehicle
GB2169380A (en) * 1984-12-27 1986-07-09 Nissan Motor Power transmission device for motor vehicles
FR2594916A1 (en) * 1986-02-27 1987-08-28 Luk Lamellen & Kupplungsbau DAMPING DEVICE
US4760754A (en) * 1986-02-27 1988-08-02 Luk Lamellen Und Kupplungsbau Gmbh Apparatus for transmitting torque between flywheels in the power train between the engine and the transmission of a motor vehicle
US4846759A (en) * 1986-03-19 1989-07-11 Daimler-Benz Aktiengesellschaft Device for reducing engine-excited vibrations of a drive train, especially a split flywheel
FR2700192A1 (en) * 1986-07-05 1994-07-08 Luk Lamellen & Kupplungsbau Split steering wheel.
FR2601103A1 (en) * 1986-07-05 1988-01-08 Luk Lamellen & Kupplungsbau OSCILLATION DAMPING DEVICE
US4783895A (en) * 1986-07-05 1988-11-15 Luk Lamellen Und Kupplungsbau Gmbh Method of making apparatus for damping torsional vibrations
FR2700191A1 (en) * 1986-07-05 1994-07-08 Luk Lamellen & Kupplungsbau Device for damping vibrations.
US4947706A (en) * 1986-09-05 1990-08-14 Toyota Jidosha Kabushiki Kaisha Flywheel with a torsional damper
US4950204A (en) * 1987-08-28 1990-08-21 Toyota Jidosha Kabushiki Kaisha Flywheel with a torsional damper
US4950205A (en) * 1987-09-14 1990-08-21 Toyota Jidosha Kabushiki Kaisha Flywheel with a torsional damper
US5032107A (en) * 1987-12-14 1991-07-16 Toyota Jidosha Kabushiki Kaisha Flywheel device with a torsional damper
US5156067A (en) * 1988-04-01 1992-10-20 Toyota Jidosha Kabushiki Kaisha Torsional damper type flywheel device
US5269199A (en) * 1988-04-01 1993-12-14 Toyota Jidosha Kabushiki Kaisha Torional damper type flywheel device
US5083981A (en) * 1988-12-08 1992-01-28 Fichtel & Sachs Ag Two-mass fly-wheel for a motor vehicle
US5088964A (en) * 1988-12-15 1992-02-18 J. M. Voith Gmbh Viscous damper assembly for a flywheel assembly including friction plates
US5156066A (en) * 1989-09-20 1992-10-20 Ab Volvo Flywheel for an internal combustion engine
US5168773A (en) * 1989-09-20 1992-12-08 Ab Volvo Flywheel device for an internal combustion engine
US5209139A (en) * 1989-09-20 1993-05-11 Ab Volvo Flywheel for an internal combustion engine
EP0423089A1 (en) * 1989-09-20 1991-04-17 Ab Volvo Flywheel for an internal combustion engine
FR2687442A1 (en) * 1992-02-14 1993-08-20 Valeo Double damping flywheel, particularly for a motor vehicle
DE4303371A1 (en) * 1992-02-20 1993-10-28 Valeo Rotary vibration damper having two coaxial parts for vehicle - has single friction unit axially clamped between friction faces and having anti-wear means to prevent sliding contact.
DE4303371B4 (en) * 1992-02-20 2004-06-24 Valeo Torsional vibration damper, in particular double damping wheel and clutch disc for motor vehicles
US5503595A (en) * 1992-02-20 1996-04-02 Valeo Torsion damping device for a motor vehicle, being in particular a double damped flywheel or a clutch friction wheel
DE4307133A1 (en) * 1992-03-10 1993-10-07 Valeo Automotive torsional-vibration damper with coaxial masses - has friction unit with elastic component between axial friction surfaces on masses
FR2688564A1 (en) * 1992-03-10 1993-09-17 Valeo Double damping flywheel, particularly for motor vehicles
US5370581A (en) * 1992-03-10 1994-12-06 Valeo Torsion damping device, especially for a motor vehicle
DE4307133B4 (en) * 1992-03-10 2004-07-08 Valeo Double damping flywheel, especially for motor vehicles
US5620373A (en) * 1992-03-18 1997-04-15 Aisin Seiki Kabushiki Kaisha Torque variation absorbing device
DE4313507C2 (en) * 1992-04-30 2002-06-13 Valeo Double damping flywheel, in particular for a motor vehicle
FR2690721A1 (en) * 1992-04-30 1993-11-05 Valeo Double moving shock absorber for automobile vehicles - comprises first, second masses with friction device mounted within second mass engaging with some play with head of fixing screw implanted radially below anti-friction member
US5367920A (en) * 1992-04-30 1994-11-29 Valeo Damped double flywheel for a motor vehicle
FR2690722A1 (en) * 1992-04-30 1993-11-05 Valeo Double damping flywheel, especially for a motor vehicle.
GB2315840A (en) * 1993-06-19 1998-02-11 Luk Lamellen & Kupplungsbau Flywheel device
GB2315840B (en) * 1993-06-19 1998-09-02 Luk Lamellen & Kupplungsbau Flywheel device
GB2323425A (en) * 1993-06-19 1998-09-23 Luk Lamellen & Kupplungsbau Flywheel device
GB2323425B (en) * 1993-06-19 1999-02-10 Luk Lamellen & Kupplungsbau Flywheel device
US5759105A (en) * 1993-06-25 1998-06-02 Valeo Double damped flywheel having friction device for ease of assembly and calibration, especially for motor vehicles
US5784928A (en) * 1994-06-30 1998-07-28 Valeo Damped flywheel, especially for a motor vehicle
WO1996000859A1 (en) * 1994-06-30 1996-01-11 Valeo Flywheel particularly for motor vehicles
FR2721984A1 (en) * 1994-06-30 1996-01-05 Valeo SHOCK ABSORBER, AND CLUTCH IN PARTICULAR FOR A MOTOR VEHICLE EQUIPPED WITH SUCH A STEERING WHEEL
US9523409B2 (en) 2011-01-21 2016-12-20 Aisin Seiki Kabushiki Kaisha Torque fluctuation absorbing apparatus

Also Published As

Publication number Publication date
FR2633683B1 (en) 1993-11-05
GB2160296B (en) 1987-12-23
FR2633684A1 (en) 1990-01-05
FR2565650B1 (en) 1990-04-27
FR2565650A1 (en) 1985-12-13
GB8514928D0 (en) 1985-07-17
DE3520853C2 (en) 1996-07-18
FR2633683A1 (en) 1990-01-05
FR2633684B1 (en) 1994-03-04
DE3520853A1 (en) 1986-04-24

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Legal Events

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PCNP Patent ceased through non-payment of renewal fee

Effective date: 20040612