US20010006136A1 - Friction liner having a network of grooves, for a clutch - Google Patents
Friction liner having a network of grooves, for a clutch Download PDFInfo
- Publication number
- US20010006136A1 US20010006136A1 US09/785,644 US78564401A US2001006136A1 US 20010006136 A1 US20010006136 A1 US 20010006136A1 US 78564401 A US78564401 A US 78564401A US 2001006136 A1 US2001006136 A1 US 2001006136A1
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- Prior art keywords
- liner
- grooves
- network
- friction
- reaction surface
- Prior art date
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- 238000006243 chemical reaction Methods 0.000 claims abstract description 34
- 239000007788 liquid Substances 0.000 claims abstract description 8
- 238000004891 communication Methods 0.000 claims description 6
- 230000008878 coupling Effects 0.000 claims description 6
- 238000010168 coupling process Methods 0.000 claims description 6
- 238000005859 coupling reaction Methods 0.000 claims description 6
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 claims description 5
- 229910052799 carbon Inorganic materials 0.000 claims description 5
- 239000002131 composite material Substances 0.000 claims description 4
- 239000012530 fluid Substances 0.000 description 5
- 230000002093 peripheral effect Effects 0.000 description 5
- 238000010438 heat treatment Methods 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 2
- 238000013016 damping Methods 0.000 description 2
- 230000003014 reinforcing effect Effects 0.000 description 2
- 229920003043 Cellulose fiber Polymers 0.000 description 1
- 238000003763 carbonization Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000001627 detrimental effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/60—Clutching elements
- F16D13/64—Clutch-plates; Clutch-lamellae
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/74—Features relating to lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D47/00—Systems of clutches, or clutches and couplings, comprising devices of types grouped under at least two of the preceding guide headings
- F16D47/06—Systems of clutches, or clutches and couplings, comprising devices of types grouped under at least two of the preceding guide headings of which at least one is a clutch with a fluid or a semifluid as power-transmitting means
-
- 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
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D69/00—Friction linings; Attachment thereof; Selection of coacting friction substances or surfaces
- F16D2069/004—Profiled friction surfaces, e.g. grooves, dimples
-
- 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
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0215—Details of oil circulation
-
- 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
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
- F16H2045/0289—Details of friction surfaces of the lock-up clutch
-
- 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
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
- F16H2045/0294—Single disk type lock-up clutch, i.e. using a single disc engaged between friction members
Definitions
- This invention relates to friction liners, in particular for bridging clutches for torque converters.
- the invention relates to a friction liner of the above type which has an annular friction surface for making axial contact against a reaction surface, the liner being also of the type in which the friction surface is formed with a network of grooves to enable a liquid to flow between the liner and the reaction surface.
- Torque converters are in particular used in motor vehicles to provide a coupling between the heat engine of the vehicle and the gearbox, which may be automatic and/or of a continuously variable type.
- the transmission of the torque is obtained by circulation of a fluid between two bladed or finned wheels or rotors, one of which is coupled to the engine and the other to the gearbox.
- these two wheels are not coupled together mechanically, so that there always exists between them the possibility of relative slipping movement. In some operating modes of the vehicle, this slipping movement is of no value and can even be detrimental to the overall performance of the drive train of the vehicle.
- a bridging clutch is generally provided, for the purpose of making a direct mechanical coupling between the engine and the gearbox in certain operating modes, corresponding for example to quasi stabilised speed ranges.
- bridging clutches have been used essentially in an “all or nothing” operating mode, that is to say they are used only in a fully engaged state or a fully disengaged state.
- the bridging clutch is tending more and more to be used, no longer only in its fully engaged and fully disengaged states, but also in a mode in which it slips, in particular with a view to damping out torque variations.
- the object of the invention is to overcome the above mentioned problems.
- a friction liner for a bridging clutch of a torque converter having an annular friction surface which is adapted to make axial engagement against a reaction surface, the friction liner being of the type in which the friction surface includes a network of grooves to enable a liquid to flow between the liner and the reaction surface, is characterised in that the network of grooves comprise concentric circular grooves which are connected together through radial grooves spaced apart circumferentially, in that radial grooves are open firstly into an inner circular groove and secondly at the inner edge of the liner, in that the radial grooves formed between two circular grooves are offset circumferentially with respect to the radial grooves formed between the inner circular groove and the inner edge, and in that the radial grooves are not open radially to the outside of the liner.
- a friction liner for a bridging clutch of a torque converter having an annular friction surface which is adapted to make axial engagement against a reaction surface, the friction liner being of the type in which the friction surface includes a network of grooves to enable a liquid to flow between the liner and the reaction surface, is characterised in that the network of grooves is not open radially to the outside of the liner, and in that the liner has a spiral groove and a set of radial grooves which are open at the inner edge of the liner, the said radial grooves intersecting the spiral groove at several points.
- a friction liner having an annular friction surface which is adapted to make axial engagement against a reaction surface, the friction liner being of the type in which the friction surface includes a network of grooves to enable a liquid to flow between the liner and the reaction surface, is characterised in that the network of grooves is not open radially to the outside of the liner, in that it has a single groove which is elliptical and centred on the axis of the liner, the major axis of the ellipse defined by the said single groove being shorter than the outer diameter of the liner, and in that radial grooves put the elliptical groove in communication with the inner edge of the liner.
- the friction liner is preferably incorporated in a bridging clutch of a torque converter.
- the depth of the grooves of the friction liner is preferably substantially equal to one half of the axial thickness of the liner.
- the liner is preferably made of a composite material including carbon.
- FIG. 1 is a diagrammatic view showing in axial cross section a bridging clutch for a torque converter.
- FIGS. 2 and 3 are enlarged scrap views showing part of the clutch of FIG. 1, and illustrating more particularly the contact between the friction liner and the reaction surface of the clutch.
- FIG. 4 is a front view of a first embodiment of an annular friction liner in accordance with the invention, for a clutch of the kind exemplified in FIGS. 1 to 3 .
- FIG. 5 is a view in cross section taken on the line 5 - 5 in FIG. 4.
- FIG. 6 is a view similar to FIG. 4 but showing a second embodiment of the invention.
- FIG. 7 is a view in cross section taken on the line 7 - 7 in FIG. 6.
- FIG. 8 is a view similar to FIG. 6 but shows a third embodiment of the invention.
- FIG. 9 is a view in cross section taken on the line 9 - 9 in FIG. 8.
- FIG. 1 shows a torque converter 10 which is arranged to be, for example, interposed between a heat engine and an automatic gearbox, in a motor vehicle.
- the torque converter 10 comprises a substantially cylindrical outer casing 12 having an axis A 1 , which is coupled to the output shaft (not shown) of the engine of the vehicle, so as to be driven in rotation about its axis A 1 .
- the torque converter 10 has a substantially transverse wall 16 arranged on the side of the torque converter opposite to the engine. This wall 16 has an internal face 14 which carries a series of vanes 18 that act as a fluid pump.
- a turbine wheel 20 is provided with vanes 22 and is mounted for rotation about the axis A 1 with respect to the casing 12 .
- the turbine wheel 20 is arranged to drive in rotation an output shaft 24 of the torque converter 10 , which is coupled to the gearbox.
- the turbine wheel 20 is mounted on a central sleeve 26 , which is coupled to the output shaft 24 , for example through a splined coupling.
- the casing of the torque converter contains oil which provides fluid coupling between the pump vanes 18 and the turbine wheel 20 .
- a bridging clutch 30 is arranged within the casing 12 of the torque converter 10 , for coupling the output shaft 24 of the torque converter 10 in rotation to the casing 12 when the clutch is engaged. Engagement of the bridging clutch 30 thus normally prevents relative rotational slipping movement about the axis A 1 between the casing 12 (constituting a pump) and the turbine wheel 20 that drives the shaft 24 .
- the bridging clutch 30 includes a substantially annular movable clutch plate 32 which is mounted, through a radially-inner axial peripheral flange 34 , in sliding axial movement on the central sleeve 26 .
- the movable clutch plate 32 is also coupled in rotation to the central sleeve 26 through an interposed torsion damping device 36 , for absorbing the torque variations that occur during engagement and disengagement of the clutch.
- the movable clutch plate 32 carries an annular friction liner 38 at its outer periphery.
- the liner 38 is arranged to make axial contact against a corresponding reaction surface 40 formed on the internal face of a transverse wall 42 of the casing 12 .
- This wall 42 is the casing wall which lies axially on the same side of the torque converter as the engine of the vehicle, and may be referred to as the proximal wall of the casing, the wall 16 then being the distal wall.
- the clutch liner 38 may for example be made of a composite material comprising a resin in which reinforcing elements are embedded. These reinforcing elements may for example be in the form of cellulose fibres or carbon fibres. In another version, the liner 38 may be of a carbon/carbon composite material.
- the movable clutch plate 32 defines within the torque converter casing 12 two chambers 44 and 46 , between which the plate 32 constitutes a piston, in such a way that, according to the prevailing oil pressure in each of these chambers, the clutch plate 32 is urged axially in one or other direction.
- the first chamber 44 which is defined between the movable clutch plate 32 and the proximal wall 42 which carries the reaction surface 40
- the movable clutch plate 32 is pushed axially in a direction such as to cause the bridging clutch 30 to be disengaged.
- the second chamber 46 of the casing 12 defined between the clutch plate 32 and the distal wall 16 and, as shown in FIG. 1, also containing the torque converter itself, is supplied with fluid under pressure
- the clutch plate 32 is displaced axially in a direction such as to cause the clutch 30 to be engaged.
- FIGS. 4 to 9 showing three different versions of a friction liner 38 incorporating features of the invention.
- These liners 38 are in the form of flat annular plate elements having an axis A 1 and a transverse fastening face 48 , by means of which they are fastened, for example, on the movable clutch plate 32 , together with an opposed annular transverse face, or friction surface, 50 which makes the frictional contact against the reaction surface 40 , FIGS. 1 to 3 , of the casing 12 .
- the friction surface 50 is formed with a network of grooves which enable oil to circulate between the friction liner 38 and the reaction surface 40 , especially for cooling purposes.
- This network of grooves is not open radially towards the outside of the liner 38 .
- the liner 38 comprises a peripheral outer ring portion 52 which is solid and which has a transverse surface, constituting part of the friction surface 50 , which is continuous over the whole periphery of the liner.
- the grooves which constitute the above mentioned network of grooves are open radially in only the inner peripheral edge 62 of the annular friction liner 38 .
- These grooves can be made, in particular, either by moulding or by machining.
- FIGS. 2 and 3 show diagrammatically the contact between the friction liner 38 against the reaction surface 40 .
- the movable clutch plate 32 tends to deform, due mainly to the contact force applied between the central sleeve 26 (FIG. 1) and the movable clutch plate 32 in the region of its internal flange 34 .
- the movable clutch plate 32 tends to deform in such a way that the liner 38 makes its initial contact with the reaction surface 40 through the outer peripheral edge 51 (FIG. 4) of the outer ring portion 52 of the liner. Subsequently, under the effect of pressure, the contact between the liner 38 and the reaction surface 40 spreads over the whole of the frictional contact surface 50 of the liner, as can be seen in FIG. 2.
- the bridging clutch 30 is controlled in such a way as to slip on the reaction surface 40 , that is to say if the excess pressure in the chamber 46 of the casing 12 is moderated, the contact pressure between the reaction surface 40 and the liner friction surface 50 is reduced in such a way that a slight flow of oil will be able to pass between the two surfaces 40 and 50 , such as to cool them.
- This oil flow is assisted by the presence of the grooves which are formed in the radially inner portion of the liner 38 , and which limit the radial distance over which the ring portion 52 tends to provide sealing.
- FIGS. 4 to 9 show three different versions of this network.
- the liner has essentially two concentric circular grooves 54 and 56 , which are joined together through radial grooves 58 regularly spaced apart circumferentially.
- further radial grooves 60 are open firstly into the inner circular groove 54 and secondly in the inner edge 62 of the liner 38 .
- the radial grooves 58 formed between the two circular grooves 54 and 56 are offset circumferentially with respect to the other radial grooves 60 which extend between the inner circular groove 54 and the inner edge 62 .
- the liner 38 has a single spiral groove 64 and a set of radial grooves 66 which are open in the inner edge 62 of the liner 38 .
- the radial grooves 66 intersect the spiral groove 64 at several points as shown.
- the liner 38 has a single groove 68 which is elliptical, centred on the axis A 1 of the liner 38 .
- the major axis A 2 of the ellipse is shorter than the outer diameter of the liner.
- Radial grooves 70 provide communication between the elliptical groove 68 and the internal edge 62 of the liner 38 .
- the depth of the various grooves 54 , 56 , 58 , 60 , 64 , 66 , 68 , 70 is substantially equal to one half of the axial thickness of the liner 38 .
- grooves may take a number of very different forms, so that the invention is not limited to those described above by way of example.
- the various geometries proposed for the network of grooves in the friction liner 38 enable the torque that can be transmitted by the bridging clutch 30 to be increased, while at the same time limiting heating of the liner 38 and heating of the oil when the clutch 30 is in a slipping mode.
- the invention is not limited to the use of a single friction liner.
- the liner 38 can, in this connection, cooperate with a further liner carried by the reaction surface.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
A torque converter includes a bridging clutch having an annular friction liner for engaging axially against a reaction surface of the clutch. The liner is in the form of an annular ring having a friction surface, an outer perimeter and an inner perimeter, with a network of grooves formed in the friction surface to enable a liquid to flow between the liner and the reaction surface. The network of grooves is not open radially in the outer perimeter of the liner.
Description
- This invention relates to friction liners, in particular for bridging clutches for torque converters.
- More particularly, the invention relates to a friction liner of the above type which has an annular friction surface for making axial contact against a reaction surface, the liner being also of the type in which the friction surface is formed with a network of grooves to enable a liquid to flow between the liner and the reaction surface.
- Torque converters are in particular used in motor vehicles to provide a coupling between the heat engine of the vehicle and the gearbox, which may be automatic and/or of a continuously variable type. In a torque converter, the transmission of the torque is obtained by circulation of a fluid between two bladed or finned wheels or rotors, one of which is coupled to the engine and the other to the gearbox. In their construction, these two wheels are not coupled together mechanically, so that there always exists between them the possibility of relative slipping movement. In some operating modes of the vehicle, this slipping movement is of no value and can even be detrimental to the overall performance of the drive train of the vehicle.
- In addition, in parallel with the torque converter, a bridging clutch is generally provided, for the purpose of making a direct mechanical coupling between the engine and the gearbox in certain operating modes, corresponding for example to quasi stabilised speed ranges. Up to the present time, such bridging clutches have been used essentially in an “all or nothing” operating mode, that is to say they are used only in a fully engaged state or a fully disengaged state.
- With a view to optimising the performance of the drive train of the vehicle considered as a whole, it is now thought desirable to use the bridging clutch in a larger number of operating modes of the drive train, and especially, for example, during gear changing operations. In addition, the bridging clutch is tending more and more to be used, no longer only in its fully engaged and fully disengaged states, but also in a mode in which it slips, in particular with a view to damping out torque variations.
- Thus, there is now an increasing tendency for the bridging clutch to be operated in a way which tends to give rise to severe heating, firstly of the contact surfaces and secondly of the oil which not only controls the clutch but also cools it.
- With a view to preventing this additional heating causing accelerated wear of the liners, or causing the oil to be degraded by carbonisation, it has previously been proposed to arrange on the friction liners a network of grooves which give improved circulation of the oil between the friction liner and the reaction surface. Various proposals have been made as to the form of the grooves in this type of network, all of them aiming to establish communication between the outer and inner perimeters of the annular friction liner.
- However, the existence of the network of grooves gives rise to a loss of oil, even when the bridging clutch is used in its fully engaged mode and when there are no longer any differences in speed between the input shaft connected to the engine and the output shaft connected to the gearbox. In addition, the presence of these grooves in the friction liner substantially reduces the effective contact surface between the friction liner and the reaction surface, to the detriment of the torque that can be transmitted without slipping by the bridging clutch.
- The object of the invention is to overcome the above mentioned problems.
- According to the invention in a first aspect, a friction liner for a bridging clutch of a torque converter, having an annular friction surface which is adapted to make axial engagement against a reaction surface, the friction liner being of the type in which the friction surface includes a network of grooves to enable a liquid to flow between the liner and the reaction surface, is characterised in that the network of grooves comprise concentric circular grooves which are connected together through radial grooves spaced apart circumferentially, in that radial grooves are open firstly into an inner circular groove and secondly at the inner edge of the liner, in that the radial grooves formed between two circular grooves are offset circumferentially with respect to the radial grooves formed between the inner circular groove and the inner edge, and in that the radial grooves are not open radially to the outside of the liner.
- According to the invention in a second aspect, a friction liner for a bridging clutch of a torque converter, having an annular friction surface which is adapted to make axial engagement against a reaction surface, the friction liner being of the type in which the friction surface includes a network of grooves to enable a liquid to flow between the liner and the reaction surface, is characterised in that the network of grooves is not open radially to the outside of the liner, and in that the liner has a spiral groove and a set of radial grooves which are open at the inner edge of the liner, the said radial grooves intersecting the spiral groove at several points.
- According to the invention in a third aspect, a friction liner, having an annular friction surface which is adapted to make axial engagement against a reaction surface, the friction liner being of the type in which the friction surface includes a network of grooves to enable a liquid to flow between the liner and the reaction surface, is characterised in that the network of grooves is not open radially to the outside of the liner, in that it has a single groove which is elliptical and centred on the axis of the liner, the major axis of the ellipse defined by the said single groove being shorter than the outer diameter of the liner, and in that radial grooves put the elliptical groove in communication with the inner edge of the liner.
- The friction liner is preferably incorporated in a bridging clutch of a torque converter.
- The depth of the grooves of the friction liner is preferably substantially equal to one half of the axial thickness of the liner.
- The liner is preferably made of a composite material including carbon.
- Further features and advantages of the invention will appear more clearly on a reading of the following detailed description of some preferred embodiments of the invention, which is given by way of non-limiting example only and with reference to the accompanying drawings.
- FIG. 1 is a diagrammatic view showing in axial cross section a bridging clutch for a torque converter.
- FIGS. 2 and 3 are enlarged scrap views showing part of the clutch of FIG. 1, and illustrating more particularly the contact between the friction liner and the reaction surface of the clutch.
- FIG. 4 is a front view of a first embodiment of an annular friction liner in accordance with the invention, for a clutch of the kind exemplified in FIGS.1 to 3.
- FIG. 5 is a view in cross section taken on the line5-5 in FIG. 4.
- FIG. 6 is a view similar to FIG. 4 but showing a second embodiment of the invention.
- FIG. 7 is a view in cross section taken on the line7-7 in FIG. 6.
- FIG. 8 is a view similar to FIG. 6 but shows a third embodiment of the invention.
- FIG. 9 is a view in cross section taken on the line9-9 in FIG. 8.
- FIG. 1 shows a
torque converter 10 which is arranged to be, for example, interposed between a heat engine and an automatic gearbox, in a motor vehicle. - In the known way, the
torque converter 10 comprises a substantially cylindricalouter casing 12 having an axis A1, which is coupled to the output shaft (not shown) of the engine of the vehicle, so as to be driven in rotation about its axis A1. Thetorque converter 10 has a substantiallytransverse wall 16 arranged on the side of the torque converter opposite to the engine. Thiswall 16 has aninternal face 14 which carries a series ofvanes 18 that act as a fluid pump. Inside thecasing 12, aturbine wheel 20 is provided withvanes 22 and is mounted for rotation about the axis A1 with respect to thecasing 12. Theturbine wheel 20 is arranged to drive in rotation anoutput shaft 24 of thetorque converter 10, which is coupled to the gearbox. Theturbine wheel 20 is mounted on acentral sleeve 26, which is coupled to theoutput shaft 24, for example through a splined coupling. - The casing of the torque converter contains oil which provides fluid coupling between the
pump vanes 18 and theturbine wheel 20. - Again in the known way, a
bridging clutch 30 is arranged within thecasing 12 of thetorque converter 10, for coupling theoutput shaft 24 of thetorque converter 10 in rotation to thecasing 12 when the clutch is engaged. Engagement of thebridging clutch 30 thus normally prevents relative rotational slipping movement about the axis A1 between the casing 12 (constituting a pump) and theturbine wheel 20 that drives theshaft 24. - The
bridging clutch 30 includes a substantially annularmovable clutch plate 32 which is mounted, through a radially-inner axialperipheral flange 34, in sliding axial movement on thecentral sleeve 26. Themovable clutch plate 32 is also coupled in rotation to thecentral sleeve 26 through an interposedtorsion damping device 36, for absorbing the torque variations that occur during engagement and disengagement of the clutch. - The
movable clutch plate 32 carries anannular friction liner 38 at its outer periphery. Theliner 38 is arranged to make axial contact against acorresponding reaction surface 40 formed on the internal face of atransverse wall 42 of thecasing 12. Thiswall 42 is the casing wall which lies axially on the same side of the torque converter as the engine of the vehicle, and may be referred to as the proximal wall of the casing, thewall 16 then being the distal wall. - The
clutch liner 38 may for example be made of a composite material comprising a resin in which reinforcing elements are embedded. These reinforcing elements may for example be in the form of cellulose fibres or carbon fibres. In another version, theliner 38 may be of a carbon/carbon composite material. - Thus, the
movable clutch plate 32 defines within thetorque converter casing 12 twochambers plate 32 constitutes a piston, in such a way that, according to the prevailing oil pressure in each of these chambers, theclutch plate 32 is urged axially in one or other direction. Thus, when thefirst chamber 44, which is defined between themovable clutch plate 32 and theproximal wall 42 which carries thereaction surface 40, is supplied with fluid under pressure, themovable clutch plate 32 is pushed axially in a direction such as to cause thebridging clutch 30 to be disengaged. Conversely, when thesecond chamber 46 of thecasing 12, defined between theclutch plate 32 and thedistal wall 16 and, as shown in FIG. 1, also containing the torque converter itself, is supplied with fluid under pressure, theclutch plate 32 is displaced axially in a direction such as to cause theclutch 30 to be engaged. - Reference is now made to FIGS.4 to 9, showing three different versions of a
friction liner 38 incorporating features of the invention. Theseliners 38 are in the form of flat annular plate elements having an axis A1 and atransverse fastening face 48, by means of which they are fastened, for example, on themovable clutch plate 32, together with an opposed annular transverse face, or friction surface, 50 which makes the frictional contact against thereaction surface 40, FIGS. 1 to 3, of thecasing 12. As can be seen in FIGS. 4 to 9, thefriction surface 50 is formed with a network of grooves which enable oil to circulate between thefriction liner 38 and thereaction surface 40, especially for cooling purposes. - This network of grooves is not open radially towards the outside of the
liner 38. Thus, theliner 38 comprises a peripheralouter ring portion 52 which is solid and which has a transverse surface, constituting part of thefriction surface 50, which is continuous over the whole periphery of the liner. Instead, the grooves which constitute the above mentioned network of grooves are open radially in only the innerperipheral edge 62 of theannular friction liner 38. These grooves can be made, in particular, either by moulding or by machining. - With reference to FIGS. 2 and 3, these Figures show diagrammatically the contact between the
friction liner 38 against thereaction surface 40. In this connection, due to the mode of actuating of the bridgingclutch 30, which is urged towards its engaged position by an excess of pressure in thechamber 46 as compared with that in thechamber 44, the movableclutch plate 32 tends to deform, due mainly to the contact force applied between the central sleeve 26 (FIG. 1) and the movableclutch plate 32 in the region of itsinternal flange 34. - This being so, and as is shown most particularly in FIG. 3, the movable
clutch plate 32 tends to deform in such a way that theliner 38 makes its initial contact with thereaction surface 40 through the outer peripheral edge 51 (FIG. 4) of theouter ring portion 52 of the liner. Subsequently, under the effect of pressure, the contact between theliner 38 and thereaction surface 40 spreads over the whole of thefrictional contact surface 50 of the liner, as can be seen in FIG. 2. - However, the use of a liner having a network of grooves which are not open radially outwardly enables the outer
peripheral ring portion 52 of theliner 38 to form a seal once thering portion 52 has made initial contact with thereaction surface 40. This seal tends to prevent any loss of oil between thefriction surface 50 of theliner 38 and thereaction surface 40, and this improves transmission of the torque. - However, if the bridging
clutch 30 is controlled in such a way as to slip on thereaction surface 40, that is to say if the excess pressure in thechamber 46 of thecasing 12 is moderated, the contact pressure between thereaction surface 40 and theliner friction surface 50 is reduced in such a way that a slight flow of oil will be able to pass between the twosurfaces liner 38, and which limit the radial distance over which thering portion 52 tends to provide sealing. - As to the form of the network of grooves in the
liner 38, reference is made once again to FIGS. 4 to 9 which show three different versions of this network. - In the first version shown in FIGS. 4 and 5, the liner has essentially two concentric
circular grooves radial grooves 58 regularly spaced apart circumferentially. In addition, furtherradial grooves 60, again spaced apart at regular intervals, are open firstly into the innercircular groove 54 and secondly in theinner edge 62 of theliner 38. In this embodiment, theradial grooves 58 formed between the twocircular grooves radial grooves 60 which extend between the innercircular groove 54 and theinner edge 62. - In the second embodiment which is shown in FIGS. 6 and 7, the
liner 38 has asingle spiral groove 64 and a set ofradial grooves 66 which are open in theinner edge 62 of theliner 38. Theradial grooves 66 intersect thespiral groove 64 at several points as shown. - In the third embodiment shown in FIGS. 8 and 9, the
liner 38 has asingle groove 68 which is elliptical, centred on the axis A1 of theliner 38. The major axis A2 of the ellipse is shorter than the outer diameter of the liner.Radial grooves 70 provide communication between theelliptical groove 68 and theinternal edge 62 of theliner 38. - As can be seen most particularly in FIGS. 7 and 9, the depth of the
various grooves liner 38. - These various embodiments of the invention show that the grooves may take a number of very different forms, so that the invention is not limited to those described above by way of example. Thus for example, it is possible to form radial grooves which are substantially developments of a circle.
- In general terms, the various geometries proposed for the network of grooves in the
friction liner 38 enable the torque that can be transmitted by the bridgingclutch 30 to be increased, while at the same time limiting heating of theliner 38 and heating of the oil when the clutch 30 is in a slipping mode. - In addition, the invention is not limited to the use of a single friction liner. The
liner 38 can, in this connection, cooperate with a further liner carried by the reaction surface.
Claims (5)
1. A friction liner for a torque converter bridging clutch having a reaction surface, the liner being annular and having a radially outer edge, a radially inner edge, and an annular friction surface for engagement with a cooperating said reaction surface, the friction surface defining a network of grooves therein for circulation of a liquid between the liner and said reaction surface, wherein the network of grooves comprise concentric circular grooves, first radial grooves spaced apart circumferentially and joining said concentric circular grooves together, and second radial grooves open into an inner one of said circular groove, said second radial grooves being also open at the inner edge of the liner, the said first radial grooves and second radial grooves being offset circumferentially with respect to each other, communication between the various grooves and the outer edge of the liner being absent.
2. A friction liner for a torque converter bridging clutch having a reaction surface, the liner being annular and having a radially outer edge, a radially inner edge, and an annular friction surface for engagement with a cooperating said reaction surface, the friction surface defining a network of grooves therein for circulation of a liquid between the liner and said reaction surface, wherein communication between the network of grooves and the outer edge of the liner is absent, and wherein the network of grooves comprises a spiral groove and a set of radial grooves open at the inner edge of the liner and intersecting the spiral groove at several points.
3. A friction liner for a coupling device having a reaction surface, the liner being annular and having a radially outer edge, a radially inner edge, and an annular friction surface for cooperating engagement with a said reaction surface, the liner defining a network of grooves in said friction surface for circulation of a liquid between the liner and said reaction surface, wherein communication between the network of grooves and the outer edge of the liner is absent, the network of grooves consisting of a single elliptical groove concentric with the liner and having a major axis shorter than the diameter of the outer edge of the liner, the network further comprising radial grooves joining the elliptical groove with the inner edge of the liner.
4. A liner according to any one of to , wherein said grooves have a depth substantially equal to one half of the axial thickness of the liner.
claims 1
3
5. A liner according to any one of to , made of a composite material including carbon.
claims 1
3
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/785,644 US6290046B2 (en) | 1996-07-18 | 2001-02-16 | Friction liner having a network of grooves, for a clutch |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR96.09194 | 1996-07-18 | ||
FR9609194A FR2751386B1 (en) | 1996-07-18 | 1996-07-18 | FRICTION LINING FOR A CLUTCH WITH A NETWORK OF GROOVES |
US09/415,982 US6213273B1 (en) | 1996-07-18 | 1999-10-12 | Friction liner having a network of grooves, for a clutch |
US09/785,644 US6290046B2 (en) | 1996-07-18 | 2001-02-16 | Friction liner having a network of grooves, for a clutch |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/415,982 Division US6213273B1 (en) | 1996-07-18 | 1999-10-12 | Friction liner having a network of grooves, for a clutch |
Publications (2)
Publication Number | Publication Date |
---|---|
US20010006136A1 true US20010006136A1 (en) | 2001-07-05 |
US6290046B2 US6290046B2 (en) | 2001-09-18 |
Family
ID=9494332
Family Applications (3)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US08/896,214 Expired - Fee Related US6035992A (en) | 1996-07-18 | 1997-07-17 | Friction liner having a network of grooves, for a clutch |
US09/415,982 Expired - Lifetime US6213273B1 (en) | 1996-07-18 | 1999-10-12 | Friction liner having a network of grooves, for a clutch |
US09/785,644 Expired - Lifetime US6290046B2 (en) | 1996-07-18 | 2001-02-16 | Friction liner having a network of grooves, for a clutch |
Family Applications Before (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US08/896,214 Expired - Fee Related US6035992A (en) | 1996-07-18 | 1997-07-17 | Friction liner having a network of grooves, for a clutch |
US09/415,982 Expired - Lifetime US6213273B1 (en) | 1996-07-18 | 1999-10-12 | Friction liner having a network of grooves, for a clutch |
Country Status (7)
Country | Link |
---|---|
US (3) | US6035992A (en) |
EP (1) | EP0819863B1 (en) |
JP (1) | JPH1068458A (en) |
KR (1) | KR980010013A (en) |
DE (1) | DE69716183T2 (en) |
ES (1) | ES2184934T3 (en) |
FR (1) | FR2751386B1 (en) |
Cited By (2)
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US20060065504A1 (en) * | 2004-09-30 | 2006-03-30 | Schultz John C | Dual clutch engine coupling damper |
CN100453839C (en) * | 2004-09-30 | 2009-01-21 | 通用汽车环球科技运作公司 | Dual clutch engine coupling damper |
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FR2783298B1 (en) * | 1998-09-10 | 2001-02-09 | Valeo | HYDROKINETIC COUPLING APPARATUS WITH COOLING GROOVE |
DE10008167A1 (en) * | 2000-02-23 | 2001-08-30 | Zahnradfabrik Friedrichshafen | Friction clutch |
DE10238122B4 (en) * | 2002-08-21 | 2012-03-29 | Zf Sachs Ag | Hydrodynamic coupling device, in particular hydrodynamic torque converter |
EP1473478A1 (en) * | 2003-04-29 | 2004-11-03 | BorgWarner, Inc. | Fluid flow groove arrangement on a friction material |
US7014024B2 (en) * | 2003-06-11 | 2006-03-21 | Sulzer Euroflamm Us Inc. | System and method for improving cooling in a friction facing environment |
US20060236523A1 (en) * | 2003-10-02 | 2006-10-26 | Sulzer Euroflamm Us Inc | Friction facing method for use in a friction environment |
US7168544B2 (en) * | 2003-10-02 | 2007-01-30 | Sulzer Euroflamm Us Inc. | Friction facing material for use in a friction environment |
US7069636B2 (en) * | 2003-10-02 | 2006-07-04 | Euroflamm Select Inc. | Friction facing method for use in a friction environment |
JP4781792B2 (en) * | 2005-11-25 | 2011-09-28 | Nskワーナー株式会社 | Lock-up clutch |
JP2007146927A (en) * | 2005-11-25 | 2007-06-14 | Nsk Warner Kk | Lock-up clutch |
US20070270069A1 (en) * | 2006-05-18 | 2007-11-22 | Sulzer Euroflamm Us Inc. | Friction material and system and method for making the friction material |
JP4979295B2 (en) * | 2006-07-31 | 2012-07-18 | Nskワーナー株式会社 | Lock-up clutch mechanism |
WO2008055457A2 (en) * | 2006-11-06 | 2008-05-15 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Clutch assembly, and force transmission device comprising a clutch assembly |
EP2185833B1 (en) * | 2007-08-15 | 2012-01-04 | BorgWarner Inc. | Frictional part with a zig-zag or undulating circumferential groove in the frictional surface |
JP4840458B2 (en) * | 2009-02-12 | 2011-12-21 | トヨタ自動車株式会社 | Wet friction plate |
WO2011111117A1 (en) * | 2010-03-12 | 2011-09-15 | トヨタ自動車株式会社 | Lock-up clutch |
KR101298269B1 (en) * | 2011-10-26 | 2013-08-22 | 한국파워트레인 주식회사 | Torque converter for vehicle |
US9624984B2 (en) * | 2015-01-15 | 2017-04-18 | Allison Transmission, Inc. | Startup clutch lubrication system and method thereof |
USD802723S1 (en) * | 2015-11-27 | 2017-11-14 | Ebara Corporation | Sealing ring |
EP3318776B1 (en) * | 2016-11-07 | 2021-09-22 | Ratier-Figeac SAS | Rotating no-back brake system |
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-
1996
- 1996-07-18 FR FR9609194A patent/FR2751386B1/en not_active Expired - Lifetime
-
1997
- 1997-07-09 ES ES97111606T patent/ES2184934T3/en not_active Expired - Lifetime
- 1997-07-09 DE DE69716183T patent/DE69716183T2/en not_active Expired - Lifetime
- 1997-07-09 EP EP97111606A patent/EP0819863B1/en not_active Expired - Lifetime
- 1997-07-16 KR KR1019970033056A patent/KR980010013A/en not_active Application Discontinuation
- 1997-07-17 US US08/896,214 patent/US6035992A/en not_active Expired - Fee Related
- 1997-07-18 JP JP9193660A patent/JPH1068458A/en active Pending
-
1999
- 1999-10-12 US US09/415,982 patent/US6213273B1/en not_active Expired - Lifetime
-
2001
- 2001-02-16 US US09/785,644 patent/US6290046B2/en not_active Expired - Lifetime
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20060065504A1 (en) * | 2004-09-30 | 2006-03-30 | Schultz John C | Dual clutch engine coupling damper |
US7401687B2 (en) * | 2004-09-30 | 2008-07-22 | Gm Global Technology Operations, Inc. | Dual clutch engine coupling damper |
CN100453839C (en) * | 2004-09-30 | 2009-01-21 | 通用汽车环球科技运作公司 | Dual clutch engine coupling damper |
Also Published As
Publication number | Publication date |
---|---|
EP0819863B1 (en) | 2002-10-09 |
EP0819863A1 (en) | 1998-01-21 |
US6035992A (en) | 2000-03-14 |
US6290046B2 (en) | 2001-09-18 |
FR2751386A1 (en) | 1998-01-23 |
DE69716183D1 (en) | 2002-11-14 |
DE69716183T2 (en) | 2003-06-12 |
KR980010013A (en) | 1998-04-30 |
US6213273B1 (en) | 2001-04-10 |
FR2751386B1 (en) | 1998-09-18 |
JPH1068458A (en) | 1998-03-10 |
ES2184934T3 (en) | 2003-04-16 |
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