GB1586522A - Creación de Inventos y Patentes con Inteligencia Artificial

GB1586522A – Multiple-disc torque transmission device
– Google Patents

GB1586522A – Multiple-disc torque transmission device
– Google Patents
Multiple-disc torque transmission device

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Publication number
GB1586522A

GB1586522A
GB46878/77A
GB4687877A
GB1586522A
GB 1586522 A
GB1586522 A
GB 1586522A
GB 46878/77 A
GB46878/77 A
GB 46878/77A
GB 4687877 A
GB4687877 A
GB 4687877A
GB 1586522 A
GB1586522 A
GB 1586522A
Authority
GB
United Kingdom
Prior art keywords
discs
pressure disc
piston
stop
disc
Prior art date
1976-11-16
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.)

Expired

Application number
GB46878/77A
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.)

ETUDES ET RECHERCHES AVANCEES

Original Assignee
ETUDES ET RECHERCHES AVANCEES
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
1976-11-16
Filing date
1977-11-10
Publication date
1981-03-18

1977-11-10
Application filed by ETUDES ET RECHERCHES AVANCEES
filed
Critical
ETUDES ET RECHERCHES AVANCEES

1981-03-18
Publication of GB1586522A
publication
Critical
patent/GB1586522A/en

Status
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

F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES

F16D13/00—Friction clutches

F16D13/22—Friction clutches with axially-movable clutching members

F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs

F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member

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

F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes

F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member

F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action

F16D55/36—Brakes with a plurality of rotating discs all lying side by side

F16D55/40—Brakes with a plurality of rotating discs all lying side by side actuated by a fluid-pressure device arranged in or one the brake

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL

F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES

F16D25/00—Fluid-actuated clutches

F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch

F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces

F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially

F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs

F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae

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

F16D65/00—Parts or details

F16D65/02—Braking members; Mounting thereof

F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor

F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes

F16D65/095—Pivots or supporting members therefor

F16D65/097—Resilient means interposed between pads and supporting members or other brake parts

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

F16D65/00—Parts or details

F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position

F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake

F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes

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

F16D65/00—Parts or details

F16D65/78—Features relating to cooling

F16D65/84—Features relating to cooling for disc brakes

F16D65/853—Features relating to cooling for disc brakes with closed cooling system

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

F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES

F16D2121/00—Type of actuator operation force

F16D2121/02—Fluid pressure

F16D2121/04—Fluid pressure acting on a piston-type actuator, e.g. for liquid pressure

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

F16D2125/00—Components of actuators

F16D2125/02—Fluid-pressure mechanisms

F16D2125/04—Cylinders

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

F16D2125/00—Components of actuators

F16D2125/02—Fluid-pressure mechanisms

F16D2125/06—Pistons

Description

PATENT SPECIFICATION
2 ( 21) Application No 46878/77 ( 22) Filed 10 Nov 1977 s ( 31) Convention Application No 7 634 451 U ( 32) Filed 16 Nov 1976 in C ( 33) France (FR) M ( 44) Complete Specification published 18 March 1981 ( 51) INT CL 3 F 16 D 55/40, 13/52 ( 52) Index at acceptance F 2 E 2 N 2 A 2 A 2 N 2 D 2 B 2 N 2 E 5 DF F 2 C 1 C 12 B 1 C 4 B 2 1 C 9 B 2 1 C 9 B 6 1 E 7 ( 11) 1586522 ( 19 ( 54) A MULTIPLE-DISC TORQUE TRANSMISSION DEVICE ( 71) We, ETUDES ET RECHERCHES AVANCEES, a Company organized under the laws of France, of Rue Baroin, 42000 Saint Etienne, France, do hereby dedare the invention, for which we pray that a Patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement: –
The present invention relates to a multiple friction-disc torque transmission device, such as a brake or a dutch.
In these transmission devices, whether used as brakes or clutches, the thurst force necessary for the compression of the disc increases in proportion as these latter come into contact and it frequently happens that the force exerted on the discs most distant from the control means for moving the discs to press them axially together is insufficient.
According to this invention there is provided a multiple-disc torque transmission device comprising a first stack of axially movable discs locked in rotation with a first body, a second stack of axially movable discs locked in rotation with a second body, the discs of the first stack being intercalated between the discs of the second stack and one of the two bodies being free to rotate in relation to the other, and control means for axially moving the discs of both stacks so as to compress them against each other, which two stacks of discs are axially separated into two groups by an axially movable intermediate pressure disc, one of these groups being axially disposed between the intermediate pressure disc and a stop on one of the two bodies, and the second group being axially disposed between the intermediate pressure disc and an axially movable end pressure disc, the control means being adapted to exert axial forces in the direction of the stop, which forces operate on both of said pressure discs so as initially to take up the clearance between the discs of the first group, then subsequently on the end pressure disc so as to take up the clearances between the discs of the second group, and finally on both of said pressure discs so as to compress the discs of both of said groups.
With these arrangements the discs of the two groups are now brought into contact before being compressed It will be readily understood that at the moment of their compression the thrust force is more uniformly exerted on each of them, which improves the efficiency of the device.
Preferably, said pressure discs are axially movably mounted on the body carrying the stop, which body is disposed within the other body and is fixed, said other body being free to rotate.
According to a particular embodiment of this brake, the control means comprises sets of concentric pistons disposed parallel to the axis of the pressure discs and equiangularly spaced from each other in a circular member secured to the fixed body, which member is located behind the end pressure disc, concentric piston comprising a central piston the body of which bears against the end pressure disc and which has a smaller section axial extension extending through the end pressure disc and the fixed discs of the second group and bearing against the intermediate pressure disc an intermediate annular piston surrounding the body of the central piston and bearing, at the rear, against a shoulder of the central piston, and an outer annular piston surrounding the intermediate piston, these pistons being actuated by a pressurised fluid, the arrangement being such that the fluid first actuates simultaneous movement of the central piston and the intermediate piston, then movement of the intermediate piston alone and finally movement of the outer annular piston alone.
It is to be noted that the central and intermediate pistons have small diameters, which allows the discs of the first and then of the second group to be brought rapidly into contact.
In one construction according to the invention the control means exerts a force in the direction of the stop against that exerted by two series of return springs fitted on parallel rods passing through the assembly of fixed discs and extending between the stop and the end pressure disc, the return springs of one 1,586,522 series bearing against the stop and the opposing face of the intermediate pressure disc, whereas those of the other series, which are less stiff, bear against the opposing faces of the two pressure discs.
With this arrangement, the intermediate and end pressure discs can return to their initial position as soon as the control means releases the discs The separation of the discs can then take place more rapidly.
In another construction according to the invention the control means comprises a ring piston bearing against the end pressure disc, this ring piston being accommodated in an annular recess in a member fixed with respect to the fixed body, which member is located behind the end pressure disc, parallel rods extending through the assembly of fixed discs and extending between the end pressure disc and the stop in relation to which the rods are axially movable, said rods having a larger section at their part located inside the pressure discs, washers fitted on the rods and applied against the faces of the pressure discs, and two series of springs surrounding the rods, the springs of the first series bearing against the stop of the fixed body and the washer applied to the opposing face of the intermediate pressure disc, and those of the second series, which are stiffer, bearing against the washers applied to opposing faces of the two pressure discs respectively, the annular recess being connectable to a source of pressurised fluid for moving the ring against the force exerted by the springs.
When the ring piston is operated by the pressurised fluid, it in its turn pushes the end pressure disc and the washers applied against that disc Now, since the springs of the second series are stiffer than those of the first series, they are not immediately compressed but control the movement of the intermediate pressure disc, which allows the bringing into contact of the discs of the first group Then, when this first approach phase is achieved, the end pressure disc moves in its turn during the compression of the springs of the second series, which allows the discs of the second group to be brought into contact Compression of the complete assembly of discs takes place immediately after the completion of this second approach phase.
It is to be noted that the difference in the stiffness of the springs contributes to the separation of the discs during releasing.
Two embodiments of the present invention are shown by way of example in the accompanying drawings in which:
Figure 1 is an axial sectional view of a multiple-disc brake of the invention, Figure 2 is a sectional view along line II-II of Figure 1, Figures 3 to 6 are partial schematical sections showing the operation of the control means provided for moving the discs of the brake shown in Figures 1 and 2, Figure 7 is an axial sectional view of a second embodiment according to the invention, Figure 8 is a partial sectional view showing resilient rings for distributing the total clearance among the discs, and Figure 9 is a fragmentary diagrammatic view illustrating oil passage-ways formed on the stop.
The disc brake in Figures 1 and 2 is shown mounted on a wheel-hub 1 rotatable on bearings 4 on a banjo casing 2 and a crown wheel support 3 forming part of a differential (not shown) The brake comprises a first stack of discs 5 locked, in rotation, with a drum 6 secured by bolts 7 on the hub but slidable axially on the drum, a second stack of discs 8 interposed between discs 5 and locked, in rotation, with a body 9 secured on the banjo casing, but slidable axially on body 9 and control means 10 for axially moving the discs of both stacks so as to compress them against each other.
The two stacks of discs form two subassemblies separated by an intermediate pressure disc 11 locked in rotation with body 9, but axially slidable on the body The first of these sub-assemblies is located between pressure disc 11 and a stop 12 fixed on body 9, whereas the second is located between said disc 11 and a pressure disc 13 also locked in rotation with, but axially slidable on, body 9.
The control means 10 comprises sets of concentric pistons disposed parallel to the axis of the disc assembly and evenly distributed about that axis in a member 14 fixed on body 9, behind the end pressure disc 13 105 Referring to Figures 1 and 3, each set of concentric pistons comprises a central piston having a shoulder bearing against pressure disc 13 and having an axial extension 16 of smaller diameter extending through pres 110 sure disc 13 and discs 8 and abutting pressure disc 11, an intermediate annular piston 17 surrounding the body of the central piston and engaged by a shoulder 18 thereon and an outer annular piston 19 surrounding the 115 intermediate piston 17.
These concentric pistons define chambers, respectively 15 a, 17 a and 19 a, connectable in succession to a pressurised fluid source so as to be successively advanced in the direc 120 tion of stop 12 In the illustrated construction movement of piston 15 relative to member 14 from their initial positions places chamber 15 a in communication with chamber 17 a, and axial movement of piston 17 125 relative to member 14 places chamber 19 a in communication with chamber 17 a.
The pistons move against the force exerted by two series of springs 20, 21 which are fitted on parallel rods 22 extending through 130 1.586,522 3 pressure disc 11 and the assembly of discs 8 and bear, with their ends, on stop 12 and pressure disc 13 In the example shown, springs 20 bear against the stop 12 and the facing surface of pressure disc 13, whereas springs 21, which are less stiff, bear against the opposing faces of the pressure discs 11 and 13.
The operation of the brake illustrated in Figures 1 and 2 will now be described with reference to Figures 3 to 6.
Initially (see Figure 3) discs 5 and 8 are separated from each other by suitable clearances When chamber 15 a is connected to the pressurised fluid source, piston 15 moves towards stop 12 taking with it the intermediate pressure disc 11, piston 17 and the outer pressure disc 13 Since the distance between the pressure discs 11 and 13 remains unaltered, discs 5 and 8 disposed therebetween move axially but the sum of the clearances provided between them keeps the same value, but when piston 15 has moved sufficiently to allow the connection between chambers 15 a and 17 a, as shown in Figure 4, piston 17 moves leftward relative to piston 15 and the distance separating the pressure discs 11 and 13 diminishes so that the discs 5 and 8 located between these two members come closer together and then into contact when piston 17 occupies the position shown in Figure 5, the connection between chamber 17 a and 19 a being in its turn achieved in this position In consequence, piston 19 is pushed against pressure disc 13, as shown in Figure 6, which allows it to exert the final compression of the assembly of discs 5 and 8.
Thus, the final compression takes place after two successive approach phases in which the discs, owing to the small diameters of pistons 15 and 17, are brought rapidly into contact and under the action of a limited pressure It will be appreciated that the pressure is uniformly exerted on all the discs whatever the final positions of the pistons.
If now the fluid supply to the pistons is cut off springs 20, which are stiffer, are the first to exert their action and cause the recoil of pressure disc 11 which, in its turn, pushes back all the movable members behind it.
Discs 5 and 8 located between stop 12 and pressure disc 11 can thus return to their initial position with their initial clearances.
Springs 21 now exert their action and push back disc 13 allowing the discs 5 and 8 which are still pressed against both pressure discs to come back, in their turn, to their initial position.
It should be noted that after release of discs 5 and 8, the residual clearances may be evenly restored by using resilient rings 23 as those shown in Figure 8 These rings, which are fitted on rods 24 passing through discs 8 and bearing, at their ends, on stop 12 and pressure disc 13, recover their initial thickness when the axial compression is removed so as to space discs 5 and 8.
The disc brake shown in Figure 7 differs from that shown in Figures 1 and 2 only by 70 its control means 10 In the construction of Figures 7 the control means 10 comprises a ring 25 bearing against pressure disc 13 and housed in an annular recess 26 formed in a member 27 secured to body 9 Parallel 75 rods 28 equiangularly spaced around body 9 extend through discs 8 to bear on stop 12 and pressure disc 13, and their parts located inside the pressure discs have an increased diameter Washers 29 are fitted on rods 28 80 and abut the faces of the pressure discs, and two series of springs 30 and 31 surround the rods, springs 30 bearing on stop 12 and the washers facing this latter, whilst springs 31, which are stiffer, bear against the washers 85 resting on the opposing faces of the two pressure discs.
So that ring 25 may move in the direction of stop 12, the bottom of the recess 26 is connectable through passageways 32 and 90 33 to a source of pressurised fluid When the pressurised fluid is fed to recess 26, ring 25 pushes against pressure disc 13 and its abutting washers Springs 31, which are stiffer than springs 30, are not compressed at first, 95 so that the pressure disc 11 moves in the direction of the stop Disc 11 then compresses springs 30, thus allowing discs 5 and 8 located in front of it to be brought into contact with each other Then, as the ring continues to 100 move, springs 31 are compressed in their turn, allowing pressure disc 13 to come nearer to pressure disc 11 and causing discs 5 and 8 located therebetween also to be brought into contact When this phase is completed, the 105 ring finally exerts its action on the whole assembly of discs 5 and 8 for the final compression.
Conversely, when the connection between recess 26 and the pressurised fluid source 110 is interrupted, springs 31 relax before springs 30, allowing discs 5 and 8 located between compression discs 11 and 13 to come back to their initial position before the others.
It will be evident that, after release of 115 discs 5 and 8, the original clearances can be spread uniformly by using resilient rings such as those described above with reference to Figure 8.
It will be noted moreover that in both 120 embodiments considered here, discs 5 and 8 are disposed in an oil circuit comprising troughs 34 formed in the inner wall of drum 6 and opening slightly behind a deflector 35 fixed on the front face of stop 12 The de 125 flector serves to direct oil, conveyed by the troughs in the space enclosing discs 5 and 8, towards curved passageways 36 in said front face of the stop (see Figure 9), then towards an annular channel 37 defined by the body 130 1,586,522 1,586,522 9 and hub 1 This latter is provided with helical grooves 38 promoting the advance of the oil in the channel, whilst bores 39 formed in body 9 bring back the oil from the channel into the space enclosing discs 5 and 8.
During rotation of drum 6, discs 5 and 8 are then constantly bathed in an oil flow, which allows the brake to operate in the best conditions.
It will be apparent to those skilled in the art that the discs can if desired be axially separated into more than two groups.

Claims (8)

WHAT WE CLAIM IS: –

1 A multiple-disc torque transmission device comprising a first stack of axially movable discs locked in rotation with a first body, a second stack of axially movable discs locked in rotation with a second body, the discs of the first stack being intercalated between the discs of the second stack and one of the two bodies being free to rotate in relation to the other, and control means for axially moving the discs of both stacks so as to compress them against each other, which two stacks are axially separated into two groups by an axially movable intermediate pressure disc, one of these groups being axially disposed between the intermediate pressure disc and a stop on one of the two bodies, and the second group being axially disposed between the intermediate pressure disc and an axially movable end pressure disc, the control means being adapted to exert axial forces in the direction of the stop, which forces operate on both of said pressure discs so as initially to take up the clearances between the discs of the first group, then subsequently on the end pressure disc so as to take up the clearances between the discs of the second group, and finally on both of said pressure discs so as to compress the discs of both of said groups.

2 A device according to claim 1, wherein said pressure discs are axially movably mounted on the body carrying the stop, which body is disposed within the other body and is fixed, said other body being free to rotate.

3 A device according to claim 2, wherein the control means comprises sets of concentric pistons disposed parallel to the axis of the pressure discs and equiangularly spaced from each other in a circular member secured to the fixed body, which member is located behind the end pressure disc, each concentric piston comprising a central piston the body of which bears against the end pressure disc and which has a smaller section axial extension extending through the end pressure disc and the fixed discs of the second group and bearing against the intermediate pressure disc, an intermediate annular piston surrounding the body of the central piston and bearing, at the rear, against a shoulder of the central piston, and an outer annular piston surrounding the intermediate piston, 65 these pistons being actuated by a pressurised fluid, the arrangement being such that the fluid first actuates simultaneous movement of the central piston and the intermediate piston, then movement of the intermediate 70 piston alone and finally movement of the outer annular piston alone.

4 A device according to claim 2, wherein the control means exerts a force in the direction of the stop against that exerted by two 75 series of return springs fitted on parallel rods passing through the assembly of fixed discs and extending between the stop and the end pressure disc, the return springs of one series bearing against the stop and the opposing 80 face of the intermediate pressure disc, whereas those of the other series, which are less stiff, bear against the opposing faces of the two pressure discs.

A device according to claim 2, wherein 85 the control means comprises a ring piston bearing against the end pressure disc, this ring piston being accommodated in an annular recess in a member fixed with respect to the fixed body, which member is located 90 behind the end pressure disc, parallel rods extending through the assembly of fixed discs and extending between the end pressure disc and the stop in relation to which the rods are axially movable, said rods having a larger 95 section at their part located inside the pressure discs, washers fitted on the rods and applied against the faces of the pressure discs, and two series of spring surrounding the rods, the springs of the first series bearing against 100 the stop of the fixed body and the washer applied to the opposing face of the intermediate pressure disc, and those of the second series, which are stiffer, bearing against the washers applied to opposing faces of the two 105 pressure discs respectively, the annular recess being connectable to a source of pressurised fluid for moving the ring against the force exerted by the springs.

6 A device according to any one of claims 110 2 to 5, further comprising axial rods bearing, at their ends, on the stop and on the end pressure disc, which rods extend through the fixed discs and carrying between adjacent discs, axially resiliently compressible rings 115 whose axial thickness is when uncompressed greater than that of the discs in the stacks.

7 A device according to any one of claims 2 to 6, wherein the two groups of discs are disposed in an oil circuit comprising troughs 120 formed in the inner wall of the rotary body, which troughs direct the oil, which is taken by the troughs from a space enclosing the discs, towards curved passageways formed in said face of the stop via a deflector, then 125 towards an annular channel defined by the fixed body and a cylindrical member fixed with respect to the rotary body, which member extends under the fixed body and has at 1,586,522 this location helical grooves for promoting the advance of the oil along the channel and thence through bores formed in the fixed body to bring the oil back to the space enclosing the discs.

8 A multiple disc torque transmission device substantially as hereinbefore described with reference to and as illustrated in Figures 1 to 6, 8 and 9 or in Figures 7 to 9 of the accompanying drawings.
STEVENS, HEWLETT & PERKINS, Chartered Patent Agents, 5, Quality Court, Chancery Lane, London WC 2 A 1 HZ, Agents for the Applicants.
Printed for Her Majesty’s Stationery Office by the Courier Press, Leamington Spa, 1981.
Published by the Patent Office, 25 Southampton Buildings, London, WC 2 A l AY, from which copies may be obtained.

GB46878/77A
1976-11-16
1977-11-10
Multiple-disc torque transmission device

Expired

GB1586522A
(en)

Applications Claiming Priority (1)

Application Number
Priority Date
Filing Date
Title

FR7634451A

FR2370890A1
(en)

1976-11-16
1976-11-16

MULTI-DISC TORQUE TRANSMISSION DEVICE IN OIL

Publications (1)

Publication Number
Publication Date

GB1586522A
true

GB1586522A
(en)

1981-03-18

Family
ID=9179962
Family Applications (1)

Application Number
Title
Priority Date
Filing Date

GB46878/77A
Expired

GB1586522A
(en)

1976-11-16
1977-11-10
Multiple-disc torque transmission device

Country Status (10)

Country
Link

US
(1)

US4144955A
(en)

BE
(1)

BE860531A
(en)

CA
(1)

CA1076391A
(en)

DE
(1)

DE2750231A1
(en)

ES
(1)

ES464077A1
(en)

FR
(1)

FR2370890A1
(en)

GB
(1)

GB1586522A
(en)

IT
(1)

IT1087973B
(en)

NL
(1)

NL7712592A
(en)

SE
(1)

SE422233B
(en)

Cited By (3)

* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

GB2337308A
(en)

1998-01-07
1999-11-17
Eaton Corp
Force transmitting assembly having multiple piston areas for variation of force magnitude

DE10334402B4
(en)

2002-08-02
2006-04-06
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Arrangement and method for torque transmission

CN103557253A
(en)

2013-10-09
2014-02-05
山东临工工程机械有限公司
Double-axis friction plate type brake clutch for planetary transmission with double-turbine torque converter

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1983-08-04
Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen

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1987-01-09
Renault

MULTIPLE DISC CLUTCH OR BRAKE WITH DISK SPREADING DEVICE

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General Motors Corporation
Plate separator

JPS6213849A
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1985-07-08
1987-01-22
Daikin Mfg Co Ltd
Control mechanism for speed change shift in automatic transmission

US6920971B2
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2003-04-17
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Caterpillar Inc
Cushioned hydraulic clutch/brake piston

DE10349905A1
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2003-10-25
2005-05-25
Zf Friedrichshafen Ag
Transmission with integrated brake for motor vehicle has brake plate carrier in communication with bowl-shaped element which during rotation of plate carrier receives lubricating fluid and transmits it to plates

AT8925U1
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2005-10-17
2007-02-15
Magna Drivetrain Ag & Co Kg

HYDRAULICALLY OPERATED LAMINATE COUPLING WITH WEAR ADJUSTMENT

DE102010019699B4
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2009-05-26
2021-07-29
Magna powertrain gmbh & co kg

Multi-disc clutch

JP6187359B2
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2014-03-31
2017-08-30
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Brake device for transmission

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2014-12-22
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Avl Powertrain Engineering, Inc.
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2015-02-27
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1976-11-16
FR
FR7634451A
patent/FR2370890A1/en
active
Granted

1977

1977-10-31
SE
SE7712261A
patent/SE422233B/en
not_active
IP Right Cessation

1977-11-03
IT
IT7729276A
patent/IT1087973B/en
active

1977-11-07
US
US05/849,470
patent/US4144955A/en
not_active
Expired – Lifetime

1977-11-07
CA
CA290A
patent/CA1076391A/en
not_active
Expired

1977-11-07
BE
BE182386A
patent/BE860531A/en
not_active
IP Right Cessation

1977-11-10
DE
DE19772750231
patent/DE2750231A1/en
not_active
Withdrawn

1977-11-10
GB
GB46878/77A
patent/GB1586522A/en
not_active
Expired

1977-11-11
ES
ES464077A
patent/ES464077A1/en
not_active
Expired

1977-11-15
NL
NL7712592A
patent/NL7712592A/en
not_active
Application Discontinuation

Cited By (4)

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Priority date
Publication date
Assignee
Title

GB2337308A
(en)

1998-01-07
1999-11-17
Eaton Corp
Force transmitting assembly having multiple piston areas for variation of force magnitude

GB2337308B
(en)

1998-01-07
2002-03-06
Eaton Corp
Force transmitting assembly

DE10334402B4
(en)

2002-08-02
2006-04-06
General Motors Corp., Detroit

Arrangement and method for torque transmission

CN103557253A
(en)

2013-10-09
2014-02-05
山东临工工程机械有限公司
Double-axis friction plate type brake clutch for planetary transmission with double-turbine torque converter

Also Published As

Publication number
Publication date

DE2750231A1
(en)

1978-05-24

BE860531A
(en)

1978-05-08

ES464077A1
(en)

1978-07-16

SE422233B
(en)

1982-02-22

SE7712261L
(en)

1978-05-17

IT1087973B
(en)

1985-06-04

US4144955A
(en)

1979-03-20

FR2370890B1
(en)

1979-04-06

FR2370890A1
(en)

1978-06-09

CA1076391A
(en)

1980-04-29

NL7712592A
(en)

1978-05-18

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