CN111795080B - Wet clutch mechanism including improved seal - Google Patents

Wet clutch mechanism including improved seal Download PDF

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Publication number
CN111795080B
CN111795080B CN201910444937.0A CN201910444937A CN111795080B CN 111795080 B CN111795080 B CN 111795080B CN 201910444937 A CN201910444937 A CN 201910444937A CN 111795080 B CN111795080 B CN 111795080B
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CN
China
Prior art keywords
seal
clutch mechanism
piston
support
wet clutch
Prior art date
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Application number
CN201910444937.0A
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Chinese (zh)
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CN111795080A (en
Inventor
D.费尼欧克斯
A.切龙
A.多尔
G.瓦罗夸奥克斯
J.鲍莱特
F.蒂鲍特
C.费里
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Valeo Embrayages SAS
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Valeo Embrayages SAS
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Publication of CN111795080A publication Critical patent/CN111795080A/en
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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
    • 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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • 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
    • F16D25/12—Details not specific to one of the before-mentioned types
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3232—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips
    • 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
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F16D2021/0661—Hydraulically actuated multiple lamellae clutches
    • 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
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/08—Details or arrangements of sealings not provided for in group F16D3/84

Landscapes

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

Abstract

The invention relates to a wet clutch mechanism (10) for a torque transmission system, comprising at least about an axis O: -a multi-disc assembly (E1, E2) consisting of friction discs (12, 22), -a torque input disc carrier (6) arranged to receive the multi-disc assembly, -a piston (40, 50) axially movable relative to the input disc carrier between an engaged position and a disengaged position, the piston being controllably displaced by a control chamber (32, 36), a balancing chamber (34, 38) being associated with the control chamber, the balancing chamber being defined in part by the piston (40, 50) and the input disc carrier (6), -elastic return means (60) arranged to return the piston to the disengaged position of the clutch mechanism, and wherein the balancing chamber is sealed by a sealing support (70).

Description

Wet clutch mechanism including improved seal
Technical Field
The present invention relates to a wet clutch mechanism comprising an improved seal at the balance chamber.
Background
Such wet clutch mechanisms are intended to form part of a torque transmission system, in particular for motor vehicles or for so-called industrial vehicles, such as trucks, public transportation vehicles or agricultural vehicles.
Patent application EP 2 909,052 A1 discloses a wet dual clutch mechanism for a motor vehicle comprising a torque input device for coupling to a crankshaft, a first torque output shaft, a second torque output shaft, a first clutch capable of coupling or uncoupling the torque input device and the first torque output shaft, and a second clutch capable of coupling or uncoupling the torque input device and the second torque output shaft. The first and second clutches, each of multiple discs, are radially disposed one above the other. Each multi-plate clutch includes a flange rotatably connected to an input plate carrier forming a torque input device and a friction plate rotatably connected to an output plate carrier. Each clutch further comprises an axially movable piston which is controlled to be displaced by means of a control chamber associated with a balancing chamber, which is delimited at least by a balancing cover.
Pressurized hydraulic fluid is supplied to the control chamber to allow the movable piston to displace between a first position corresponding to an engaged configuration of the clutch and a second position corresponding to a disengaged configuration of the clutch.
Instead, a so-called cooling hydraulic fluid is supplied to the balancing chamber, which allows lubricating the components of the clutch mechanism and compensating the axial forces generated by the movable piston.
The movable piston of the clutch mechanism is located in an intermediate position between the balance chamber and the control chamber, so it defines both chambers of the clutch mechanism. The balance chamber of the first clutch is formed by the input disc carrier and the movable piston and includes openings that allow leakage flow of cooling fluid, typically located in the lower portion of the balance chamber, therethrough. The leakage flow is oriented in the direction of the multi-plate clutch.
It is also necessary to ensure a sealed balance chamber at the junction of the movable piston and the input disc holder. The tightness of the balancing chamber is achieved in particular by means of a dynamic seal attached and vulcanized on an axially movable piston. The dynamic seal slides along a cylindrical bore formed directly in the input disc carrier. Such a configuration is known from document EP 2909 052 A1.
Disadvantages associated with this arrangement involve complex manufacture of the movable piston, for example obtained by stamping and multiple machining to adapt the piston to different clutch mechanisms. In practice, the piston is an adjusting member which is machined according to the other constituent parts of the clutch mechanism and the torque capacity to be transmitted by said clutch mechanism. The piston is a stamped plate member that includes an axial extension, typically in the form of an actuation finger, that exerts an axial force on the stack of flanges and friction discs to transmit drive torque within the clutch.
The torque to be transmitted at the clutch is defined by the number of friction discs forming the multi-plate assembly. Accordingly, the torque to be transmitted constrains the geometry of the axial extension of the piston. Thus, the greater the torque to be transferred, the greater the number of friction discs, and the need to reduce the axial extension of the piston to maintain an equal axial dimension. Accordingly, pistons are components whose geometry is rarely standardized to several applications of wet clutch mechanisms using the same input disc carrier.
The application of seals on pistons is therefore part of the background of complex industrialization, and it seems necessary to simplify the manufacturing process in order to better control the seals at the balancing chamber on the one hand and to reduce the manufacturing costs on the other hand. This is even more critical when the seal is obtained by overmolding directly onto the piston: such curing operations are typically performed by external partial contractors, which adds to the complexity of the industrialization.
Disclosure of Invention
The object of the present invention is to provide a simple, effective and economical solution to this problem, in particular.
It is an object of the present invention, inter alia, to provide a wet clutch mechanism for a torque transmitting system that allows to solve at least part of certain drawbacks of the prior art.
For this purpose, the invention proposes a wet clutch mechanism for a torque transmission system, in particular for a motor vehicle, comprising at least, about an axis O:
A multi-disc assembly consisting of a flange and a friction disc,
A torque input disc holder arranged to receive the multi-disc assembly,
A piston axially movable relative to said input disc carrier between an engaged position and a disengaged position of the clutch mechanism, the piston being controllably displaced by a control chamber associated with a balancing chamber defined in part by the piston and the input disc carrier,
-Elastic return means arranged to return the piston to the disengaged position of the clutch mechanism, and
The balancing chamber is partially sealed by a seal support, a first seal and a second seal, the seal support supporting the first seal and maintaining the second seal in a proper axial position relative to the balancing chamber,
The compression of the first seal is achieved by the axial force exerted by the resilient return means.
Such a wet clutch mechanism according to the present invention has the advantage of simplifying the manufacturing process of the piston, since the first and second seals are arranged on the seal support. The holding of the first seal in place within the wet clutch mechanism eliminates the need for complex assembly operations such as riveting or welding operations. The axial force of the elastic return means now ensures the positioning of the first seal and the sealing of the balancing chamber.
Preferably, the resilient return means applies an axial force between the input disc carrier and the piston, the resilient return means bringing the seal support against the input disc carrier or the piston. In this way, the axial force of the elastic return means prevents any rotation of the sealing support during its operation on the vehicle and ensures the sealing of the balancing chamber.
Advantageously, the seal support is a separate component from the input disc carrier and the piston. In this way, the material of the support may be chosen indistinguishable from the material of the input disc holder or the piston, and the geometry of the support may be more easily adapted to the type of seal used.
The invention may have one or the other of the following described features, taken in combination with or independently of each other:
The sealing support may be made of a plate, in particular a steel plate or an aluminium plate;
The sealing support may be made by stamping the plate;
the sealing support may be made by machining;
The seal support may comprise a radially extending bearing supporting the first seal and/or the second seal;
The seal support may comprise an axially extending bearing supporting the first seal and/or the second seal;
the radially extending bearing of the seal support may comprise an annular recess in which the first seal is inserted;
The elastic return means may comprise two support plates of annular shape and a series of helical springs distributed circumferentially between the two support plates;
one of the two support plates of the elastic return device can carry a second seal;
The elastic return means may comprise an annular elastic washer;
the elastic return means may comprise a wave washer;
the elastic return means may be supported on a radially extending support of the sealing support;
the elastic return means may be arranged outside the balancing chamber;
The elastic return means may be arranged radially outside the axially extending support;
the elastic return means may be arranged radially inside the axially extending support;
The first seal and the second seal may be separate;
the first seal and/or the second seal may be lip seals;
the first seal and/or the second seal may be an O-ring seal;
The first seal and/or the second seal may be directly overmolded onto the seal support, for example according to a vulcanization method;
the first seal and the second seal may be made in the form of a single identical seal directly over-molded on the seal support;
The sealing support may be shared with one of the annular bearing plates of the elastic return device;
The multi-plate clutch may include a flange rotatably connected to the input plate carrier and a friction plate rotatably connected to the output plate carrier.
According to a further aspect of the invention, the object of the invention is also a wet clutch mechanism which employs all or part of the above-mentioned features, and wherein the resilient return means bring the seal support against the input disc carrier, the first seal being compressed between the seal support and the input disc carrier.
Preferably, the sealing support is axially supported on the input disc carrier and is free to displace radially relative to the input disc carrier.
This further aspect of the invention has the advantage of simplifying the assembly of the wet clutch mechanism. The seal support and the first seal are simply placed on the input disc carrier and then compressed axially by placing the resilient return means in place. The holding of the first seal in place within the wet clutch mechanism eliminates the need for complex assembly operations such as riveting or welding operations. The risk of misalignment and concentricity defects along the axis O of the seal support relative to the piston are avoided.
Advantageously, the elastic return means can be interposed axially between the sealing support and the piston.
Preferably, the second seal is slidable on a cylindrical bearing provided on the piston.
The seal support may include rotation stop tabs circumferentially arranged around the radially extending support portion, which tabs are inserted into shaped stampings made in the disk carrier so as to completely avoid rotation of the seal support relative to the input disk carrier.
According to a further aspect of the invention, the object of the invention is also a wet clutch mechanism which employs all or part of the above-mentioned features, and wherein the elastic return means bring the seal support against the piston, the first seal being compressed between the seal support and the piston.
Preferably, the sealing support is axially supported on the piston and is free to displace radially relative to the piston.
This further aspect of the invention has the advantage of simplifying the assembly of the wet clutch mechanism. The seal support and the first seal are simply placed on the piston and then compressed axially by placing the resilient return means in place. The holding of the first seal in place within the wet clutch mechanism eliminates the need for complex assembly operations such as riveting or welding operations. The risk of misalignment and concentricity defects along the axis O of the seal support relative to the input disc holder are avoided.
Advantageously, the elastic return means may be interposed axially between the sealing support and the input disc holder.
The resilient return means may be supported directly on the input disc support. Alternatively, the elastic return means may be indirectly supported on the input disc carrier, in particular on a balancing cover attached to the input disc carrier.
Preferably, the second seal is slidable on a cylindrical support provided on the input disc carrier or on a balancing cover attached to a balancing chamber of the input disc carrier.
The seal support may comprise a rotation stop tab arranged circumferentially inside the radially extending bearing, said tab being inserted in a shaped stamping made in the piston, so as to completely avoid rotation of the seal support with respect to the piston.
According to another aspect of the present invention, the invention also relates to a wet double clutch mechanism for a torque transmission system, in particular for a motor vehicle, comprising, about an axis O:
a torque input disc carrier arranged to be rotatably connected to the drive shaft,
-A first clutch and a second clutch controlled to selectively couple the drive shaft to a first driven shaft and a second driven shaft, and arranged radially one above the other;
each clutch comprising a multi-disc assembly comprising a flange rotatably connected to an input disc carrier and a friction disc rotatably connected to an output disc carrier,
At least one of the clutches includes:
a piston axially movable relative to said input disc carrier between an engaged position and a disengaged position of the clutch, the piston being controllably displaced by a control chamber associated with a balancing chamber defined in part by the piston and the input disc carrier,
-Elastic return means arranged to return the piston to the disengaged position of the clutch, and
The balancing chamber is partially sealed by a seal support, a first seal and a second seal, the seal support supporting the first seal and maintaining the second seal in a proper axial position relative to the balancing chamber,
The compression of the first seal is achieved by the axial force exerted by the resilient return means.
In the context of a wet clutch mechanism according to the invention, the first clutch and/or the second clutch employ all or part of the features described above.
Drawings
The invention will be better understood by reading the following description, which is given by way of example only and with reference to the accompanying drawings, in which:
fig. 1 is an axial cross-sectional view of a wet dual clutch mechanism according to a first embodiment of the present invention;
FIG. 2 is an enlarged partial view of an axial section of the first embodiment of the invention of FIG. 1;
FIG. 3 is an isometric view of a single seal support according to the first embodiment of the invention of FIG. 1;
fig. 4 is an enlarged partial view of a wet dual clutch mechanism according to a second embodiment of the present invention;
fig. 5 is an enlarged partial view of a wet dual clutch mechanism according to a third embodiment of the present invention.
Detailed Description
In the following description and in the claims, the following terms are used in a non-limiting manner and for ease of understanding: the term "front" or "rear" is oriented with respect to the axial direction O and along a radial direction orthogonal to said axial direction O, along a direction with respect to the axial direction determined by the main rotation axis O of the transmission of the motor vehicle.
Fig. 1 to 3 show a first embodiment of a wet clutch mechanism 10 according to the invention. And more particularly to a wet dual clutch mechanism 10 having a primary axis of rotation O. The wet dual clutch mechanism 10 rotates within the transmission housing 100.
The wet dual clutch mechanism 10 for the torque transmission system 1 comprises at least one input element 2 about an axis O, which input element 2 is rotationally connected to a drive shaft (not shown). The input element 2 is located at the rear of the wet dual clutch mechanism 1.
In the first embodiment, the input member 2 having an L-shape as a whole includes a radially oriented portion formed by the input web 3 and an axially oriented portion formed by the hub 4. The input web 3 and the input hub 4 are joined, preferably by welding, together.
The hub 4 is arranged radially inward with respect to the input web 3.
The input hub 4 is rotationally connected, for example by means of splines 5, to the output of a damping device (for example a double flywheel damper or the like), the input of which is connected, in particular by means of a motor flywheel, to a drive shaft formed by a crankshaft which drives the motor of a motor vehicle equipped therewith.
The input web 3 comprises teeth 9 at the outer radial end of its axially oriented portion, the teeth 9 extending radially outwards and being supported on the input disc carrier 6 for inputting torque.
The wet double clutch mechanism 10 is controlled to selectively connect the drive shaft to the first driven shaft A1 and the second driven shaft A2.
Preferably, the first driven shaft A1 and the second driven shaft A2 are coaxial. The first driven shaft A1 is driven to rotate when the first clutch E1 is closed, and the second driven shaft A2 is driven to rotate when the second clutch E2 is closed, the first driven shaft A1 and the second driven shaft A2 being connected to a transmission equipped with a motor vehicle, respectively.
The wet double clutch mechanism 1 includes a first clutch E1 and a second clutch E2, which are multi-disc type, respectively.
The multi-plate assembly of the first clutch E1 includes a flange 11 rotatably connected to the input plate carrier 6 and a friction plate 12 rotatably connected to the output plate carrier 13. The friction disk 12 is uniformly interposed axially between two consecutive flanges 11.
The output disc carrier 13 of the first clutch E1 is rotatably connected to the friction disc 12 by engagement and to the first driven shaft A1 by spline connection.
The output disc holder 13 has an overall "L" shape with its inner radial end coupled to the output spline hub.
The multi-plate assembly of the second clutch E2 includes a flange 21 rotatably connected to the input plate carrier 6 and a friction plate 22 rotatably connected to the output plate carrier 23.
The output disc carrier 23 of the second clutch E2 is rotatably connected to the friction disc 22 by engagement and to the second driven shaft A2 by a spline connection.
The output disc holder 23 has an overall "L" shape with its inner radial end coupled to the output spline hub.
The input disc carrier 6 further comprises a cylindrical hub 7 with an axis of rotation O, an outer disc carrier 14 for the first clutch E1 and an inner disc carrier 24 for the second clutch E2.
The outer disc carrier 14 for the first clutch E1 comprises in particular an axial extension 15 and an annular portion 16, the axial extension 15 being arranged to receive the multi-disc assembly of the first clutch, the annular portion 16 extending radially inwards from the axial extension 15 along a plane perpendicular to the axis O.
The axial extension 15 forms an internal groove that receives the flange 11 of the multi-disc assembly of the first clutch.
The inner disc carrier 24 for the second clutch E2 comprises an axial extension 25, the axial extension 25 being arranged to receive the multi-disc assembly of the second clutch. The inner disc support 24 has an annular shape. The axial extension 25 forms an external groove that receives the flange 21 of the multi-disc assembly of the second clutch.
As shown in fig. 1, the inner disc support 24 is attached and rotationally coupled to the annular portion 16 of the outer disc support 14.
The cylindrical hub 7 is common to the first clutch E1 and the second clutch E2. The cylindrical hub 7 is inserted into a hole provided in the transmission housing 100.
As shown in fig. 1, the first clutch E1 is disposed radially above the second clutch E2.
Preferably, the first clutch E1 and the second clutch E2 are in an open state, also referred to as "normally open", and are selectively actuated in operation by a control device (not shown) contained in the transmission housing 100 to transition from an open state to a closed state.
The wet dual clutch mechanism 1 is hydraulically controlled by a pressurized fluid, typically oil.
To selectively control the state change of the first clutch E1 and the second clutch E2 between the disengaged position and the engaged position, the pressurized oil supply of the device management mechanism 10 is controlled. The control device is connected to a cylindrical hub 7, the cylindrical hub 7 comprising oil supply channels 71a, 71b and 71c, the number of which is for example three, as shown in fig. 1.
Passages 71a, 71c axially at the front and rear ends of the cylindrical hub 7 are associated with the control chamber 32 of the first clutch E1 and the control chamber 36 of the second clutch E2, respectively. The passage 71b axially between the passages 71a, 71c is associated with the balance chamber 34 of the first clutch E1 and the balance chamber 38 of the second clutch E2, respectively.
The first clutch E1 of the multiple disk type comprises a piston 40, the piston 40 being axially movable here from front to rear between a disengaged position and an engaged position, which correspond to the open and closed states of the first clutch E1, respectively.
Advantageously, the piston 40 comprises at its outer radial end an axially rearward extending support 41. The support 41 is supported on the end flange 12 of the multi-disc assembly of the first clutch E1. In the example shown in fig. 1, the support 41 is discontinuous.
The control chamber 32 of the piston 40 for the first clutch E1 is associated with a balancing chamber 34, the balancing chamber 34 being delimited by a portion of the cylindrical hub 7, a portion of the input disc carrier 16 and a portion of the piston 40.
The piston 40 of the first clutch E1 extends radially and is arranged axially between the control chamber 32 axially at the front and the balancing chamber 34 axially at the rear. The piston 40 is concentric with the input disc holder 6.
As shown in fig. 1, the piston 40 is controlled to be displaced by the control chamber 32, the control chamber 32 being axially delimited by a front face of an inner radial portion of the piston 40 and a rear radial face of the closing member 45.
The balance chambers 34, 38 are supplied with cooling oil through the passages 71 b.
The piston 40 is controlled to axially clamp said multi-disc assembly of the first clutch E1 in the engaged position against the reaction means 8 formed directly in the input web 3.
The first clutch E1 comprises elastic return means 60, which in the example of fig. 1 are made in the form of a helical spring, to automatically return the piston 40 to the disengaged position. In this position, the piston 40 axially releases the multi-disc assembly, which then no longer transmits torque in the direction of the first driven shaft A1. The elastic return means 60 exert an axial force between the input disc holder 6 and the piston 40. In a variant not shown, the elastic return means may comprise an annular elastic washer or a wave washer.
As shown in fig. 2, the elastic return means 60 comprise, in particular, two support plates 61, 62 of annular shape and a series of helical springs 63 distributed circumferentially between the two support plates 61, 62.
The bearing plate 61 is axially supported on the seal support 70 of the balancing chamber 34.
The balance chamber 34 is sealed by a seal support 70, a first seal 71 and a second seal 72. In this example, the seal support 70 supports the first seal 71 and holds the second seal 72 axially in place relative to the balance chamber 34.
The compression of the first seal 71 is achieved by the axial force exerted by the elastic return means 60. Thus, the holding of the first seal 71 in place within the wet clutch mechanism no longer requires complex assembly operations.
The seal support 7 is a separate component from the input disc carrier and piston and can therefore be made more easily from stamped steel or aluminium plates. The shape of the seal support 70 is adapted to the first seal 71 and the second seal 72, the first seal 71 and the second seal 72 being made in the form of a single identical seal directly over-molded onto the seal support. The seal support comprises in particular a radially extending bearing 74 supporting the first seal 71 and an axially extending bearing 75 supporting the second seal 72. The radially extending bearing 74 of the seal support comprises an annular recess 76, in which recess 76 the first seal 71 is inserted.
The first seal is axially compressed between two parts that do not move relative to each other, namely the input disc carrier and the seal support. The first seal 71 is shown here in the form of a lip seal, but may be replaced by an O-ring seal or a flat seal.
The second seal 72 is interposed between two components having relative movement between each other, namely the piston and the seal support. The second seal 72 is a lip seal that slides over a cylindrical bearing 42 provided on the piston 40.
As shown in fig. 3, the seal support comprises rotation stop tabs 77 arranged circumferentially around the radially extending support 74, which tabs are inserted into a shaped stamping 68 made in the input disc carrier 6 in order to avoid rotation of the seal support 70 relative to the input disc carrier 6.
The design of the second clutch E2 of the wet dual clutch mechanism 1 is similar to the design of the first clutch E1, the second clutch E2 preferably being of the multiple disc type.
Advantageously, for the description of the second clutch E2, reference will be made to the detailed description of the first clutch E1 given above, as required.
The second clutch E2 comprises a piston 50, the piston 50 being axially movable here from rear to front between a disengaged position and an engaged position, which correspond to the open and closed state of the second clutch E2, respectively.
The piston 40 of the first clutch E1 and the piston 50 of the second clutch E2 of the wet dual clutch mechanism 1 are axially displaced in opposite directions to, for example, shift from a disengaged position to an engaged position.
Advantageously, the piston 50 comprises at its outer radial end an axially forward extending support 51. The support 51 is supported on the end flange 21 of the multi-disc assembly of the second clutch E2.
The piston 50 is controlled to axially clamp the multi-disc assembly of the second clutch E2 against the reaction means 28 in the engaged position. The reaction means 28 are formed directly on the annular portion 16 of the outer disc carrier 14 for the first clutch E1.
The second clutch E2 further comprises elastic return means 60 for automatically returning the piston 50 to the disengaged position. The elastic return means 60 comprise two support plates 61, 62 of annular shape and a series of helical springs 63 distributed circumferentially between the two support plates 61, 62.
The bearing plate 61 is axially supported on the seal support 70a of the balance chamber 38.
The balance chamber 38 is sealed by a seal support 70a, a first seal 71 and a second seal 72. In this example, the seal support 70a supports the second seal 72 and the first seal 71 relative to the balance chamber 38. The seal support 70a includes only a radially extending bearing portion that supports the first seal 71 and the second seal 72.
The compression of the first seal 71 is achieved by the axial force exerted by the elastic return means 60. The elastic return means 60 bring the sealing support 70a against the piston 50.
The elastic return means 60 are supported on a balance cover 39 of the balance chamber 38, the balance cover 38 being attached to the input disc holder 6. The second seal 72 is interposed between two parts with relative movement between them, namely the piston and the balance cap 39. The second seal 72 is a lip seal that slides over a cylindrical bearing provided on the balance cover 39.
Referring now to fig. 4, a wet dual mechanism 10 according to a second embodiment of the present invention is substantially similar to the first embodiment, except that the seal support 70b of the balance chamber 34 of the first clutch E1 is common with one of the annular bearing plates of the resilient return means.
The sealing support 70c of the balance chamber 38 of the second clutch E2 comprises a centering pin 78 for the elastic return means 60.
Referring now to fig. 5, a wet dual mechanism 10 according to a third embodiment of the present invention is substantially similar to the first embodiment, except that a seal support 70d supports a first seal 71 and holds a second seal 72 in place axially with respect to the balance chamber 34. The elastic return means 60 comprise an annular bearing plate 61, which annular bearing plate 61 brings the seal support 70d against the input disc holder 6. The support plate 61 includes a cylindrical support portion extending axially around the axially extending support portion 75 of the seal support 70 d. The axial ends of the support plate 61 and the axially extending support 75 form a cavity capable of receiving the second seal 72. The second seal 72 is a lip seal that slides over a cylindrical bearing 42 provided on the piston 40.
The present invention is not limited to the above-described embodiments.

Claims (16)

1. A wet clutch mechanism (10) for a torque transfer system, the wet clutch mechanism comprising at least about an axis O:
A multi-disc assembly (E1, E2) consisting of a flange (11, 21) and a friction disc (12, 22),
A torque input disc carrier (6) for inputting torque, arranged to receive the multi-disc assembly,
A piston (40, 50) axially movable relative to the input disc carrier between an engaged position and a disengaged position of the clutch mechanism, the piston being controllably displaced by a control chamber (32, 36), a balancing chamber (34, 38) being associated with the control chamber, the balancing chamber being defined in part by the piston (40, 50) and the input disc carrier (6),
An elastic return device arranged to return the piston to the disengaged position of the clutch mechanism, an
The balancing chamber (34, 38) is partially sealed by a seal support (70, 70a,70b,70c,70 d), a first seal (71) and a second seal (72), the seal support supporting the first seal and holding the second seal axially in place with respect to the balancing chamber,
The compression of the first seal (71) is achieved by the axial force exerted by the elastic return means (60).
2. Wet clutch mechanism (10) according to claim 1, wherein the elastic return means (60) exert an axial force between the input disc carrier (6) and the piston (40, 50), which elastic return means bring the seal support (70, 70a,70b,70c,70 d) against the input disc carrier or the piston.
3. Wet clutch mechanism (10) according to claim 1 or 2, wherein the resilient return means (60) bring a seal support (70, 70b,70 d) against the input disc carrier, the first seal (71) being pressed between the seal support and the input disc carrier.
4. A wet clutch mechanism (10) according to claim 3, wherein the elastic return means (60) is interposed axially between a sealing support (70, 70b,70 d) and the piston (40).
5. A wet clutch mechanism (10) according to claim 3, characterized in that a seal support (70, 70b,70 d) is axially supported on the input disc carrier and is free to displace radially relative to the input disc carrier.
6. A wet clutch mechanism (10) according to claim 3, wherein the second seal (72) slides on a cylindrical bearing (42) provided on the piston (40).
7. Wet clutch mechanism (10) according to claim 1 or 2, wherein the elastic return means (60) bring a seal support (70 a,70 c) against the piston (50), the first seal (71) being pressed between the seal support and the piston.
8. Wet clutch mechanism (10) according to claim 7, wherein the elastic return means (60) are interposed axially between a sealing support (70 a,70 c) and the input disc carrier (6).
9. Wet clutch mechanism (10) according to claim 7, characterized in that a sealing support (70 a,70 c) is axially supported on the piston (50) and is free to displace radially with respect to the piston.
10. Wet clutch mechanism (10) according to claim 7, wherein the second seal (72) slides on a cylindrical bearing provided on the input disc carrier (6) or on a balancing cover (39) of a balancing chamber attached to the input disc carrier (6).
11. Wet clutch mechanism (10) according to claim 1 or 2, wherein the seal support (70, 70a,70b,70c,70 d) comprises a radially extending bearing (74) and an axially extending bearing (75) supporting the first seal (71) and the second seal (72).
12. Wet clutch mechanism (10) according to claim 1 or 2, wherein the seal support (70, 70a,70b,70c,70 d) comprises a radially extending support (74) comprising an annular recess (76) into which the first seal (71) is inserted.
13. Wet clutch mechanism (10) according to claim 1 or 2, wherein the first seal (71) and the second seal (72) are made in the form of a single identical seal directly over-molded on the seal support (70, 70a,70b,70c,70 d).
14. Wet clutch mechanism (10) according to claim 1 or 2, wherein the first seal (71) and the second seal (72) are separate, the elastic return means (60) comprising two support plates (61, 62) of annular shape and a series of helical springs (63) distributed circumferentially between them, one of the two support plates (61, 62) carrying the second seal (72).
15. Wet clutch mechanism (10) according to claim 1 or 2, wherein the elastic return means (60) are arranged outside the balancing chamber (34, 38).
16. The wet clutch mechanism (10) according to claim 1, wherein the torque transfer system is for a motor vehicle.
CN201910444937.0A 2019-04-09 2019-05-27 Wet clutch mechanism including improved seal Active CN111795080B (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1903801A FR3095021B1 (en) 2019-04-09 2019-04-09 WET CLUTCH MECHANISM INCLUDING IMPROVED SEALING
FR1903801 2019-04-09

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DE102021207065B4 (en) 2021-03-29 2023-05-17 Magna Pt B.V. & Co. Kg Multi-plate clutch arrangement, in particular a triple-plate clutch with connected compensation chambers

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