KR20150047103A - Hydraulic control type clutch bearing - Google Patents

Abstract

The present invention relates to a hydraulic control type clutch bearing for the transmission of a vehicle comprising; an inner tube (3); an outer tube (4); a guide member (2) including an axial ring-shaped receiving unit which is defined by the inner tube, the outer tube, and a floor wall; and a piston (11) which is installed inside a housing of the guide member to be able to move and is guided between a guide area of the outer tube and a guide area of the inner tube. The guide member comprises a fluid supply route (8) of the housing connected between an inner and unit (10) which is opened inside the housing and an outer end unit (9) which is opened to the outer side of the guide member. The outer end unit of the fluid supply route is located inside a radiation direction of a guide area (83) of the outer tube as a radiation direction protruding unit.

Description

HYDRAULIC CONTROL TYPE CLUTCH BEARING [0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to the field of hydraulic control clutches designed to be installed in a transmission of an automobile.

Clutches that are actuated by hydraulic control for clutch disengagement or clutch engagement are known in the prior art.

The hydraulic control device is described in particular in document EP1066476. The hydraulic control device includes a cylindrical guide member installed around the transmission shaft. The guide member includes a cylindrical inner tube and a cylindrical outer tube joined together by a bottom wall to form an axial annular housing together. An axially movable piston is received in the housing to form a pressure chamber having a variable volume. A passageway or orifice is provided in the exterior to allow the hydraulic fluid to be supplied to the pressure chamber. And an outer body for fixing the hydraulic control device to the fixed portion of the vehicle surrounds the housing and is formed to face the supply orifice of the pressure chamber.

The guide member constitutes a hydraulic pressure receiver for controlling the hydraulic pressure of the clutch. A conduit connected to the outlet of the main cylinder is connected to the outer body. The conduit supplies a hydraulic fluid to the pressure chamber through a passage provided in an outer surface of the guide member and an outer body.

On the other hand, however, the addition of an enclosure which enables the fixation of the device to the stationary part of the vehicle and, on the other hand, the fixing of the supply conduit to the guide member, inevitably increases the radial charge volume. This volume charge is further problematic in hybrid architectures such as that disclosed in document FR2830859 when it is desired to accommodate a hydraulic control device inside the rotor of an electric machine.

The basic idea of the present invention is to solve the problems of the prior art by proposing a hydraulically controlled clutch device which occupies less volume and is simple to manufacture.

According to one embodiment, the present invention particularly provides a hydraulically-controlled clutch bearing for a transmission of an automobile,

A guide member including an inner tube and an outer tube, the inner tube being connected to the outer tube radially outwardly by a bottom wall, the inner tube, the outer tube and the bottom wall defining an axial annular housing together;

A piston movably installed in the housing of the guide member along a longitudinal axis of the guide member and guided between a guide surface of the outer tube and a guide surface of the inner tube,

The guide member includes a fluid supply passage of a housing extending between an inner end opening into the housing and an outer end opening on an outer surface of the guide member,

The outer end of the supply passage is positioned as a radial projection within the radial direction of the guide surface of the outer tube.

The arrangement of the outer ends of the fluid supply passages of the pressure chambers according to the present invention is advantageous in that the supply conduits are provided on the guide member at a smaller distance from the longitudinal axis of the guide member than in the case of being installed in the main part of the outer tube designed to guide the piston, The fluid supply conduit of the < / RTI > The supply conduit is fixed to the guide member closer to the longitudinal axis of the guide member, and the radial charge volume generated by being fixed to the guide member is reduced. Thus, the device according to the invention can guide the piston in the pressure chamber between the outer and inner tubes in the axial direction by limiting the charge volume required to secure the supply conduit of the pressure chamber on the guide member.

According to another advantageous embodiment, this hydraulically controlled clutch bearing may have one or more of the following features:

The bearing includes an exterior member fixedly attached to a rear end portion of the guide member along an axial direction of the guide member, the rear end portion of the guide member includes a bottom wall of the guide member, Wherein a portion of the connector is a radial projection projecting radially inwardly with respect to a guiding surface of the outer tube, the connector including a passage whose outlet is located opposite the outer end of the feed passage of the guide member .

The bearing further comprises a reinforcement, and an outer end of the passage of the guide member is open to the outer surface of the guide member located in the reinforcement.

The bearing includes an outer body fixedly attached to a rear end portion of the guide member along the axial direction of the guide member, the rear end portion of the guide member includes a bottom wall of the guide member, Wherein an outer end of the passage of the guide member is open to an outer surface of the guide member located in the reinforcing portion and the outer surface of the guide member is in contact with the outer surface of the outer member, And a shoulder portion which is complementary to the reinforcing portion and is supported and supported by the support surface of the reinforcing portion so that rotation of the guide member is interrupted, wherein the exterior body includes a connector, and a part of the connector is connected to the guide surface The radial protrusion protruding radially inwardly, the connector having an outlet communicating with the hole of the guide member And a passage positioned facing the outer end of the supply passage. This complementarity between the shoulder portion and the reinforcement portion can ensure the anti-rotation function of the guide member in addition to the reduction of the radial charge volume, and the rotation of the guide member is blocked by the bearing of the shoulder portion of the outer body at least partially including the connector .

The reinforcing portion is a groove of the outer surface of the guide member.

The reinforcing portion forms a flat portion on the outer surface of the guide member. Such a reinforcing portion can be easily realized, for example, by simply processing an overthickness in the outer surface.

The reinforcing portion includes a connecting wall connecting the bottom of the reinforcing portion to an outer surface of the guide member, and an outer end of the passage of the guide member is opened to the connecting wall.

The connecting wall extends radially from the inner tube of the guide member to the outer surface of the guide member.

The supply passage of the guide member is formed in the thickness of the bottom wall connecting the outer tube of the guide member and the inner tube of the guide member.

The feed passage of the guide member comprises a first aperture extending along an axial component and forming an inner end of the passageway and a second aperture extending along a component perpendicular to the first aperture and forming an outer end of the passageway, . The formation of these two openings in the orthogonal direction prevents the application of pressure due to rotation, so that the connection between the supply conduit and the enclosure of the guide member is very strong.

The present invention also provides a transmission unit comprising a clutch and the aforementioned clutch bearing capable of operating the clutch.

According to one embodiment, a transmission unit of an automobile comprises an electric machine including an outer stator and an inner rotor, the clutch bearing being at least partly accommodated in the interior of the inner rotor.

BRIEF DESCRIPTION OF THE DRAWINGS The invention will be better understood and other details, features and advantages of the invention will become apparent from the following detailed description of a plurality of embodiments of the invention, given by way of non-limiting example only, with reference to the accompanying drawings,

1 is a cross-sectional view of a guide member including a pressure chamber having a variable volume of the prior art.
2 is a detailed exploded view of the connection between the supply conduit and the enclosure of the guide member of FIG.
3 is a cross-sectional view of a clutch bearing according to the present invention connected to a supply conduit;
4 is a cross-sectional view of the clutch bearing of FIG. 3 in a hybrid architecture;
5A is a schematic perspective view of a guide member according to one embodiment.
FIG. 5B is a view of the guide member of FIG. 5A; FIG.
6A is a schematic perspective view of a guide member according to one embodiment.
FIG. 6B is a view of the guide member of FIG. 6A. FIG.
7A is a schematic perspective view of a guide member according to one embodiment.
- Figure 7b is a sectional view of an embodiment variant of the guide member.
8A to 8D are schematic perspective views of a modification of the embodiment of the guide member.

In the following description, the same or similar or similar parts or elements are denoted by the same reference numerals.

In the present specification and claims, the terms "outer" and "inner" and directions "axis" and "radial" are used to denote elements of a clutch bearing in accordance with the definitions given herein. For convenience, the "radial" direction is orthogonal to the coaxial axis X of the clutch bearing defining the "axis" direction and extends from the axis to the outside, And is perpendicular to the radial direction. The terms "outer" and "inner" are used to define the relative position of one element with respect to another element relative to the longitudinal coaxiality of the bearing, do.

Figure 1 shows a hydraulic controlled clutch release bearing of a clutch which is a mechanical clutch with a diaphragm of an automobile.

The hydraulic control clutch release bearing 1 includes a guide member 2, also referred to as a guide tube. The guide member 2 includes a cylindrical inner tube 3 on which a transmission shaft (not shown) is installed. The guide member 2 also includes a cylindrical outer tube 4 connected to the inner tube 3 by a bottom wall 5. The outer tube (4) has a diameter larger than the diameter of the inner tube (3). The outer tube 4 has a length along the longitudinal axis 6 of the guide member 2 and is smaller than the length of the inner tube 3 along the same longitudinal axis 6. The outer tube (4), the bottom wall (5) and the inner tube (3) together define a housing (7). The housing (7) includes a passage (8) through which the guide member (2) is supplied with hydraulic fluid. The hydraulic fluid providing the hydraulic control is passed through the inlet 9 of the passage 8 located on the outer surface of the outer tube 4 and the outlet 10 of the passage 8 opened to the housing 7, (8). This passage (8) is located near the bottom wall (5) of the guide member (2).

For example, a tubular piston 11 made of a plastic material by casting is installed in the guide member 2. More specifically, the rear end 12 of the piston 11 is received in the housing 7 of the guide member 2. [ A sealing dynamic seal (not shown) is provided at the rear end 12 of the piston 11 to sealingly seal the housing 7. The piston (11) slides into the housing (7) along the longitudinal axis (6) of the guide member (2). More specifically, the piston 11 is slid axially on the one hand by the inner tube 3 of the guide member 2 and on the other hand by the outer tube 4 of the guide member 2 . The rear end 12 of the piston 11 forms a pressure chamber 13 having a variable volume together with the housing 7. The front end 14 of the piston 11 is supported on a bearing 15 comprising a ring axially connected to the piston 11 and a ring designed to contact the fingers of the diaphragm.

The inner tube 3 of the guide member 2 is provided at its front end with a cushion designed to prevent the sealing dynamic seal from coming out of the housing 7 and to form the axial bearing of the piston 11 And has a neck portion for receiving. It is also possible to form a unit which can be manipulated and carried so that the rear end 12 of the piston 11 does not come out of the housing 7 before it is installed in the vehicle.

An external body (17) is provided at the rear end (16) of the guide member (2). More specifically, the enclosure 17 at least partly conforms to the contour of the outer tube 4 and the contour of the bottom wall 5. The enclosure 17 comprises a connector 18 designed to sealingly communicate the supply conduit 19 of the hydraulic fluid and the inlet 9 of the passage 8 of the housing 7.

The sheath 17 is formed to be fixed on a fixed wall of the vehicle, for example in a gear box, or on a frame of a hybrid vehicle, on a support element of the stator of the electric machine. Generally, the exterior body 17 is installed on the fixed wall of the vehicle. The outer body 17 is made of, for example, a castable material or a plastic material on an aluminum base. The external body (17) and the guide member (2) are installed concentrically, that is, with the same longitudinal axis (6).

Since the guide member 2 is longer in the axial direction than the outer case 17, the guide member 2 protrudes in the axial direction with respect to the outer case 17. The outer body 17 has a stepped diameter to form a supporting shoulder 20 for the rear end of a preload spring (not shown) whose other end (front end) is supported on the rear surface of the bearing 15 . The preload spring surrounds the front end 21 of the small diameter of the casing (17).

The outer tube 4 is provided at its front end with a neck 22 for cooperating with the front end 21 of the outer body 17. More specifically, the neck 22 is for receiving the lugs 23 or notches belonging to the elastic legs provided at the front end 21 of the enclosure 17. The cutoff of the guide member 2 relative to the outer body 17 is realized by a notch protruding from the inner periphery of the front end portion 21 of the outer body 17, And penetrates into the hollow press-fit portion implemented at the front end of the press-fitting portion. The outer tube (4) is provided with a hollow for blocking rotation with respect to the outer body. In a variant, the hollow is replaced by a protrusion. Since the thickness of the front end portion 21 of the exterior member 17 is small, the guide member 2 can be installed in the exterior member 17 in a snapping manner. Therefore, the guide member 2 is inserted into the outer casing 17 in the axial direction until the notch enters into the press-in portion.

The enclosure 17 includes a collar 24 which mates with the wall 5 of the guide member 2 to block the guide member 2 in one axial direction. In the axial direction the guide member 2 is guided by the lug 23 of the front end 21 of the enclosure 17 engaged with the neck 22 of the outer tube 4 and by the wall 5 of the guide member 2 Is intercepted by collar 24 of outer sheath 17 cooperating with sheath 16. In a variant, the enclosure 17 can be overmolded around the guide member 2.

A protective pleat box 25 made of an elastomeric material such as rubber surrounds the preload spring. The pleated box 25 prevents the housing 7 from being contaminated with impurities.

Fig. 2 is a detailed exploded view of the connection between the supply conduit and the enclosure of the guide member 2 of Fig.

The connector 18 of the outer body 17 includes a connecting portion 26 and a sealing portion 27.

The connector 26 of the connector 18 is cylindrical. The connection portion includes a hollow portion in a complementary form with a male end 28 of a hydraulic fluid supply conduit 19 designed to be fixed to the connection portion 26. The connecting portion (26) includes a transverse groove (29). The means (28) includes a neck (30). The means also includes a sealing joint 31 positioned between the neck portion 30 and a distal portion designed to be inserted into the hollow portion of the connecting portion 26.

The hydraulic fluid supply conduit 19 is connected to the connecting portion 26 by inserting the means 28 into the outer end 32 of the connecting portion 26. The means 28 is arranged such that the resilient legs 34 extend through the transverse groove 29 of the connection 26 and are received in the neck 30 of the end 28, As shown in Fig.

The sealing portion 27 of the connector 18 is cylindrical in a hollow circular shape and extends in the radial direction with respect to the guide member 2. [ The connection part (26) leads to the sealing part (27). The inner end 35 (see FIG. 1) of the sealing portion 27 is located in front of the inlet 9 of the passage 8 of the housing 7. A sealing joint 31 is accommodated in the sealing portion 27 to ensure sealing between the sealing portion 27 and the inlet 9 of the passage 8. A sealing system 37 having a sealing joint 38 is also provided in the hollow portion of the sealing portion 27. The sealing portion 27 of the sealing system 37 is plugged with the plug 39 and the sealing joint 38 of the sealing system 37 is inserted into the opening 27 through which the plug 39 and the connecting portion 26 communicate, .

The control fluid may be a natural liquid. In all cases, control is referred to as hydraulic control. The supply conduit 19 is connected to a main cylinder controlled by an actuator including an electric motor controlled by a clutch release pedal or alternatively connected to a computer that controls an electric motor according to a predetermined program for effecting a clutch release operation (Not shown). The main cylinder includes a controlled hydraulic chamber having a variable volume and a piston. This is the same as the receiver, that is, the clutch release device according to the present invention.

When the conductor acts on the clutch release pedal, for example, as is known from patent EP 1066476, the piston of the main cylinder is displaced in the axial direction and injects the control fluid toward the guide member 2. This fluid penetrates into the pressure chamber 13 through the connector 18 of the enclosure 17 and through the passage 8. The injection of the hydraulic fluid into the pressure chamber 13 causes displacement of the piston 11 by increasing the volume of the pressure chamber 13. During its displacement, the piston 11 applies a force to the bearing 15 and the ring of the bearing is supported on a diaphragm (not shown). Under a support load applied to the bearing 15, the diaphragm pivots and acts on the pressure plate (not shown) of the clutch to release the friction disc (not shown) of the clutch.

When the conductor acts on the clutch release pedal, the piston of the main cylinder returns to its initial position, which is the same as piston 11. [ Thus, the pressure chamber 13 is depressurized and its return acts on the diaphragm to push the bearing 15 and the piston 11 back into the housing 7. Thereafter, the clutch engages.

Generally, the bearing 15 includes a rotatable outer ring and a rotatably fixed inner ring, with a bead interposed between the inner ring and the outer ring. The outer ring is configured to act to push the inner end of the finger that the diaphragm includes. Of course, the structure can be reversed so that the outer ring of the bearing is rotationally fixed and the inner ring of the bearing is of a rotational type. Thus, the rotatable ring may be flat or bulged to point contact with the fingers of the diaphragm.

A preload spring (not shown) can sustain the bearing 15 on the diaphragm and maintain it. The preload spring acts between the sheath 17 and the piston 11 in the axial direction. This spring is compressed when the clutch engages and is released when the clutch is disengaged. For the sake of memorization, the torque is transmitted from the engine of the vehicle to the input shaft of the gearbox and passes through the guide member 2 when the clutch engages. Torque is not transmitted when the clutch is disengaged. That is, under the action of the diaphragm, the friction disk of the clutch is stopped from rotating on the input shaft of the gearbox by being tightened between the reaction plate and the pressure plate of the clutch. All of these are well known and are disclosed, for example, in document EP 1066476. Of course, the clutch device may include a clutch release lever that acts on the coil spring. This can be made of a rhinosaurus acting on the dish spring washer.

According to the concept shown in FIG. 1 or FIG. 2, the enclosure 17 protrudes radially outwardly from the connector 18. In fact, the connector 18 designed to receive the hydraulic fluid supply conduit occupies the minimum space necessary to connect the hydraulic fluid supply conduit 19 on the one hand and, on the other hand, to receive the sealing system 37. Therefore, this needs to be provided in a space corresponding to the space in which the clutch device is incorporated in the vehicle, and the space occupied by the external body 17. This need is particularly detrimental when the hydraulically controlled bearing is partially received within the front end 21.

Figs. 3 and 4 show a first embodiment of the present invention which can solve this disadvantage. More specifically, FIG. 3 illustrates a cross-sectional view of a clutch release bearing according to a first embodiment, and FIG. 4 illustrates a clitoral release bearing of FIG. 3 integrated into a hybrid architecture.

In general, the same structures and / or functional elements described above with respect to Fig. 1 are denoted by the same reference numerals in the embodiments shown below.

According to this embodiment, the outer tube 4 includes a main portion 40 and a supplementary portion 41. [ The main portion 40 forms a reinforcing portion of the outer tube 4 in this embodiment and the reinforcing portion at least has an outer surface positioned radially inwardly with respect to the main portion 40 as a radial projection.

The main part (40) is a circular cylindrical shape having a busline (6). The piston 11 is received between the inner tube 3 and the main part 40 and the sealing joint of the piston 11 on the one hand cooperates with the outer surface 82 of the inner tube 3 and on the other hand the main part 40 of the outer tube 4, (83) of the pressure chamber (40) to ensure sealing of the pressure chamber (13). The outer surface 82 of the inner tube 3 and the inner surface 83 of the main portion 40 respectively form a guide surface for guiding the piston 11 in the sliding direction in the axial direction.

3 and 4, the fluid supply inlet 9 of the housing 7 includes a main portion 7 of the outer tube 4 designed to guide the piston 11 slidingly into the housing 7, Is positioned as a radial projection inside the radial direction of the inner surface (83) of the base (40).

The auxiliary portion 41 is a circular cylindrical shape having a diameter smaller than the diameter of the main portion 40. The busbar of the auxiliary portion 41 is the longitudinal axis 6 of the guide member 2 or is the same as the busbar of the main portion 40. The auxiliary portion 41 is axially positioned between the main portion 40 and the bottom wall 5 of the guide member 2. [ The auxiliary portion 41 generally has an outer surface 42 which defines the groove of the outer tube 4 and is parallel to the outer surface 43 of the main portion 40. [ The auxiliary portion 41 is connected to the bottom portion 5 on the one hand and to the main portion 40 by means of a flat circular connecting wall 44 on the other hand.

The fluid supply inlet (9) of the housing (7) is located in the auxiliary part (41). 3 and 4, the inlet 9 is located on the outer surface 42 of the ancillary portion 41. In the embodiment shown in Figs.

The external body 17 matches the shape of the main portion 40, the connecting wall 44, the auxiliary portion 41 and the bottom wall 5 of the guide member 2. [ Similar to the enclosure 17 disclosed with respect to Figures 1 and 2, the enclosure 17 is characterized in that the inner end of the seal 27 in this embodiment is located at the front of the inlet 9 of the passage 8 And a connector (18) for enabling the supply of the pressure chamber (13) in a sealing manner. Likewise, the connector 18 includes a connection 26 as described with respect to Figs. 1 and 2 designed to receive the supply conduit 19 in a sealed manner.

However, the connector 18 is located in the front of the ancillary portion 41 including the inlet 9 in this embodiment. The auxiliary portion 41 has a smaller diameter than the main portion 40, and thus has a smaller radial occupying volume. The sealing portion 27 of the connector 18 located on the front face of the auxiliary portion 41 is located at a position where the sealing portion 27 is located on the front face of the outer tube guiding the piston 11 such as the main portion 40 in this embodiment Lt; RTI ID = 0.0 > radial < / RTI >

In this embodiment, the auxiliary portion 41 has a diameter smaller than the diameter of the main portion 40, and the piston 11 is moved along the longitudinal axis 6 only between the main portion 40 and the inner portion 3 of the outer tube 4, As shown in FIG. Actually, when the piston 11 is pushed back into the pressure chamber 13, the rear end 12 of the piston 11 is bearingly supported against the connecting wall 44.

As can be seen from Fig. 3, the enclosure 17 requires only a small charge volume of the clutch device beyond the corrugated box in this embodiment.

By way of example, FIG. 4 shows at least the hydraulic control device 1 of FIG. 3 integrated in a hybrid architecture. The hydraulic control device is designed to ensure the operation of the clutch 45 disposed between the crankshaft (not shown) of the internal combustion engine and the electric machine 46 in the axial direction. The hydraulic control device 1 is disposed inside the electric machine 46 to reduce the axial charge volume of the hybrid architecture. Therefore, the radial charge volume of the hydraulic control device should be as small as possible.

As can be seen from FIG. 4, the space required to provide the electrical machine 46 incorporating the electrical control device as in FIG. 3 is advantageously limited to the space required for the passage of the supply conduit 19. The connector 18 of the enclosure 17 is configured such that the connector 18 does not protrude radially beyond the space occupied by the hydraulic fluid supply conduit 19 around the pleat box 25, Is sufficiently radially inward as a radial projection so as to be fixed to the connecting portion 26.

In the second embodiment shown in Figs. 5A and 5B, the reinforcing portion forming the auxiliary portion 41 of the outer tube 4 occupies only a part of the circumference of the circumference of the end portion 16 of the outer tube 4. The auxiliary part (41) has a plane in which the inlet (9) of the passage (8) of the housing (7) is located. The main portion 40 of the outer tube 4 is formed of a flat portion 47 formed on the rear end portion 16 of the outer tube 4 and the main portion 40 of the outer tube 4, (See Fig. 1). The guide tube 4 is formed as an axial protrusion. The side edge of the flat surface portion 47 extending along an axis parallel to the longitudinal axis 6 of the guide member 2 is joined to the main portion 40 of the outer tube 4. [ The connecting wall 44 is present in the form of a flat wall connecting the front edge 49 of the plane portion 47 to the main portion 40 of the outer tube 4. [ 5B, such a flat surface portion 47 is embodied in a thick portion provided at the rear end portion 16 of the outer appearance 4, for example, in the vicinity of the bottom wall 5 of the guide member 2. The flat portion 47 can be realized by a simple process and the passage 8 of the housing 7 can be realized by perforation.

As in the embodiment shown in Figs. 3 and 4, by locating the inlet 9 of the passage 8 and projecting radially inward relative to the guide surface 83 of the main portion 40 of the outer tube 4 At least a part of the connector 18 of the external body 17 can be received. It is also advantageous that the enclosure 17 includes a shoulder (not shown) that matches the shape of the flat surface 47. Due to such complementarity of the shoulder portion of the outer body 17 and the flat surface portion 47, the outer surface of the outer body 17 is complementarily supported by the plane portion 47 with respect to the shoulder portion of the outer body 17, It is possible to interrupt the rotation of the main body 2. It is therefore unnecessary to provide the blocking lugs 22 on the complementary orifices 21 and the outer body 17 on the guide member 2.

6A and 6B, the bottom wall 5 has a thick portion 50 extending in the axial direction. The reinforcing portion is formed by a groove for the outer tube 4 formed in the thick portion 50 of the bottom wall 5. The radially outer surface (51) of the bottom wall (5) extends parallel to the outer surface (4). The circular connection 52 of the bottom wall 5 extends in the radial direction and connects the radial outer surface 51 to the outer surface 4. [

The radial outer surface 51 of the desired diameter can be formed by simple processing in the thick portion 50 of the bottom wall 5. [ In this embodiment, the passageway 8 of the housing 7 includes a first portion 53 and a second portion 54.

The first portion 53 of the passage 8 is realized by the non-penetrating opening in the thick portion 50 of the bottom wall 5. This opening is implemented on the face of the bottom wall 5 located in the housing 7 along the longitudinal axis 6 of the guide member 2. [ In general, the opening of the first part 53 of the passage 8 enables the implementation of the outlet 10 of the passage 8 leading to the pressure chamber 13.

The second portion of the passageway 8 is embodied by apertures on the radially outer surface 51 of the thick portion 50 of the bottom wall 5. The apertures are implemented along the radial direction such that the first portion 53 extends perpendicularly to the second portion 54. The second portion 54 of the passage 8 comprises an inlet 9 of the passage 8. The first portion 53 and the second portion 54 of the passage 8 are connected to the thick portion of the bottom wall 5 so as to allow the circulation of the hydraulic fluid from the inlet 9 to the outlet 10 of the passage 8. [ 50).

In the embodiment shown in Figs. 6A and 6B, the outer body (not shown) includes an outer body 17 which mates with the auxiliary portion 41 of the outer tube 4 in the embodiment shown in Figs. 3 and 4 Is likewise designed to match the radially outer surface 51 of the thick portion 50 of the bottom wall 5. Thus, likewise, at least a part of the connector 18 of the enclosure 17 is located radially outward with respect to the enclosure 4. [ Therefore, the external body 17 is reduced in radial charge volume as compared with the conventional external body.

The fourth embodiment will be described with reference to Fig. 7A.

In this embodiment, the reinforcing portion extends in almost the whole period of the circumference of the guide member 2. [ Thus, the thick portion 50 of the bottom wall 5 is machined on substantially the entire period of the guide member 2 as described with reference to Figs. 6A and 6B. This processing allows the thick portion 50 to support only the lug 55 extending in the axial direction toward the rear portion of the guide member 2. [ The connecting portion 52 of the thick portion 50 of the bottom wall 5 generally connects the inner tube 3 to the outer tube 4 on a substantially complete circumference and the lug 55 is connected to the guide member 2, Of the unprocessed thicker portion 50 on a small portion of the period of the cycle.

The passage 8 of the housing 7 is implemented similarly to the passage 8 of the housing 7 shown in Figs. 6A and 6B. This passage 8 is implemented in the lug 55 by the apertures forming the first portion 53 and the second portion 54 of the passage 8. The inlet 9 of the passage 8 is advantageously located in the side wall 56 of the lug 55 and the side wall 56 is located on the inner surface of the lug 55 located in the extension of the inner tube 3. [ (57) and the outer surface (58) of the lug (55) located in the extension of the outer tube (4).

The inlet 9 is located in the side wall 56 of the lug 55 and the lug is positioned radially within the radial direction with respect to the inner surface 83 of the main part designed to guide the piston 11. An external body connector (not shown) provided on the guide member 2 is received axially in the extension of the pressure chamber 13 and the seal 27 is simultaneously inserted into the side wall 56 of the lug 55, And the connecting portion 52 as shown in Fig.

Figure 7b shows a cross-sectional view of an embodiment wherein the passage 8 of the housing 7 is implemented by perforation on the bottom wall 5 of the guide member without the thick portion 50. [ In this variant, the connector 18 of the enclosure 17 extends not only in the radial direction as in the embodiment of Fig. 7a but also from the axially extending portion of the bottom wall 5 toward the rear portion. This embodiment can implement a clutch device in which the connector 18 of the enclosure 17 takes up little or no radial volume.

8A to 8D show an alternative embodiment of the guide member 2 capable of reducing the radial charge volume of the enclosure 17. Fig.

8A, the reinforcing portion of the outer tube 4 is formed by a groove 59 having a bottom 60 parallel to the radially outer surface 61 of the outer tube 4. In the first alternative embodiment shown in Fig. The bottom 60 of the groove 59 has a busbar generally the diameter and the outer diameter smaller than the diameter of the outer tube 4 and generally the longitudinal axis 6 of the guide member 2. The connecting wall 62 connects the side edge 63 and the front edge 64 of the bottom 60 of the outer tube 4. The connecting wall 62 is positioned, for example, in a plane perpendicular to the floor 60.

The inlet 9 of the passageway 8 of the housing 7 is advantageously located at the bottom 60 near the side edge 63. In this alternate embodiment, the external connector (not shown) mounted on the guide member 2 is at least partly received in the groove 59, thereby reducing the radial charge volume of the connector.

8a, the reinforcement is formed by a groove 59 as described with respect to Fig. 8a, but the inlet 9 of the passage 8 is formed in the bottom 60 of the groove 59 And is located at the connecting wall 62 without being positioned. More specifically, the inlet 9 is located on the connecting wall 65 connecting the side edge 63 of the bottom 60 to the outer tube 4.

In the third alternate embodiment shown in Fig. 8c, the outer tube 4 includes a reinforcement 66, which is composed of two abutment planes 67 along the secant line 68. The joining line 68 is positioned as a radial protrusion in the radial direction with respect to the outer tube 4. The connecting wall 69 connects the front edge 70 of the plane 67 to the outer surface 4. The inlet 9 of the passage 8 of the housing 7 is located in the plane 67 of the reinforcement 66. An external connector (not shown) provided in the guide member 2 is at least partly accommodated in the reinforcing portion 66, thereby defining the radial charge volume of the connector 18.

In a variant of the third alternative embodiment shown in Fig. 8C shown in Fig. 8d, the plane 67 of the reinforcement portion is penetrated to the guide member 2. Fig. The first plane (71) extends in a plane perpendicular to the outer tube (4) and the inner tube (3). The second plane (72) extends in a plane perpendicular to the outer tube (4) and the inner tube (3). The abutment surface 73 connecting the first plane 71 to the second plane 72 extends in a plane perpendicular to the longitudinal axis 6 of the guide member 2. The inner edge 74 of the first plane 71 and the inner edge 75 of the second plane 72 are bonded to the inner tube 3. The rear edge 76 of the first plane 71 and the rear edge 77 of the second plane 72 are joined to the bottom wall 5 of the guide member 2. The outer edge 78 of the first plane 71 and the outer edge 79 of the second plane 72 are bonded to the outer surface 4. The front edge 80 of the first plane 71 and the front edge 81 of the second plane 72 are bonded to the bonding surface 73.

In this embodiment, the inlet 9 of the passage 8 of the housing 7 is located on the first plane 71 or the second plane 72. An external connector (not shown) mounted on the guide member 2 is at least partly accommodated in the extension of the pressure chamber between the first plane 71 and the second plane 72.

The present invention is not limited to the disclosed embodiment and the space in which the passage of the receiving portion is radially inward with respect to the main portion of the external appearance and the space separating the passage of the main portion of the external appearance radially separates the external body connector at least partially, And is applicable to all embodiments capable of accommodating a part of the wiring.

While the present invention has been described in connection with a number of specific embodiments, it is clear that the invention is not so limited at all, but includes all technical equivalents of the disclosed means, and combinations thereof, as embodied within the scope of the invention.

The use of the word "includes " and variations thereof does not exclude the presence of elements or steps other than those listed in a claim. The use of the singular representation of an element does not exclude the presence of a plurality of such elements, unless stated otherwise.

In the claims, all the signs in parentheses are not to be construed as limiting the claim.

Claims (12)

As hydraulic-controlled clutch bearings for automotive transmissions in particular,
- a guide member (2) comprising an inner tube (3) and an outer tube (4), said inner tube being connected to said outer tube radially outwardly by a bottom wall (5), said inner tube, Said guide member defining an axial annular housing (7); And
A piston movably installed in the housing of the guide member along a longitudinal axis of the guide member and guided between a guide surface of the outer tube and a guide surface of the inner tube,
The guide member comprises a fluid supply passage (8) of a housing extending between an inner end (10) opening into the housing and an outer end (9) opening on the outer surface of the guide member As a result,
Characterized in that the outer end of the feed passage is positioned as a radial projection inside the radial direction of the guide surface (83) of the outer tube
Clutch bearing. The method according to claim 1,
And a connector fixed to the guide member and designed to cooperate with the hydraulic fluid supply conduit (19) and includes a portion protruding radially inwardly with respect to a guide surface of the outer tube as a radial protrusion, And an outer body (17) comprising a hydraulic fluid supply outlet located opposite the outer end
Clutch bearing. 3. The method according to claim 1 or 2,
Characterized in that the guide member further comprises a reinforcing portion (66, 59, 47, 42), and the outer end of the passage of the guide member opened to the outer surface of the guide member is located in the reinforcing portion
Clutch bearing. The method according to claim 2 or 3,
Characterized in that the reinforcing portion extends over a part of the period around the longitudinal axis of the guide member and includes a portion complementary to the reinforcing portion so that rotation of the guide member relative to the exterior member is blocked
Clutch bearing. The method according to claim 3 or 4,
Characterized in that the reinforcing portion is a groove of an outer surface of the guide member
Clutch bearing. The method according to claim 3 or 4,
Wherein the reinforcing portion forms a flat portion on an outer surface of the guide member
Clutch bearing. 7. The method according to any one of claims 3 to 6,
Wherein the reinforcing portion includes connection walls (47, 56, 65, 67, 72) connecting the bottom of the reinforcing portion to an outer surface of the guide member, and an outer end of the fluid supply passage of the guide member Characterized in that
Clutch bearing. 8. The method of claim 7,
Characterized in that the connecting walls (62, 65, 71, 72) extend radially from the inner tube of the guide member to the outer surface of the guide member
Clutch bearing. 9. The method according to any one of claims 1 to 8,
Characterized in that the supply passage of the guide member is formed in a thickness (50) of the bottom wall (5) connecting the outer surface of the guide member and the inner tube of the guide member
Clutch bearing. 7. The method according to any one of claims 1 to 6,
The feed passage of the guide member includes a first aperture (53) extending along an axial component and forming an inner end of the passage, and a second aperture (53) extending along a component perpendicular to the first aperture and forming an outer end And a second aperture (54)
Clutch bearing. Comprising a clutch and a clutch bearing according to any one of claims 1 to 10 capable of operating the clutch
Transmission unit. 12. The method of claim 11,
An electric machine comprising an external stator and an internal rotor, characterized in that the clutch bearing is at least partly accommodated in the interior of the internal rotor
Automotive transmission unit.

Images