Separating system for actuating clutch device and clutch device

Abstract

The invention relates to a disengagement system (1) for actuating a clutch device (100), comprising:-a housing (2) which extends along a longitudinal axis (A),-a piston device (3) for displaceably engaging a bearing (101),-wherein the piston device (3) and the housing (2) define a pressure chamber (D) for a hydraulic medium,-wherein the piston device (3) has an outer piston (4),-wherein the piston device (3) has an inner piston (5) for displaceably engaging the bearing (101), and-wherein the outer piston (4) has an inner piston (6) for displaceably engaging the bearing (101). The piston device (3) has at least one outer piston (4) which has a pressure section (4A) with a third pressure surface (D3),-the piston device (3) has at least one inner piston (5) which can be moved relative to the outer piston (4),-the at least one inner piston (5) has a piston section (5A) and a piston rod part (6) which is guided in the outer piston (3), -wherein the piston section (5A) has a first pressure surface (D1) and a second pressure surface (D2),-wherein the piston device (3) is designed in such a way that, in a first state, the piston section (5A) of the at least one inner piston (5) and the pressure section (4A) of the outer piston (4) are spaced apart from one another in an axial direction (A); and b. Wherein in a second state the piston section (5A) of the at least one inner piston (5) and the pressure section (4A) of the outer piston (4) adjoin one another.

Description

Technical Field

[0001] This invention relates to a disengagement system for operating a clutch device. The invention also relates to a clutch device having such a disengagement system. Background Technology

[0002] A clutch operating device is known, for example, from document DE 10 2014 223 130 A1. This document describes a fluid-technical operating device for a clutch mechanism, particularly for the transmission system of an internal combustion engine-driven motor vehicle.

[0003] The control device has a transmitting side with a hydraulic transmitting end and a receiving side with a hydraulic receiving end, wherein the control device has a multi-level switchable hydraulic transmission ratio between the transmitting side and the receiving side. Summary of the Invention

[0004] Therefore, the object of the present invention is to provide a separation system that can be manufactured inexpensively and in a space-saving manner, and that meets high torque and / or high dynamic requirements.

[0005] The objective is achieved through the features of the independent claim. Other advantageous improvements are the subject of the dependent claims.

[0006] A first aspect of the invention includes a separation system for operating a clutch device.

[0007] The separation system has a housing extending along a longitudinal axis and a piston assembly for moving the engagement support, wherein the piston assembly and the housing define a pressure chamber for a hydraulic medium.

[0008] The piston assembly has an external piston capable of moving relative to the housing along a longitudinal axis. The external piston has a pressure section with a third pressure surface oriented toward the pressure chamber.

[0009] The piston assembly further includes at least one internal piston movable relative to the external piston. The at least one internal piston has a piston section and a piston rod portion guided within or on the pressure section of the external piston.

[0010] The piston section has a first pressure surface facing the pressure chamber and oriented sideways to the piston rod. The piston rod may be mounted on the piston section or connected to and / or integrally constructed with the piston section. This results in a piston rod side where the piston section is arranged on or connected to the piston rod section.

[0011] For example, the at least one internal piston may be arranged coaxially with the external piston. Furthermore, the external piston may also be composed of multiple parts. The external piston may be a two-piece construction or have two annular structures. The at least one internal piston and / or the external piston and / or the housing may be designed rotationally symmetrically (e.g., relative to the longitudinal axis).

[0012] The piston section also includes a second pressure surface, which faces the pressure chamber and is oriented on the side opposite to the piston rod.

[0013] The piston assembly is designed such that, in the first state, the piston section of the at least one inner piston and the pressure section of the outer piston are axially spaced apart from each other, thereby allowing the difference between the first and second pressure surfaces to be pressurized with a hydraulic medium in the first state.

[0014] Furthermore, the piston assembly is designed such that, in the second state, the piston section of the at least one inner piston and the pressure section of the outer piston are adjacent to each other, thereby, in the second state, at least the second pressure surface of the piston section can be used for pressurization.

[0015] A core concept of this invention is that the internal piston can move rapidly in a first state when the pressure in the pressure chamber increases. At this time, the hydraulic medium (e.g., oil) is compressed between the internal and external pistons, or between the piston section and the pressure section, and redistributed within the pressure chamber. Therefore, only a small amount of hydraulic medium needs to be supplied to the pressure chamber to achieve a pressure increase. At this time, primarily or only at least one internal piston moves, and a small force can be applied to the engagement support connected to at least one internal piston. Therefore, at least one internal piston can be displaced along the longitudinal axis relative to the housing and the external piston.

[0016] In the second state, compared to the first state, more hydraulic medium is required to increase the pressure, or a larger volume of hydraulic medium needs to be delivered to the pressure chamber per unit time to achieve the same displacement as if at least one internal piston were moving alone. In the second state, at least one internal piston and the external piston can move relative to each other or together, so the displacement of the two pistons requires more hydraulic medium to enter the continuously expanding pressure chamber compared to the first state. In this way, at least one internal piston and the external piston move slowly (again compared to the first state), but they can act with greater force on the engagement support that can be connected to at least one internal piston.

[0017] The end result is that a low gear ratio and relatively small force allow for a rapid advance to the switching point (first state), followed by a switch to a high gear ratio (second state), thus generating the larger force required in the second state. The switching point refers to the transition point from the first state to the second state.

[0018] The switching point between the first and second gear ratios, or the first and second states, can be adjusted, for example, by adjusting the thickness along the longitudinal axis of the respective piston. Alternatively, the switching point can be optimized to occur after a period of operation. This depends on the specific requirements of the application.

[0019] Furthermore, the separation system can be used with the aid of conventional actuator technology to control, for example, torque vectoring clutches or brakes, electric limited-slip differential (eLSD) clutches or vehicle brakes, thereby increasing the actuation energy provided by the actuators and / or improving the response behavior or engagement time of the clutch or brake.

[0020] Furthermore, the difference between the first pressure surface and the second pressure surface constitutes an effective loading area, which accounts for at least 10% of the second pressure surface. Optionally, the effective loading area, i.e., the difference between the first and second pressure surfaces, accounts for approximately 5% to approximately 15% of the second pressure surface. In this way, two significantly different hydraulic transmission ratios can be achieved using the same separation system.

[0021] The third pressure surface of the pressure section of the outer piston can have the same size or the same area as the first pressure surface of the piston section of the inner piston.

[0022] Furthermore, the piston rod portion may be adjacent to its corresponding piston section along the longitudinal axis with a boundary surface corresponding to the difference between the first pressure surface and the second pressure surface. The piston rod portion may also be arranged on the piston section, or connected to and / or integrally formed with the piston section.

[0023] Furthermore, when viewed along the longitudinal axis, the piston section may have a step or protrusion extending away from the piston section and the first pressure surface, the step / protrusion being located in the radially outer edge region of the piston section. Therefore, the first pressure surface can be minimized to the greatest extent possible, because in the second state, the contact area between the piston section and the outer piston or its pressure section is maximized. For example, the protrusion may be arranged circumferentially in the radially outer region of the piston section. Additionally, gaps may be formed between the protrusion of the piston section and the outer piston or its pressure section, the piston rod, and the piston section itself.

[0024] Furthermore, the piston section, viewed along its longitudinal axis, may have a step or a protrusion, wherein, for example, when the protrusion is in contact with the outer piston or in a second state, the protrusion may be at least partially sealed by a sealing device. In this case, the sealing device may be arranged circumferentially along the protrusion or in a region radially outside or inside the protrusion.

[0025] Furthermore, the sealing device can be constructed as a ring structure protruding from the protrusion. This reduces the pressure chamber volume because the sealing device seals the gap or contact area between the first pressure surface and the external piston or its pressure section, resulting in a smaller first pressure surface in the second state compared to the first state.

[0026] Furthermore, reinforcing ribs can be provided along the longitudinal direction of the piston section. These ribs cause the third pressure surface or the pressure surface of the pressure section to deform upon contact, thereby achieving a sealing effect. This eliminates the need for additional sealing components or devices, thus reducing assembly errors and / or costs.

[0027] Furthermore, the at least one inner piston may be made of a harder material than the outer piston. This allows the softer material to yield to the harder material, providing an improved seal throughout the contact area. For example, the at least one inner piston may comprise steel or a similar material, but is not limited to these exemplary materials. The outer piston may comprise, for example, aluminum or other light metals, but is not limited to these exemplary materials. For example, the outer piston may be made of plastic.

[0028] Furthermore, the outer piston may have a stop section with a stop to restrict entry into the housing. This allows for a reliable attainment of the predetermined initial position. Additionally, during propulsion, the outer piston can more easily separate from / maintain a distance from the at least one inner piston or at the predetermined position, thereby achieving the first state.

[0029] Furthermore, the external piston or the pressure section of the external piston may be equipped with a seal for sealing the housing. The at least one internal piston or the piston rod portion of the at least one internal piston may also be provided with a seal for sealing the external piston. The piston seal may be designed as an O-ring, A-ring, injection-molded seal, or snap-on seal.

[0030] A second aspect of the present invention includes a clutch device for a motor vehicle. The clutch device includes a disengagement system and an engagement support connected to one end of the piston rod portion of the at least one internal piston.

[0031] It should be particularly noted that the features of the separation system described in the first aspect can be applied to the clutch device alone or in any combination.

[0032] In other words, the features of the separation system described in the first aspect of the present invention can also be combined with other features of the second aspect.

[0033] The clutch device may further include a clutch operatively connected to the engagement support. Furthermore, the clutch device may be equipped with a return spring that returns the engagement support to its original position in the opposite direction to the engagement direction, wherein an intermediate member may be disposed between the engagement support and the clutch, and the return spring may be fixed to the intermediate member.

[0034] The above-mentioned inventive concept will be reiterated and supplemented below using another form of expression.

[0035] In brief, this invention relates to a separation system whose characteristic curves inherently have two phases or slopes. In this case, the application range of a particular actuator can be expanded by modifying the characteristic curves to match the operating parameters of the actuator.

[0036] Developing mechatronic systems (such as actuators) can be significantly more expensive than developing purely mechanical components (such as clutches or concentric driven cylinders, also known as CSCs).

[0037] The core of this invention lies in using a hydraulic method to transmit force. This method can achieve force transmission and conversion through the hydraulically actuated piston area (or loading area / pressure area) on the driven cylinder of a clutch or at least one internal piston.

[0038] The piston rod or piston rod section arranged on the piston section can have a separate pressure element or extension, or consist of a separate pressure element or extension. A very small effective piston / load area can be achieved using a separate pressure element.

[0039] If necessary, it may be meaningful to place additional washers, discs, or intermediate components between the pressure components or piston rod and between the engagement support or clutch to transmit force more evenly.

[0040] The principle or separation system described can be implemented using either a CSC (stationary driven cylinder) or a rotary sealing joint (rotating pressure chamber). If a rotary joint is used, there is no need to use a connecting support. Attached Figure Description

[0041] The present invention will be further described in detail below with reference to the accompanying drawings and embodiments. The embodiments are shown schematically as follows: Figure 1 A cross-sectional view of a clutch device with a separation system according to a first embodiment is shown; Figure 2 Show Figure 1 The diagram shows a cross-sectional view of the separation system in its first state. Figure 3 Show Figure 1The diagram shows a cross-sectional view of the separation system transitioning from the first state to the second state. Figure 4 Show Figure 1 The diagram shows a cross-sectional view of the separation system in its second state. Figure 5 The force-displacement diagram of the detached system is shown; Figure 6 A cross-sectional view of the separation system according to the second embodiment is shown. Detailed Implementation

[0042] In the following description, the same reference numerals are used for the same technical solutions.

[0043] Figure 1 A cross-sectional view of a clutch device 100 with a separation system 1 according to a first embodiment is shown.

[0044] Figure 1 A clutch device 100 for a motor vehicle is shown in more detail, the clutch device 100 having a disengagement system 1 for operating the clutch device 100.

[0045] The clutch device 100 includes a separation system 1. The separation system 1 includes a housing 2 extending along a longitudinal axis A and a piston device 3 for moving the engagement support 101. The piston device 3 and the housing 2 define a pressure chamber D for a hydraulic medium, such as hydraulic oil.

[0046] The piston assembly 3 has an external piston 4 that is movable relative to the housing 2 along the longitudinal axis A. The external piston 4 has a pressure section 4A with a third pressure surface D3 oriented toward the pressure chamber D.

[0047] Furthermore, the piston assembly 3 has an internal piston 5 that is movable relative to the external piston 4. The internal piston 5 has a piston section 5A and a piston rod 6 that is guided in or on the pressure section of the external piston.

[0048] The piston section 5A has a first pressure surface D1, which faces the pressure chamber D and is oriented laterally to the piston rod. Figure 1 In this configuration, the piston rod portion 6 corresponds, for example, to the right side of the piston section 5A. The piston rod portion 6 is mounted on the piston section 5A or integrally connected to it.

[0049] Furthermore, the piston section 5A also includes a second pressure surface D2, which faces the pressure chamber D and is oriented on the side opposite to the piston rod portion. That is, the second pressure surface D2 corresponds to the left side of the piston section 5A, as shown below. Figure 1 As shown.

[0050] In addition, Figure 1 As can be seen, the internal piston 5, the external piston 4, and the housing 2 are designed with rotational symmetry precisely relative to the longitudinal axis A. Figure 1 As shown, the external piston 4 is constructed in a multi-piece manner.

[0051] Figure 1 It is also shown that the piston rod portion 6 is adjacent to its associated piston section 5A via an interface in the direction of the longitudinal axis A. This interface may correspond to the difference between the first pressure surface D1 and the second pressure surface D2. More simply, the piston rod portion 6 is connected to the piston section 5A.

[0052] In addition, according to Figure 1 The piston assembly 3 shown is designed such that, in a first state, the piston section 5A of the inner piston 5 and the pressure section 4A of the outer piston 4 are spaced apart from each other in the axial direction A, thereby allowing, in the first state, the difference between, for example, the first and second pressure surfaces D1 and D2, to be pressurized with a hydraulic medium. The difference formed by the first and second pressure surfaces D1 and D2 constitutes, for example, an effective loading area 7, which accounts for at least 10% of the second pressure surface D2.

[0053] Furthermore, the piston device 3 is designed such that, in the second state, the piston section 5A of the inner piston 5 and the pressure section 4A of the outer piston 4 are adjacent to each other, so that, in the second state, for example only the second pressure surface D2 of the piston section 5A can be used for pressurization.

[0054] Here, the piston section 5A, viewed along the longitudinal axis A, has, for example, a protrusion 8 that extends away from the piston section 5A and away from the first pressure surface D1. The protrusion 8 is arranged, for example, partially or completely surrounding the radially outer region of the piston section 5A. A gap 9 may be formed between the piston section 5A and the first pressure surface D1, and between the piston rod portion 6 and the outer piston 4 or the pressure section 4A of the outer piston 4.

[0055] Alternatively or additionally, when the protrusion 8 is in contact with or in a second state of the outer piston 4 or the pressure section 4A of the outer piston 4, the protrusion 8 may be sealed, for example, at least partially, by the sealing device 10. Here, the sealing device 10 is arranged circumferentially along the protrusion 8. For example, the sealing device 10 is configured as an annular structure protruding from the protrusion 8.

[0056] Furthermore, the outer piston 4 or the stop section 4B of the outer piston 4 may have, for example, a stop portion 11 that abuts against the housing 2 to restrict entry into the housing 2.

[0057] To seal the housing 2, the outer piston 4 or the pressure section 4A of the outer piston 4 has a seal 12, wherein the inner piston 5 or the piston rod portion 6 of the inner piston 5 has a seal 13 for sealing the outer piston. The seals 12, 13 are configured, for example, as sealing rings and positioned in suitable grooves on the outer surfaces of the respective pistons 4, 5.

[0058] The clutch device 100 also includes an engagement support 101, which is connected to one end of the piston rod portion 6 of the internal piston 5 of the separation system 1. Figure 1 The image exemplarily shows a clutch 102, which is operatively connected to an engagement support 102.

[0059] Optionally, the clutch device 100 may have a return spring 103 that returns the engagement support 101 to its original position in the opposite engagement direction, wherein an intermediate member 104 is arranged between the engagement support 101 and the clutch 102, and the return spring 103 may be fixed to the intermediate member.

[0060] Figure 2 The basis for the first state is shown. Figure 1 The figure shows a cross-sectional view of the separation system 1. In a first state, the pressure section 4A of the outer piston 4 and the piston section 5A of the inner piston 5 are separated from or spaced apart from each other, as shown. In the first state, the pressure chamber D is defined by the housing 2 and the third pressure surface D3 of the outer piston 4. The inner piston 5 is movably arranged in the pressure chamber D. When the pressure in the pressure chamber D increases, all sides of the inner piston 5 in contact with the hydraulic medium are subjected to the same pressure.

[0061] Figure 3 It shows that according to Figure 1 The diagram shows a cross-sectional view of the separation system 1 transitioning from a first state to a second state. During this transition, the inner piston 5 or the piston section 5A of the inner piston comes into contact with the outer piston 4 or the pressure section 4A of the outer piston. At this time, the hydraulic medium located in the gap 9 is discharged as much as possible, so that only a small amount or no hydraulic medium remains in the gap 9 where fluid separation is now taking place.

[0062] When contact is established between piston section 5A and pressure section 4A, the force transmission of separation system 1 changes. For example, the outer diameters of the two pistons 4 and 5, or piston section 5A and pressure section 4A, are set to be substantially the same size, so that during the transition from the first state to the second state, the first pressure surface D1 no longer serves as the loading surface of the hydraulic medium because the gap is fluidly separated.

[0063] Figure 4 The basis for the second state is shown. Figure 1The diagram shows a cross-sectional view of the separation system 1. In the second state, piston section 5A and outer piston 4 or pressure section 4A abut against each other. At least a portion of the first pressure surface D1 of piston section 5A abuts against the pressure section or third pressure surface D3.

[0064] In this way, the first pressure surface D1 is reduced or completely covered by the third pressure surface D3, which is opposite to the pressure section 4A. Therefore, in the second state, the second pressure surface D2 of the piston section 5A can be used for pressurization.

[0065] Figure 5 The force-displacement diagram of the separation system is shown. The lines drawn as approximately straight lines in the diagram illustrate two exemplary transmission ratios, U1 and U2.

[0066] Here, line U1 represents a smaller gear ratio, while line U2 represents a larger gear ratio. The crease, or the corner between the two lines U1 and U2, corresponds to the transition from the first state to the second state, i.e., the switching point between the two different gear ratios. For example, line U2 is shown in an offset position (here, further to the left), which illustrates a placement behavior. However, the slope and the corresponding translation are the same.

[0067] Figure 6 A cross-sectional view of the separation system according to the second embodiment is shown. Figure 6 The separation system 1 shown includes, according to Figure 1 The separation systems have essentially the same characteristics.

[0068] and Figure 1 The difference is that, according to Figure 6 In the separation system 1 shown, the piston section 5A has a pointed protrusion 8 when viewed longitudinally from A.

[0069] Furthermore, the inner piston 5 is made of a harder material than the outer piston 4, which is made of plastic, such as steel. However, the outer piston 4 may also be made of aluminum.

[0070] In this context, when the protrusion 8 comes into contact with the external piston 4 or the pressure section 4A of the external piston 4, the external piston 4 can be deformed, thereby achieving a seal.

[0071] The accompanying drawings will be further explained below using other terms.

[0072] exist Figure 5In the first part of the characteristic curve shown, corresponding to the first state, only the internal piston 5 is active and begins to move when the pressure rises rapidly. To achieve this, the hydraulic medium must be shifted between the internal piston 5 and the external piston 4, or between piston section 5A and pressure section 4A, or redistributed within the pressure chamber D. This reduces operational discontinuities while lowering the design costs of alternative solutions.

[0073] When the hydraulic medium is redistributed in pressure chamber D, flow is generated within pressure chamber D. The radial distance from the outer diameter of piston section 5A to the wall of pressure chamber D is constructed to be large enough to allow flow. At the point where the axial distance along the longitudinal axis A between the two pistons 4 and 5, i.e., pressure section 4A and piston section 5A, disappears, the inner piston 5 axially seals the outer piston 4, and only the second pressure surface D2 functions. Thus, the separation system 1 reaches according to... Figure 5 The second state or the second part of the characteristic curve.

[0074] To achieve further displacement of the internal piston 5 and the external piston 4, a larger volume of hydraulic medium needs to flow into the pressure chamber D per unit time compared to the first state, so that they travel the same path as the individual displacement of the internal piston. This corresponds to a change in the transmission ratio.

[0075] When transitioning from the second state to the first state, i.e., from line U2 to line U1, the above process will proceed in reverse order. Importantly, the two pistons 4 and 5, or pressure segment 4A and piston segment 5A, will separate again, and there will be no negative pressure or suction between pistons 4 and 5, or piston segments 4A and 5A. To prevent this, a gap 9 is constructed.

[0076] This is based on Figure 1-5 This is achieved by means of the sealing geometry or sealing device 10 between the two pistons 4 and 5 or between the piston section 5A and the pressure section 4A.

[0077] A sealing device 10 is disposed between piston section 4A and pressure section 5A. The sealing diameter is positioned as far to the outside as possible to maximize the effective area, i.e., the effective loading area 7, in the second stage or second state. The sealing device 10 has a seal, such as a flat seal or an O-ring.

[0078] List of reference numerals 1. Separation System 2. Shell 3 Piston assembly 4. External piston 4A Pressure Section 4B Stop Section 5. Internal piston 5A Piston Section 6. Piston rod section 7 Loading area 8 steps / protrusions 9 gaps 10 Sealing device 11 Stop 12 Seals 13. Seals 100 Clutch Device 101 Joint support 102 Clutch 103 Return Spring 104 Middleware D pressure chamber D1 Second Pressure Surface D2 Second Pressure Surface D3 Third Pressure Surface A. Longitudinal axis

Claims

1. A separation system (1) for operating a clutch device (100), comprising: - Casing (2), which extends along the longitudinal axis (A), - A piston device (3) for moving the engagement support (101). - wherein the piston device (3) and the housing (2) define a pressure chamber (D) for the hydraulic medium. -The piston device (3) wherein the piston device (3) has an external piston (4) that is movable relative to the housing (2) along the longitudinal axis (A). -The outer piston (4) has a pressure section (4A) with a third pressure surface (D3) oriented toward the pressure chamber (D). -The piston assembly (3) wherein the piston assembly (3) has at least one internal piston (5) which is movable relative to the external piston (4). -The at least one inner piston (5) has a piston section (5A) and a piston rod portion (6) guided in the outer piston (3). -The piston section (5A) has a first pressure surface (D1) that faces the pressure chamber (D) and is oriented toward the rod side of the piston rod. -The piston section (5A) therein has a second pressure surface (D2), which faces the pressure chamber (D) and is oriented toward the side opposite to the piston rod. -The piston device (3) therein is designed such that, a. In a first state, the piston section (5A) of the at least one inner piston (5) and the pressure section (4A) of the outer piston (4) are spaced apart from each other in the axial direction (A), thereby in the first state, the difference between the first and second pressure surfaces (D1, D2) can be used for pressurization with a hydraulic medium, and b. In the second state, the piston section (5A) of the at least one inner piston (5) and the pressure section (4A) of the outer piston (4) are adjacent to each other, thereby in the second state, at least the second pressure surface (D2) of the piston section (5A) can be used for pressurization.

2. The separation system according to claim 1, -The difference between the first pressure surface (D1) and the second pressure surface (D2) constitutes the effective loading area (7), and the effective loading area is equal to at least 10% of the second pressure surface (D2).

3. The separation system (1) according to claim 1 or 2. - wherein the piston rod portion (6) is adjacent to the piston section (5A) associated with the piston rod portion via a boundary surface in the direction of the longitudinal axis (A), and - wherein the boundary surface corresponds to the difference between the first and second pressure surfaces (D1, D2).

4. The separation system (1) according to any one of the preceding claims. - wherein the piston section (5A) has, when viewed along the longitudinal axis (A), a step (8) or protrusion (8) extending away from the piston section (5A) and the first pressure surface (D1), and -The protrusion (8) is arranged in the radial outer region of the piston section (5A).

5. The separation system (1) according to any one of the preceding claims. -The piston section (5A) has a step (8) or a protrusion (8) when viewed along the longitudinal axis (A). -The protrusion (8) can be at least partially sealed by the sealing device (10), and -The sealing device (10) is arranged circumferentially along the protrusion (8) or in the radially outer or inner region of the protrusion (8).

6. The separation system (1) according to any one of the preceding claims. -The piston section (5A) wherein the piston section (5A) has reinforcing ribs when viewed in the longitudinal direction (A), the reinforcing ribs causing the pressure surface of the pressure section (4A) of the outer piston (4) to deform upon contact, thereby achieving a sealing effect.

7. The separation system (1) according to any one of the preceding claims. - wherein at least one of the inner pistons (5) is made of a harder material than the outer piston (4).

8. The separation system (1) according to any one of the preceding claims. -The external piston (4) has a stop section (4B) having a stop portion (11) that abuts against the housing (2) to restrict entry into the housing (2).

9. The separation system (1) according to any one of the preceding claims. - wherein the external piston (4) or the pressure section (4A) of the external piston has a seal (12) for sealing relative to the housing (2), and -The at least one internal piston (5) or the piston rod portion (6) of the at least one internal piston has a seal (13) for sealing relative to the external piston (4).

10. A clutch device (100) for a motor vehicle, comprising: -The separation system (1) according to any one of the preceding claims, and -A connecting support (101) connected to one end of the piston rod portion (6) of the at least one internal piston (5).

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