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    • 专利摘要:
    DEVICE FOR HYDRAULIC ACTIVATION OF A MOTOR VEHICLE FRICTION CLUTCH. The invention relates to a hydraulic drive device (10) for a motor vehicle friction clutch (12), comprising: a manually-activated main cylinder (16), the actuation of which is detected by a sensor (14) and which it has a main pressure chamber (18) which in a resting configuration is in fluid connection with a reservoir (22) by means of a replacement region (20), a slave arrangement (26), comprising a slave pressure chamber (24) and having a slave cylinder (28) which is functionally connected to said motor vehicle friction clutch; a pressure line (30) that connects the main pressure chamber to the slave pressure chamber and in which an electrically actuated valve arrangement (38) that is connected, on the inlet side, to the reservoir and can be connected, on the side outlet, to the pressure line; and a control unit (40) to which the electrical parts are connected (sensor, valve arrangement, motor pump). The valve arrangement comprises, connects in parallel, an electrically actionable proportional valve (42) and a first check valve (44) that blocks in the direction of the main pressure chamber (18), and the motor pump is (... ).
    公开号:BR112016017325B1
    申请号:R112016017325-2
    申请日:2015-01-21
    公开日:2021-02-02
    发明作者:Wilhelm Heubner
    申请人:Fte Automotive Gmbh；
    IPC主号:
    专利说明:

    TECHNICAL FIELD
    [001] The present invention relates to a device for hydraulic actuation of a motor vehicle friction clutch according to the preamble of claim 1. In particular, the invention relates to such a device as used in motor vehicles with starter systems / extended stop and for this purpose allowing manual as well as automatic hydraulic actuation of the motor vehicle friction clutch. PREVIOUS TECHNIQUE
    [002] A conventional hydraulic clutch drive for motor vehicles comprises a main cylinder, which is connected with a compensation reservoir filled with hydraulic fluid and which can be activated, for example, by means of a clutch pedal. The master cylinder is hydraulically connected to a slave cylinder by means of a pressure line so that the pressure generated in the main cylinder by pressing the clutch pedal is transmissible to the slave cylinder by means of the fluid column in the pressure line. As a result, the motor vehicle's friction clutch release bearing is driven by the slave cylinder with a driving force, in order to separate the clutch pressure plate from the driven clutch plate by means of a release mechanism and therefore, to separate the engine from the transmission of the motor vehicle.
    [003] It has already been proposed (see, for example, the descriptive reports of documents DE 41 21 016 A1 and DE 10 2007 002 842 A1) for automatic hydraulic actuation (partially) of the motor vehicle's friction clutch to extend the actuation of the clutch hydraulic by a hydraulic pressure source (motor pump) that can be placed in fluid connection by means of an electrically controllable valve arrangement with the pressure line between the manually actuated main cylinder and the slave cylinder. The reasons for the (partially) automatic actuation of the friction clutch for motor vehicles are, at this moment, in the time collector: in the first case, mention can be made of the desired extension of the known start / stop systems of motor vehicles with manual transmissions , in which, to reduce fuel consumption, the internal combustion engine is switched off when it changes to the neutral environment and separates the clutch and is switched on again when the clutch pedal is activated, for the so-called “start / stop systems in the clutch ”, In which to switch off the internal combustion engine it is no longer necessary to switch to the neutral environment (see, for example, WO 2000/24603 A1 specification), and which also allows the so-called“ engineless operation ”, or that is, rolling with the gear engaged and turning off the internal combustion engine. Then, it is possible to avoid that, by the (partially) automatic clutch operation, damage and excessive wear due to misuse, that is, starting in the 'wrong' gear, 'sudden gripping' or 'not fully pressing' the clutch pedal , etc. In addition, it is also possible to implement assistance systems, which, through an appropriate intervention in the activation of the clutch, allow, for example, greater comfort in bottled traffic, avoid 'stopping' the internal combustion engine or 'disarming' dangerous states (see descriptive report of document DE 10 2007 002 842 A1), in which, after the recognition of a critical path situation, for example, a risk of collision, by a “pre-insurance” sensor system of the internal combustion engine is dissociated drive wheels by automatically disengaging the clutch as soon as the internal combustion engine can no longer reduce the effect of a service brake on the motor vehicle.
    [004] With regard to the device, the specification of document DE 10 2007 002 842 A1, which defines the preamble of claim 1, describes a hydraulic clutch actuation with a main unit, which is manually activated by means of a pedal detected and that has a piston working chamber, which in a resting configuration is in fluid connection with a hydraulic reservoir through a replacement region, a slave unit, which has a piston working chamber and which is operationally connected with the friction clutch of the motor vehicle, and a pressure line for hydraulic connection of the piston chambers of the main unit and slave unit. In addition, a hydraulic pump hydraulically connected on the inlet side with the hydraulic reservoir and actuated by an electric motor is provided, at the pump outlet of the pump being hydraulically connectable with the pressure line, which serves for which is a valve arrangement of actionable control electrically connected to the pressure line. Finally, the prior art system has a control unit (CAN bus, control circuit) with which the pedal sensor, hydraulic pump arrangement and control valve for manual or automatic activation of the friction clutch for motor vehicles are connected electrically.
    [005] Safety in the event of a power supply failure is, in fact, guaranteed in this prior art as the control valve arrangement is spring-tilted in a configuration that connects the piston working chambers of the main unit and the slave unit. However, from safety aspects, this prior technique needs to be improved as it is not easily possible for the driver to intervene in an automatic clutch process by pressing the pedal.
    [006] The same applies to the prior art according to the specification in document DE 41 21 016 A1. In addition, although the device disclosed is intended, in terms of object, to combine the advantages of the two drive systems (automatic and manual), for this purpose there is a substantial expenditure on technical hardware with several valve and pressure blocks or energy stores. OBJECT
    [007] The purpose of the invention is to provide, for the hydraulic actuation of a motor vehicle friction clutch, a device that avoids the above mentioned disadvantages and that, in comparison with the prior art described makes it possible, in particular, with a simple construction, perform - for the most diverse purposes - (partially) automatic clutch actuation processes in which the driver can, however, intervene at any time, without problems. ILLUSTRATION OF THE INVENTION
    [008] The object is filled by the resources indicated in claim 1. Advantageous or convenient developments of the invention are the subject of claims 2 to 7.
    [009] According to the invention, a device for hydraulic actuation of a motor vehicle friction clutch comprises a manually activated master cylinder, the actuation of which is detected by a sensor and which has a main pressure chamber which in a configuration rest is in fluid connection with a reservoir by means of a replacement region, a slave arrangement, which has a slave pressure chamber and which comprises at least one slave cylinder operatively connected with the motor vehicle friction clutch, the pressure for hydraulic connection of the main pressure chamber with the slave pressure chamber, a motor pump, which is connected hydraulically on the side of the inlet with the reservoir and the outlet of the pump from which it can be connected hydraulically with the pressure line, a electrically actuated valve arrangement connected to the pressure line, and a control unit with which the sensor, the motor pump and the arrangement the valve valves are, for manual and / or automatic activation of the electrically connected friction clutch of the motor vehicle, with the feature that the valve arrangement comprises, in parallel connection, an electrically actionable proportional valve and a first check valve that locks in the direction of the main pressure chamber, the motor pump being connected hydraulically to the pressure line by means of a second check valve, which locks in the direction of the motor pump, between the valve arrangement and the slave pressure chamber .
    [0010] In other words, the electrically actionable valve arrangement divides the pressure line between the main pressure chamber and the slave pressure chamber into a line section on the master side and a line section on the slave side. From not only the main cylinder (manually) through the line section on the main side, but also the motor pump (automatically), through the pump outlet, the volume of hydraulic fluid can be displaced in or in the slave side line and accumulated pressure, which when the proportional valve is closed is “closed” by the non-return valves in relation to the main cylinder or a motor pump, in order to load the slave pressure chamber and, therefore, actuate, for example, disengaging, the friction clutch for motor vehicles. Through the proper activation of the proportional valve and the defined opening of the same produced, it is then possible - without activating the main cylinder - to maintain the pressure on the slave side when, in a given case, the motor pump is running or to reduce it in the form defined by means of the proportional valve, in order, for example, to reengage the friction clutch of the motor vehicle, in which case the hydraulic fluid flows out of the line section of the slave side through the proportional valves returns to the reservoir through the main side line section, the main pressure chamber and the properly sized refueling region of the main cylinder. In the case of manual actuation of the main cylinder, the hydraulic connection between the main pressure chamber and the replacement region of the main cylinder is interrupted in a manner known per se (for example, “limit switch” of the refueling hole, which is in the cylinder housing, by the primary sealing element on the piston or by a central valve on the main piston, which in the case of movement of the piston outside the resting configuration closes automatically), so that the hydraulic relief of the slave section of the line by proportional valve is no longer possible. Thus, a switching valve function is also transmitted to the main cylinder together with its refueling system known per se, such a function allows the actuator to intervene at any time and directly, this is also very quickly, in an automatic actuation of the motor vehicle friction clutch by manual actuation (pedal) of the main cylinder without additional valves and / or other components that are necessary for this purpose. Thus, with a very simple circuit format, a device is created, which is improved from safety aspects by comparison with the previous technique described in the introduction, for the hydraulic actuation of a motor vehicle friction clutch, by which the Most (partially) automatic triggering processes can be performed on the device.
    [0011] In principle, it is conceivable to build the proportional valve so that it is spring-tilted in a zero-lock setting configuration. However, particularly with regard to the safety fault, it is preferred that the proportional valve is spring-tilted in the zero-pass configuration.
    [0012] In addition, it can be provided so that the slave cylinder, which has a slave piston mechanically connected to the friction clutch of the motor vehicle, has a limit that serves the purpose of limiting the driving path of the slave piston. Thus, it is possible in a simple way to prevent ‘over-pressure’ and possibly the damage that accompanies the motor vehicle’s friction clutch as measures to limit the driving stroke are not accepted in the clutch itself.
    [0013] Whether the device is to be used for the hydraulic actuation of a motor vehicle friction clutch with a constantly elevating characteristic curve (for example, with an approximately linear plot of the actuation force along the actuation stroke) is basically possible in a simpler mode of the device for distribution with a path sensor in the slave arrangement. However, it is preferable if a travel sensor, which is electrically connected with the control unit and by which a representative of the drive stroke on the slave side of a state disengaged from the motor vehicle's friction clutch is detectable, is provided in the slave arrangement. This makes the most diverse automatic drives possible, optionally even overlapping the manual drive, of friction clutches for motor vehicles with any desired characteristic curve, for example - as is often the case - extending in the form of an "arched rear" .
    [0014] Additionally, according to the concept of the invention, the slave arrangement may comprise a portioning cylinder, which is hydraulically connected upstream of the slave cylinder and which has the slave pressure chamber. Thus, in particular, existing clutch actuation systems can be extended in scope in a simple way, keeping the main and slave cylinders already supplied in order to allow (in part) automatic clutch actuations.
    [0015] Finally, in this regard, it is advantageous if at least the reservoir, the motor pump, the second check valve and the portioning cylinder, optionally together with the travel sensor, are combined to form a module , which can be arranged on the motor vehicle in a simple and easy to assemble manner, as well as regardless of the position of the main and slave cylinders, for example, in a place that is better protected from external influences (temperature, etc. ) and is more easily accessible and / or less confined. The module then preferably also includes the valve arrangement and, optionally, the control unit, so that the components provided for the automatic actuation of the clutch are integrated to the greatest degree. BRIEF DESCRIPTION OF THE DRAWINGS
    [0016] The invention is explained in more detail below on the basis of the preferred modalities with reference to the schematic accompanying drawings, in which the same reference numbers denote the same or corresponding parts and in which:
    [0017] Fig. 1 shows a circuit diagram of a device for hydraulic actuation of a motor vehicle friction clutch according to a first embodiment of the invention, with a slave arrangement with detected path,
    [0018] Fig. 2 shows a circuit diagram of a device for hydraulic actuation of a motor vehicle friction clutch according to a second modality of the invention, with a limit, which is additional by comparison with the first modality, for limitation of the drive path of the slave arrangement, and
    [0019] Fig. 3 shows a circuit arrangement of a device for hydraulic actuation of a motor vehicle friction clutch according to a third embodiment of the invention, in which the slave arrangement comprises a portioning cylinder hydraulically connected upstream of the slave cylinder.
    [0020] The illustration of the details of the clutches and the elements (manual transmissions, internal combustion engine) connected operationally by means of clutches has been dispensed with in the drawings and in the following description, because these details or elements and their function are sufficiently known to the person skilled in the art and explanations regarding them do not appear to be necessary for an understanding of the present invention. DETAILED DESCRIPTION OF THE MODALITIES
    [0021] In Fig. 1, reference number 10 denotes, in general, a device for hydraulic actuation of a motor vehicle friction clutch 12. As will be described in more detail below, device 10 comprises an activable main cylinder manually 16, the actuation of which is detected by a sensor 14 and which has a main pressure chamber 18 which in a resting configuration is in fluid connection with a reservoir 22 by means of a replacement region 20, a slave arrangement 26 , which has a slave pressure chamber 24 and which comprises one or at least one slave cylinder 28 operatively connected with the motor vehicle friction clutch 21, a pressure line 30 for hydraulic connection of the main pressure chamber 18 with the pressure chamber slave pressure 24, a motor pump 32 with a hydraulic pump unit M, the inlet of the pump 34 of which is hydraulically connected with the reservoir 22, while its outlet of the pump 36 is hydraulic connectable with pressure line 30, an electrically actuated valve arrangement 38, which is connected to pressure line 30, and a control unit 40, with which (inter alia) sensor 14, motor pump 32, that is, the M pump unit thereof, and valve arrangement 38 are electrically connected for manual and / or hydraulic actuation - which will be explained further - of the motor vehicle friction clutch 12. It is significant that valve arrangement 38 comprises, in parallel connection, an electrically actuated proportional valve 42 and a blocking of the first check valve 44 in the direction of the main pressure chamber 18, while the motor pump 32 is hydraulically connected with the pressure line 30 may in the middle of a second non-return valve 46, which locks in the direction of motor pump 32, between valve arrangement 38 and slave pressure chamber 24. Non-return valves 44, 46 can be spring-tilted within their respective settings called them, but this is not illustrated in the figures.
    [0022] The main cylinder 16 comprises, in a manner known per se, a housing of the main cylinder 48 which together with a main piston 50 limits the main pressure chamber 18. A piston rod 52 is pivotally connected with the main piston 50 and with a pedal 54. The pedal 54 can be rotated around a pivot holder 56 by manual actuation (foot) in order to axially move the main piston 50 in the main cylinder housing 48 by the piston rod 52 and thus increase a pressure in the main pressure chamber 18 as well as to move the hydraulic fluid from the main pressure chamber 18 to the pressure line 30. A replacement spring, which is optionally supplied on pedal 54 or in or inside the main cylinder 16, to the main piston 50 is not shown in this document.
    [0023] In the illustrated embodiment the main piston 50 is a so-called 'shaft piston', in which a (secondary) sealing element 58, which seals the main cylinder 16 in relation to the environment and which is fixed in relation to the housing, cooperates with a guide surface provided on the piston shaft, while a (primary) sealing element 60, which is mounted on the piston head, cooperates with a guide surface on the cylinder housing in order to seal the main pressure chamber 18 by the element seal 60 after the 'excessive travel' of the replacement connection with reservoir 22 (replacement region 20). However, the main piston could just as well be a 'classic' piston that has two 'in-transit' sealing elements (primary and secondary) cooperating with a guide surface in the housing, or a so-called 'submersible piston', the guide surface the piston of which it cooperates with at least one (primary) sealing element fixed in relation to the housing and the pressure chamber. In addition, the piston of the main cylinder could be provided with a central valve that in a resting configuration of the main piston connects the main pressure chamber with the replacement region. This known variant of the main cylinder is common anywhere as a consequence of the axial displacement of the main piston in the housing of the main cylinder outside its illustrated resting configuration the connection, which is produced through the replacement region, with the reservoir is interrupted , after which a pressure first accumulates in the main pressure chamber.
    [0024] In the present case, sensor 14 is a sensor fixed to the cylinder housing and sensitive to magnetic flux, for example, a Hall sensor, which cooperates with a signal element, which is mounted on the main piston 50 , in the form of a permanent magnet (not shown) in order to detect a stroke of the main piston 50. Sensor arrangements of this type in the hydraulic main cylinders are described, for example, in the descriptive reports of documents EP 1 369 597 A2 and EP 1 489 385 A2 of the same applicant, to which reference is made expressly in relation to the constructive form and function. The sensor 14 provides a voltage signal dependent on the U path, which is conducted via an electrical signal line 62 to the electronic control unit 40.
    [0025] Valve arrangement 38 divides, by its parallel connection of proportional valve 42 and first check valve 44, the pressure line 30 into a section of the pressure line on the side of the transmitter 64 permanently connected with the main pressure chamber 18 and a section of the slave side pressure line 66 constantly connected with the slave pressure chamber 24. The proportional valve 42 illustrated in this document is a 2/2-way proportional valve, which is spring-biased by means of a valve spring 68 in a zero configuration that allows passage and can be closed in the manner defined by an electromagnetic unit 70 against the force of valve spring 68. To supply the current to the electromagnetic unit 70, it is connected with the control unit 40 can in the middle of an electrical control line 72. As far as the proportional valve construction 42 is concerned, it can be performed as, for example, an incl valve inhaled by a 2/2-way spherical seat spring that can be electrically operated in a zero-pass configuration, as is known in the beginning of document DE 196 33 420 A1 (see Fig. 4) by the same applicant.
    [0026] The pump outlet 36 of the motor pump 32 is connected to the pressure line section of the slave side 66 by means of a conveyor line 74 to which the second check valve 46 is thus connected which blocks the direction of the flow. motor pump 32. The inlet of the pump 34 of the motor pump 32 is in permanent fluid connection with the reservoir 22 by means of a suction line 76. For supplying the current to or activating the electric pump unit M, this is connected with control unit 40 it can be via an electrical control line 78. Pump types, such as, for example, gear pumps, bearing cell pumps, vane cell pumps, and radial or axial piston pumps can be used for motor pump 32 as they are in a position to generate pressures (up to 40 bar) usual for hydraulic clutch drives. For the present use, it is, in principle, sufficient if the motor pump 32 is constructed as a constant transport pump that provides a constant volume flow for a predetermined speed of rotation of the pump unit M. The drive of the pump M can, optionally, be controllable in the rotation speed in order to be able to react to possible fluctuations in pressure and also to make possible, by low rotation speeds, a finely measurable “introduction” or “filling” of hydraulic fluid.
    [0027] The slave cylinder 28 comprises, in a manner known per se, a housing of the slave cylinder 80 in which a slave piston 82 is guided to be longitudinally displaceable and sealed at the circumference, (in a manner not shown in more detail) in in relation to the slave cylinder housing 80. The slave piston 82 in conjunction with the housing of the slave cylinder 80 in this document delimits the slave pressure chamber 24, which can be charged with the hydraulic fluid through a pressure connection 84. For to this end, the pressure line 30 is connected by its pressure line section on the slave side 66 with the pressure connection 84. Mounted on the slave piston 82 on the same side as the slave pressure chamber 24 is a piston rod 86 by means of which the slave cylinder 28 is in operational connection in a manner known per se with the friction clutch 12, with a compression spring 88 arranged in the slave pressure chamber 24 keeping the components that participate on the side of the cylinder and the side in contact with the clutch.
    [0028] In the illustrated embodiment, a path sensor 92 electrically connected to the control unit 40 by means of a signal line 90 is provided in slave arrangement 26, more precisely, the slave cylinder housing 80, whereby the sensor a of a drive path, which is representative of a state disengaged from the friction clutch 12, on the slave side is detectable. As with the main cylinder 16, in this case because it is a sensor that is fixed in relation to the cylinder housing and sensitive to magnetic flux, for example, a Hall sensor, which cooperates with a signal element, which is mounted on the piston slave 82, in the form of a permanent magnet (not shown) in order to detect the drive path of the slave piston 82.
    [0029] Even in the illustrated modality, the slave cylinder 28 is illustrated in the “classic” construction mode, which can similarly be - and due to its very compact annular construction it can, in general, even be preferable in an application real - a so-called “central disengager” or “central engager”, as described, in principle, for example, in the descriptive reports of documents DE 197 16 473 A1 and DE 199 44 083 A1 of the same applicant. In addition, express reference can be made, at this point, for example, to the descriptive reports of documents DE 102 22 730 A1 and DE 20 2006 014 024 U1 of the same applicant with regard to the construction and function of central disengagers with detected path.
    [0030] Before the function - which with respect to the important points is the same for the different modalities - of the hydraulic drive device 10 is explained, it will be briefly described below as the second and third modalities according to Figs. 2 and 3 differ from the first modality previously described (Fig. 1).
    [0031] In the second embodiment according to Fig. 2, the slave cylinder 28 has a limit 94 that serves the purpose of limiting the driving path s of the slave piston 82 mechanically connected with the friction clutch 12, by means of the rod piston 86. As shown in this document, limit 94 can be of annular construction and properly mounted on the inner circumference of the slave cylinder housing 80 and, in particular, as seen in the axial direction at one location of the cylinder slave 28 in which the hydraulically loaded slave piston 82 comes into contact with limit 94 before the piston rod 86 can be moved too far out of the slave cylinder housing 80. An 'overlap' and thus possible damage that accompanies the friction clutch 12 can thus be reliably avoided in a simple manner.
    [0032] In the third embodiment illustrated in Fig. 3 the slave arrangement 26 comprises a portioning cylinder 96, which as seen from the direction of the main cylinder 16 is connected hydraulically upstream of the slave cylinder 28 and has the slave pressure chamber 24 A separation piston 100 is received in a cylinder housing 98 of portioning cylinder 96 to be longitudinally displaceable and to be provided at the circumference of the piston with two axially spaced sealing elements 102 which provide a sliding seal in relation and a surface guide on the inner circumference of the cylinder housing 98. In the cylinder housing 98 the separation piston 100 separates the slave pressure chamber 24 from the slave arrangement 26 from an additional main pressure chamber 104, which for your part is in permanent communication by means of an additional pressure line 106 with an additional slave pressure chamber 108 in the slave cylinder 28 connects operatively with friction clutch 12.
    [0033] The compression spring 110 received in the additional main pressure chamber 104 tilts the separation piston 100 in the direction of the slave pressure chamber 24, that is, for the resting configuration shown on the left in Fig. 3. In the configuration of separation piston 100 resting the additional main pressure chamber 104 is in fluid connection with the reservoir 22 by means of a replacement line 112 in order to provide compensation for temperature expansions, wear path, etc., in the friction clutch 12 or in the slave cylinder 28. In this embodiment the slave arrangement 26 thus includes the slave cylinder 28, the portioning cylinder 96 having the slave pressure chamber 24, the additional pressure line 106 between the cylinders 28, 96, and the replacement 112 from reservoir 22 to additional main pressure chamber 104 in portioning cylinder 96.
    [0034] When the slave pressure chamber 24 is subjected to a hydraulic load through the pressure line section on the slave side 66 of the pressure line 30 the separation piston 100 moves to the right in Fig. 3 against the force of the compression spring 110, in the case of the sealing element 102 on the side of the main pressure chamber, that is, on the right in Fig. 3, separates the replacement connection with the reservoir 22, so that a pressure can build up in the chamber of additional main pressure 104. This hydraulic pressure, for its part, is present, by means of the other pressure line 106, in the additional slave pressure chamber 108 and can act there on the slave piston 82 of the slave cylinder 28 to be effective in terms of drive. Since, in that case, the separation piston 100 cannot move within the portioning cylinder 96 to an arbitrary extent, the portioning cylinder 96 also has a stop function analogous to limit 94 in the second embodiment according to Fig . two.
    [0035] In addition, in the illustrated embodiment, the path sensor described above 92 is supplied in the portioning cylinder 96, that is, attached to the cylinder housing 98 thereof, and cooperates with a signal element (not shown) on the piston of the cylinder. separation 100 in order to detect the stroke of the separation piston 100, which by virtue of the hydraulic connection of the portioning cylinder 96 with the slave cylinder 28 is representative of a disengagement state or an engagement state of the friction clutch 12.
    [0036] Finally, regarding the different modalities, mention can be made of the modular construction of the circuit. Considering that in the modalities according to Figs. 1 and 2, the reservoir 22, the motor pump 32 with the electric pump unit M, the second check valve 46 and the associated hydraulic connections are combined to form a module 114, which can optionally also include the arrangement valve 38 and the control unit 40, in the third embodiment according to Fig. 3, the reservoir 22, the motor pump 32 together with the electric pump unit M, the second check valve 46, the pressure cylinder portioning 96 with travel sensor 92 (if present) and associated hydraulic connections are combined to form a module 116. As indicated in 116 ', this module may, in addition, include valve arrangement 38 and the control unit 40, so that only module 116 'would have to be inserted as a separate component between the main cylinder and the slave cylinder of a conventional manually operated hydraulic clutch actuation system, in order to also (partially) perform actuations of automatic clutches.
    [0037] The function of the hydraulic drive device 10 will be explained briefly below for all common modes, and a distinction must be made between the cases of (A) manual override, (B) 'starter start', (C ) automatic activation and (D) “overlapping” drives. (A) Manual override: The main cylinder 16 is manually operated using the pedal 54. The hydraulic fluid displaced from the main pressure chamber 18 by the main piston 50 travels through the main side pressure line section 64, a free current open proportional valve 42 and / or the first check valve 44 of valve arrangement 38 and the slave line pressure line section 66 of the pressure line 30 to the slave pressure chamber 24 on the slave cylinder 28 (Figs 1 and 2) or in the intermediate measurement or portioning cylinder 96 (Fig. 3). As a result, the slave piston 82 is directly (Figs. 1 and 2) or indirectly (Fig. 3: by means of the separation piston 100, the additional main pressure chamber 104, the additional pressure line 106 and the pressure chamber additional slave 108) hydraulically loaded and displaced so as to disengage the friction clutch 12.
    [0038] When a return stroke (release of pedal 54) occurs, hydraulic fluid flows back from the slave pressure chamber 24 through the slave line pressure line section 66, the open current proportional valve 42 of the valve arrangement 38 and the pressure line section of the main side 64 of the pressure line 30 inside the main pressure chamber 18 of the main cylinder 16. Equalizing the volume to provide compensation for thermal expansions, friction clutch wear 12 or deformations of the friction clutch 12 at high speeds of rotation occur through the equalization system of the main cylinder 16 (replacement region 20) or portioning cylinder 96 (replacement line 112) in the case of Fig. 3.
    [0039] (B) Prevention of the “starting start” (also called Peak Torque Limiting function (PTL) in technical terminology): If by the path sensor (s) 14, 92 in the main cylinder 16 and / or cylinder slave 28 or portioning cylinder 96 there is a recognition of excessive closing speeds of the friction clutch 12, with the risk of excessive torque spikes caused by the energy stored in the inert masses of the clutch and internal combustion engine, the proportional valve 42 of the valve arrangement 38 can be fully or partially closed by properly activating the electromagnetic unit 70 by means of the control unit 40 and the closing speed of the friction clutch 12 can be regulated to a tolerable amount.
    [0040] (C) Automatic activation: The electric pump unit M of the motor pump 32 and the proportional valve 42 of the valve arrangement 38, more specifically the electromagnetic unit 70 of the same, are activated by means of the electronic control unit 40 , which also reads the signals from the travel sensors 14, 92 (and / or, optionally, pressure sensors present). If the control unit 40 receives a command to open or disengage the friction clutch 12, it connects to the electric pump unit M, after which the hydraulic fluid is sucked by the motor pump 32 from the reservoir 22 through from the suction line 76 and transported through the conveyor line 74 and the second check valve 46 to the pressure line section on the slave side 66 of the pressure line 30, and supplies current to the electromagnetic unit 70 of the proportional valve 42 , with a value corresponding to the expected need. The proportional valve 42 remains closed until the pressure, which corresponds to the current supplied, in the pressure line section of the slave side 66 is reached and the proportional valve 42 opens automatically, in order to maintain the force balance between the magnetic force and the hydraulic forces on the proportional valve 42 (dynamic pressure principle), or the desired position is reported by the travel sensor 92 to the control unit 40 and the valve current on the proportional valve 42 is withdrawn via the control unit 40. In this case, the motor pump 32 can be switched off, the hydraulic pressure in the system being maintained by means of the closed proportional valve 42 and two check valves 44, 46.
    [0041] If the friction clutch 12 is to be closed again or reengaged, then the valve current in the proportional valve 42 is reduced by the control unit 40 and the movement of the slave piston 82 in the slave cylinder 28 is properly adjusted with the help of the path signals from the path sensor 92. The hydraulic fluid, in this case, flows from the proportional valve 42, through the pressure line section on the main side 64 of the pressure line 30, the main pressure chamber 18 of the main cylinder 16 arranged in the resting configuration and the appropriately sized equalization system (replacement region 20) back to the reservoir 22.
    [0042] (D) “Overlapping” drives: Manual override (see A) is reported by the travel sensor 14 from the main cylinder 16 to the control unit 40. Automatic drives (see C) can therefore be excluded through control unit 40 if a manual override is in progress. However, it can also be advantageous, for example, to protect the friction clutch 12 against excessive wear, to fully open a friction clutch that is incompletely open or disengaged 12 insofar as a critical safety situation cannot arise as a consequence. In this case, the electromagnetic unit 70 of the proportional valve 42 would be supplied with power by the control unit 40, which connects the electric pump unit M of the motor pump 32 and admits the hydraulic fluid until the friction clutch 12 is completely open or disengaged, after which the proportional valve 42 can be reopened. In the case of manual closing or engagement of the friction clutch by means of the pedal 42, the admitted volume of hydraulic fluid in the pressure line 30 then must escape through the replacement system (replacement region 20) of the main cylinder 16 to the reservoir 22.
    [0043] If the automatic activation is in progress and the driver additionally activates the pedal 54 in order to manually disengage the friction clutch 12, which is recognized by means of the sensor 14 in the main cylinder 16, then the automatic activation is interrupted by the control unit 40. The volume, which is already or still present in the slave cylinder 28 or portioning cylinder 96, of the hydraulic fluid reduces the possible drive path in the main cylinder 16 and indicates to the driver that he or she has been involved in a automatic process. However, the driver is always in charge and possible defective control actions on the control unit can be deactivated by the driver. After the driver's intervention, the system remains passive until the clutch process is completed. In the case of manual closing or engagement of the friction clutch 12 the volume, which was previously stored by the pump in the motor 32 in the pressure line 30, of the hydraulic fluid must then escape again through the replacement system (replacement region 20) from main cylinder 16 to reservoir 22.
    [0044] A hydraulic drive device for a motor vehicle friction clutch is revealed, comprising a manually-activated main cylinder, the drive of which is detected by a sensor, with a main pressure chamber, which in the resting configuration is in fluid connection to a reservoir by means of a replacement region, a slave arrangement, which has a slave pressure chamber and which comprises a slave cylinder operatively connected with a motor vehicle friction clutch, a pressure line, which connects the chamber main pressure valve with the slave pressure chamber and to which an electrically actionable valve arrangement is connected, a motor pump, which is connected on the inlet side with the reservoir and is connectable on the outlet side with the pressure line, and a control unit with which the electrical parts (sensor, valve arrangement, motor pump) are connected. According to the invention, the valve arrangement comprises, in parallel connection, an electrically actionable proportional valve and a blocking of the first check valve in the direction of the main pressure chamber, while the motor pump is connected by means of a second valve check valve, which locks in the direction of the motor pump, between the valve arrangement and the pressure chamber slave to the pressure line. REFERENCE NUMBER LIST 10 hydraulic actuating device 12 friction clutch 14 sensor 16 main cylinder 18 main pressure chamber 20 spare region 22 reservoir 24 slave pressure chamber 26 slave arrangement 28 slave cylinder 30 pressure line 32 motor pump 34 inlet pump 36 pump outlet 38 valve arrangement 40 control unit 42 proportional valve 44 first check valve 46 second check valve 48 main cylinder housing 50 main piston 52 piston rod 54 pedal 56 pivot support 58 sealing element ( 60 sealing element (primary) 62 signal line 64 pressure line section on the main side pressure line section on the slave side valve spring 66 68 70 72 74 76 78 80 82 84 86 88 90 92 94 96 98 100 102 104 106 108 110 112 114 116 s MU electromagnetic unit electrical control line conveyor line suction line electrical control line cylinder housing scr avo slave piston pressure connection piston rod compression spring signal line limit travel sensor portioning cylinder cylinder housing separating piston sealing element additional main pressure chamber additional pressure line additional slave pressure chamber compression line spare module, 116 'stroke module, drive path electrical pump unit voltage signal
    权利要求:
    Claims (7)
    [0001]
    1. DEVICE (10) FOR HYDRAULIC ACTIVATION OF A MOTOR VEHICLE FRICTION CLUTCH (12), comprising a manually-activated main cylinder (16), the actuation of which is detected by a sensor (14) and which has a pressure chamber main (18) which in a resting configuration is in fluid connection with a reservoir (22) by means of a replacement region (20), a slave arrangement (26), which has a slave pressure chamber (24) and comprising at least one slave cylinder (28) operatively connected with the motor vehicle friction clutch (12), a pressure line (30) for hydraulic connection of the main pressure chamber (18) with the slave pressure chamber (24 ), a motor pump (32, M), which is connected hydraulically on the inlet side with the reservoir (22) and the pump outlet (36) from which it can be connected hydraulically with the pressure line (30), a electrically actionable valve arrangement (38) connected to the pressure line (3 0), and a control unit (40), with which the sensor (14), the motor pump (32, M) and the valve arrangement (38) are electrically connected for manual and / or automatic clutch activation motor vehicle friction valve (12), characterized by the valve arrangement (38) comprising, in parallel connection, an electrically actionable proportional valve (42) and a blocking of the first check valve (44) in the direction of the main pressure chamber (18) , the motor pump (32, M) being connected hydraulically to the pressure line (30) by means of a second check valve (46), which locks in the direction of the motor pump (32, M), between the arrangement valve (38) and the slave pressure chamber (24).
    [0002]
    2. DEVICE (10), according to claim 1, characterized in that the proportional valve (42) is inclined by springs in a zero-pass configuration.
    [0003]
    3. DEVICE (10) according to claim 1 or 2, characterized in that the slave cylinder (28) comprises a slave piston (82), which is mechanically connected with the motor vehicle friction clutch (12), and a limit ( 94) which serves the purpose of limiting a slave piston drive path (s) (82).
    [0004]
    DEVICE (10) according to any one of claims 1 to 3, characterized in that a path sensor (92) electrically connected with the control unit (40) is provided in the slave arrangement (26), by which a sensor Drive path (s) on the slave side and representative of a motor vehicle friction clutch disengagement state (12) being detectable.
    [0005]
    DEVICE (10) according to any one of claims 1 to 4, characterized in that the slave arrangement (26) comprises a portioning cylinder (96) which is hydraulically connected upstream of the slave cylinder (28) and which has the chamber slave pressure (24).
    [0006]
    6. DEVICE (10) according to claim 5, characterized by at least the reservoir (22), the motor pump (32, M), the second check valve (46) and the portioning cylinder (96), optionally together with the travel sensor (92), be combined to form a module (116, 116 ').
    [0007]
    7. DEVICE (10), according to claim 6, characterized in that the module (116 ') also includes the valve arrangement (38) and optionally the control unit (40).
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    同族专利:
    公开号 | 公开日
    MX2016009773A|2017-01-26|
    CN106104056A|2016-11-09|
    JP2017504773A|2017-02-09|
    DE102014001073A1|2015-07-30|
    US9803705B2|2017-10-31|
    KR101911157B1|2018-10-23|
    US20160341265A1|2016-11-24|
    CN106104056B|2018-07-17|
    WO2015113744A1|2015-08-06|
    KR20160114168A|2016-10-04|
    EP3099955B1|2017-10-04|
    EP3099955A1|2016-12-07|
    JP6411525B2|2018-10-24|
    ES2647793T3|2017-12-26|
    PL3099955T3|2018-01-31|
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    法律状态:
    2020-04-14| B06U| Preliminary requirement: requests with searches performed by other patent offices: suspension of the patent application procedure|
    2020-12-08| B09A| Decision: intention to grant|
    2021-02-02| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 21/01/2015, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    DE102014001073.2|2014-01-30|
    DE102014001073.2A|DE102014001073A1|2014-01-30|2014-01-30|Device for the hydraulic actuation of a motor vehicle friction clutch|
    PCT/EP2015/000104|WO2015113744A1|2014-01-30|2015-01-21|Device for hydraulically actuating a motor vehicle friction clutch|
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