Braking device and method for operating a breaking device

Abstract

The invention relates to a brake device and a method for operating a brake device, wherein said brake device comprises an actuation device, also a booster device, in particular having an electro-hydraulic drive, a piston cylinder device (main cylinder) in order to supply hydraulic pressure medium to the brake circuits, a valve device for controlling or regulating the supply of the pressure medium and an electronic control or regulating device (ECU). According to the invention provision is made for additional pressure medium volume to be supplied in a controlled manner to at least one brake circuit by means of a further piston cylinder device, in particular a double stroke piston (10) and at least one valve (AS) controlled by the control or regulating device (ECU).

Claims

1. An actuation device for a vehicle brake, comprising: an actuation device in the form of a brake pedal, at least one piston cylinder unit which is connected to the vehicle brake via a hydraulic brake circuit to supply pressure medium to the brake circuit and to apply pressure on the vehicle brake, and an electromotive drive for the piston cylinder unit, wherein the at least one piston cylinder unit includes a piston arranged to be directly driven by the electromotive drive, wherein said piston is arranged to supply pressure medium, via a first pressure chamber, to the brake circuit in a controlled manner in both movement directions of the piston, forward stroke and return stroke, and wherein a further piston is provided in at least one piston-cylinder unit, wherein the further piston is hydraulically driven and is configured to transfer pressure of the directly-driven piston to a second pressure chamber, wherein the second pressure chamber is connected to a further brake circuit.

2. The actuation device according to claim 1, wherein the piston cylinder unit forms an annular space from which the pressure medium is enabled to be supplied to at least one brake circuit.

3. The actuation device according to claim 1, further comprising valves configured to control supply of the pressure medium.

4. The actuation device according to claim 1, wherein the piston supplying the pressure medium in both movement directions is driven by an electric motor.

5. The actuation device according to claim 1, wherein volume control and injection in at least one brake circuit takes place via a return stroke of the piston.

6. The actuation device according to claim 1, wherein supply of the pressure medium by means of the piston in at least two brake circuits takes place simultaneously or serially, and wherein the actuation device further comprises a closing valve.

7. The actuation device according to claim 1, further comprising at least one securing valve provided in a supply line for the pressure medium.

8. An actuation device for a vehicle brake, comprising: an actuation device in the form of a brake pedal, at least one piston cylinder unit which is connected to the vehicle brake via a hydraulic brake circuit to supply pressure medium to the brake circuit and to apply pressure on the vehicle brake, and an electromotive drive for the piston cylinder unit, wherein the at least one piston cylinder unit includes a piston arranged to be directly driven by the electromotive drive, wherein said piston is arranged to supply pressure medium, via a first pressure chamber, to the brake circuit in a controlled manner in both movement directions of the piston, forward stroke and return stroke, and wherein the actuation device further comprises a mechanical coupling in a fallback level and arranged for separating the drive and the piston driven by the drive.

9. The actuation device according to claim 1, further comprising a positioning sensor for the driven piston and configured for controlling supply of the pressure medium.

10. The actuation device according to claim 1, further comprising a reservoir configured to receive pressure medium for pressure reduction in one or more of the brake circuits.

11. The actuation device according to claim 1, wherein a diagnosis of valves and seals takes place during a normal operating process.

12. A double stroke piston for a hydraulic actuation device according to claim 1, wherein the double stroke piston of the hydraulic actuation device is configured to supply pressure medium in both piston movement directions.

13. An actuation device for a vehicle brake, comprising: an actuation device in the form of a brake pedal, at least one piston cylinder unit which is connected to the vehicle brake via a hydraulic brake circuit to supply pressure medium to the brake circuit and to apply pressure on the vehicle brake, and an electromotive drive for the piston cylinder unit, wherein the at least one piston cylinder unit includes a piston arranged to be directly driven by the electromotive drive, wherein said piston is arranged to supply pressure medium, via a first pressure chamber, to the brake circuit in a controlled manner in both movement directions of the piston, forward stroke and return stroke, and wherein a free travel is provided between the brake pedal or a pedal plunger and a spindle or between a coupling plunger and the spindle, wherein the spindle is connected to the piston via a bending rod or a coupling.

14. A method for operating a brake device, wherein said brake device comprises an actuation device having an electro-hydraulic drive, a main piston cylinder device to supply hydraulic pressure medium to brake circuits, a valve device for controlling or regulating supply of the pressure medium, and an electronic control or regulating device (ECU), the method comprising: supplying pressure medium volume in a controlled manner to at least one brake circuit by means of a further piston cylinder device, including a double stroke piston directly driven by the electrohydraulic drive and configured to perform said supplying pressure medium via a pressure chamber to the at least one brake circuit, and by means of at least one valve controlled by the ECU; and supplying pressure medium volume, via a further piston that is hydraulically driven by the double stroke piston, and via a further pressure chamber, to at least one further brake circuit.

15. The method according to claim 14, wherein in a case of low pedal speed, additional pressure medium volume is supplied with pressure in the range of 5 bar, and in the case of high pedal speed with a pressure in the range of 30 bar.

16. The method according to claim 14, further comprising reducing pressure when the pedal stroke is reduced by opening a solenoid valve and volume outflow in a reservoir.

17. An actuation device for a vehicle brake, comprising: an actuation device in the form of a brake pedal, at least one piston cylinder unit which is connected to the vehicle brake via a hydraulic brake circuit to supply pressure medium to the brake circuit and to apply pressure on the vehicle brake, and an electromotive drive for the piston cylinder unit, wherein the at least one piston cylinder unit includes a piston arranged to be directly driven by the electromotive drive, wherein said piston is arranged to supply pressure medium, via a first pressure chamber, to the brake circuit in a controlled manner in both movement directions of the piston, forward stroke and return stroke, and wherein a further piston cylinder unit is provided, wherein the further piston cylinder unit includes a further piston, wherein a working space of the further piston cylinder unit is connected with at least one brake circuit via a hydraulic conduit, wherein the further piston is actuated by the actuating device, and wherein a free travel is provided between the actuating device and the further piston.

18. The actuation device according to claim 17, wherein the piston cylinder unit forms an annular space from which the pressure medium is enabled to be supplied to at least one brake circuit.

19. The actuation device according to claim 17, further comprising valves configured to control supply of the pressure medium.

20. The actuation device according to claim 17, wherein the piston supplying the pressure medium in both movement directions is driven by an electric motor.

21. The actuation device according to claim 17, wherein volume control and injection in at least one brake circuit takes place via a return stroke of the piston.

22. The actuation device according to claim 17, wherein supply of the pressure medium by means of the piston in at least two brake circuits takes place simultaneously or serially, and wherein the actuation device further comprises a closing valve.

23. The actuation device according to claim 17, further comprising at least one securing valve provided in a supply line for the pressure medium.

24. The actuation device according to claim 17, further comprising a mechanical coupling in a fallback level and arranged for separating the drive and the piston driven by the drive.

25. The actuation device according to claim 17, further comprising a positioning sensor for the driven piston and configured for controlling supply of the pressure medium.

26. The actuation device according to claim 17, further comprising a reservoir configured to receive pressure medium for pressure reduction in one or more of the brake circuits.

27. The actuation device according to claim 17, wherein a diagnosis of valves and seals takes place during a normal operating process.

28. The actuation device according to claim 17, wherein a free travel is provided between the brake pedal or a pedal plunger and a spindle or between a coupling plunger and the spindle, wherein the spindle is connected to the piston via a bending rod or a coupling.

Description

DESCRIPTION OF THE FIGURES

(1) They show:

(2) FIG. 1 a brake system with the double stroke piston (DHK) according to the invention;

(3) FIG. 2 a section of the brake system with double stroke piston (DHK) with valve connection;

(4) FIG. 3 a section of the brake system with an alternative valve connection;

(5) FIG. 4 a depiction of the double stroke piston (DHK);

(6) FIG. 5 the temporal volume delivery in three stages;

(7) FIG. 5a a summary concerning stage 1;

(8) FIG. 5b a summary concerning stages 1 and 2;

(9) FIG. 6 a different embodiment of a brake system with a double stroke piston according to the invention;

(10) FIG. 6a an embodiment with idle stroke and injection from an auxiliary piston, wherein in the upper half of the figure the spindle of the drive is connected to the piston by means of a connection element, in particular a bending rod and by means of a coupling in the lower half;

(11) FIG. 7 an embodiment with a device for avoiding the escape of leakage fluid to the outside;

(12) FIG. 8 an alternative valve connection of the double stroke piston (DHK);

(13) FIG. 9 a double stroke piston (DHK) with an expansion for prefilling the brake circuits;

(14) FIG. 9a a double shutoff valve;

(15) FIG. 10 an embodiment with an annular piston;

(16) FIG. 10a a double seal on the double stroke piston configured as an annular piston;

(17) FIG. 10b a structural separation of annular piston and DK piston;

(18) FIG. 11 the arrangement according to FIG. 1 with double stroke piston (DHK) and SK piston in parallel or twin arrangement;

(19) FIG. 12 the piston cylinder unit (THZ) with auxiliary piston and the actuator with double stroke piston (DHK) as parallel system;

(20) FIG. 13 another embodiment of the double stroke piston (DHK);

(21) FIG. 13a an expansion of the embodiment depicted in FIG. 13 with a differential piston;

(22) FIG. 14 a further embodiment with parallel piston capable of return stroke;

(23) FIG. 15 an entire system with structuring of the functional blocks;

(24) FIG. 15a an adaptive travel simulator (WS);

(25) FIG. 16 Valve connections; and

(26) FIG. 17 an auxiliary piston in block B.

(27) The brake system depicted in FIG. 1 is based, for example on the brake system depicted and described in DE 10 2013 105377 from the applicant to which reference is hereby made also for purposes of disclosure.

(28) The brake system substantially consists of an actuation device, in particular a brake pedal 1, a pedal interface 14 with an auxiliary piston 16 and redundant pedal stroke sensors 2, a drive with a motor 8 and transmission, in particular a ball screw transmission 7 with a spindle 5, a piston cylinder unit actuatable by means of the drive, in particular the spindle 5, a tandem main cylinder (THZ) 13 with a directly driven double stroke piston (DHK) 10, which rests on the spindle 5 and a directly, i.e. hydraulically driven piston (SK) 12. The double stroke piston 10 is configured in a stepped manner and forms an annular space 10a by means of the stepping. Between the drive, in particular the spindle 5 and the double stroke piston 10, a coupling 9 is arranged, which acts mechanically in this case and is mechanically actuatable. An example of a coupling of this type is described in EP 2217478A2 from the applicant to which reference is hereby made and is thus only schematically depicted in FIG. 1. A reservoir 11 is connected to the piston cylinder unit 13 via hydraulic lines and with the pressure chambers 10b, 12b of the piston cylinder unit 13 and via a normally open solenoid valve AS with the annular space 10a. The annular space 10a is also connected to the brake circuits A, B via hydraulic lines, in which the normally closed solenoid valves EA are connected. Furthermore, a travel simulator device WS and further valve device described in detail below as well as an electronic control or regulating device (ECU) (not depicted) are provided.

(29) The brake pedal 1 acts on the auxiliary piston 16 arranged in the pedal interface 14. Said auxiliary piston acts on the pedal plunger 3 and the latter acts on the piston plunger 4. The pedal plunger 3 and the piston plunger 4 can be separated or connected to each other. An idle stroke or free travel LW is provided between the pedal plunger 3 and the double stroke piston 10. In the case of the example depicted in FIG. 1, the free travel LW is provided between the end of the piston plunger 4 and the coupling 9. In the case of the embodiment according to FIG. 6, the free travel LW is provided between the separately configured pedal plunger and the piston plunger. If long free travel corresponding to DE 10 2013 105377 from the applicant is not provided, in the case of the alternative with short free travel the free travel between piston plunger 4 and coupling is approximately zero, the coupling is thus moved with each braking. This has the advantage that a jam can be diagnosed.

(30) The piston plunger 4 acts via the coupling 9 on the double stroke piston (DHK) 10, which is configured in particular in a stepped manner and forms an annular space 10a. This annular space 10a is connected to the reservoir 11 and the brake circuits A, B via hydraulic lines.

(31) The motor 8 is normally controlled via the pedal stroke sensors 2 and acts via the rotor, ball screw drive (KGT) 7 and the spindle 5 by way of a short play on the piston (DHK) 10. This generates pressure in the brake circuit A, which acts via the (SK) piston 12 in the brake circuit B in a manner known per se. Preferably, the pistons are arranged in a tandem main cylinder (THZ) 13. Twin arrangements are also possible in the context of the invention.

(32) Below, the pressure build-up P.sub.auf and pressure reduction P.sub.ab are firstly described for the normal brake function, then for the ABS function. The function of the travel simulator device WS is described in DE 10 2013 105377 from the applicant to which reference is hereby made.

(33) In the case of the function of the pressure build-up P.sub.auf, the double stroke piston (DHK) 10 and (SK) piston 12 come into the region of the stroke end, which is detected in the DHK by the motor sensor 6 via the rotor revolution and spindle pitch (stroke). The movement (position) of the piston SK 12 can be assessed from the spindle stroke and the pressure determined by a pressure sensor DG provided in the brake circuit A using the known assessment of the pressure-volume characteristic curve. If the stroke end is now reached, the motor 8 and the spindle 5 are switched from prestroke to return stroke. In this connection, the normally open valve AS arranged in hydraulic line to the reservoir 11 is closed and one or both of the normally closed valves EA arranged in hydraulic lines to the brake circuits A, B is open. The spindle 5 now moves the double stroke piston 10 back via the closed coupling 9 and the volume from the annular piston space 10a now reaches into the brake circuits A and B via the EA. This can take place simultaneously or serially. If the end of the return stroke is now reached, then the prestroke takes place again with the closing of the valves EA and opening of the valve AS.

(34) The return stroke depends, in this regard, on the position of the pedal 1 or the pedal plunger. In the case of full control of the travel simulator WS, the return stroke can be approximately 60% of the prestroke, which, however, delivers sufficient volume. In the case of a normal vehicle, the return stroke is required only in the fading region, in the case of small commercial vehicles it can even take place with 50% braking.

(35) Borderline cases are conceivable, in which the additional volume delivery via the return stroke starts earlier, e.g. in the case of a small leakage or vapour bubble formation. It is advantageous in this method for the volume delivery to be able to take place in a highly dynamic manner and without notable time delay theoretically only limited by the supply in the reservoir 11. This in the case of relatively small piston dimensions and corresponding spindle forces.

(36) Valve Connections:

(37) The ABS regulation can take place in the preferred and often described manner by valves SV in the multiplex (MUX) method, wherein only one valve SV is in each case provided per wheel brake RZ (not depicted), as this is depicted in FIG. 1 for the brake circuit A. By way of the possibility of continuous volume delivery, the conventional method of pressure control can also take place via inlet valves E and outlet valves A (one valve E and A each per wheel brake RZ), as this is depicted in FIG. 1 with regard to the brake circuit B. The volume required for the pressure reduction P.sub.ab which is conveyed via the return flow line R into the reservoir, can be supplemented by the volume delivery of the piston (DHK) 10.

(38) The E or A valves still have additional functions. In the case of regulation due to low , the piston (DHK) 10 must be moved very far back, which would lead to a collision with the pedal/piston plunger. In order to avoid this, an opening of the EA valve and pressure reduction from the brake circuit can expediently take place, as this is described in DE 10 2010 045617 from the applicant (so-called HLF). The volume from the brake circuit A or additionally B can be conveyed for the pressure reduction into the reservoir 11 via the piston 10 or the associated pressure chamber and the valve AS.

(39) Alternatively, a free travel LW can be provided between pedal and piston plunger, as is described in detail e.g. in DE 10 2013 105377 from the applicant. A further borderline case is conceivable by locked motor or spindle. The vehicle remains braked in this case. In this connection, the pressure can be released via the E/A valves.

(40) In the fallback level (RFE), the coupling between the spindle 5 and the piston 10 is expediently separated, i.e. the coupling is open, since otherwise the RFE effect is reduced by the additional force to overcome residual torque and spindle return spring, which accounts for approximately 15% such that the 0.64 g cannot be reached. The piston plunger thus separates the coupling 9 in the RFE and acts directly on the piston 10 DHK. If, e.g. for reasons of cost the coupling is left out, a corresponding reduction of the efficiency results. It is also conceivable to make the piston of the piston cylinder unit (THZ) 13 smaller in diameter since the quick supply allows this and sufficient pressure medium volume is provided in the fallback level via injecting.

(41) In order to improve the pedal travel in the fallback level, as described in DE 10 2013 105377 from the applicant, volume from the pressure chamber of the auxiliary piston 16 can be conveyed via the valve ESV into the brake circuits. This can take place in this case e.g. via the valve ESV into the brake circuit A. Alternatively, pressure medium can be conveyed via the valve ESV on the rear side of the piston 10 (corresponding to the line marked in a dashed manner in FIG. 6). This has the advantage that a brake circuit failure does not occur in the case of a leakage of the valve ESV. In addition, depending on the position of the pistons 10, 12, pressure medium volume can also be injected via the valves EA into the brake circuits. This injecting is particularly advantageous for a solution with idle stroke, as is described in DE 10 2013 105377 from the applicant. The impinging of the pedal plunger on the double stroke piston 10 can be detected via the pedal travel sensor 2.

(42) FIG. 2 shows an additional, normally closed safety valve SiV in the line from the annular space 10a of the DHK piston 10 to the valves EA. Unsealed EA valves result in a brake circuit failure since the leakage volume reaches into the reservoir 11 via the DHK piston 10. This impedes the redundant SiV in the line to the reservoir 11 via the valve AS.

(43) The valve AS can also be configured redundantly by parallel connection of a second valve. It is thus ensured that a pressure build-up is possible even in the case of a valve failing.

(44) FIG. 3 shows a simplified valve connection for the control of the DHK piston 10. Instead of the valves EA and AS, a 3/2 way solenoid valve MV can be used for each brake circuit A, B, which saves the valve AS because the annular space 10a of the valve 10 is connected via the 3/2 solenoid valve to the reservoir in the outlet position. In the connected state, this connection is closed and the annular space 10a is connected to the brake circuit A or B via the 3/2 solenoid valve. This is only depicted for a brake circuit A in the figure since an alternative embodiment is shown for the others. One 3/2 solenoid valve would then also be used for the brake circuit B. An SiV (not shown) can also still be used here in addition in the line. For brake circuit B, the opening of the brake circuit B can be avoided by a plunger 17 together with the EA valve.

(45) FIG. 4 shows the stepped DHK piston 10 with the annular space 10a and the different effective areas A1-A3 thereof in an enlarged manner. The volume for the prestroke is determined from volume V.sub.V=A.sub.1piston stroke, the following applies for return stroke V.sub.R=(A.sub.2A.sub.3A.sub.1)piston stroke. Preferably, V.sub.R is selected so as to be smaller, a smaller piston force=motor torque is thus required for the higher pressure range if only one return stroke is required.

(46) In the case of two prestrokes, the same effect can optionally be achieved by one idle stroke for the prestroke by the prestroke delivering into the reservoir 11 in the case of a closed valve SV.

(47) FIG. 5 shows the temporal volume delivery in three stages via the two-fold prestroke VH and one return stroke RH. The switch time from prestroke VH to return stroke RH requires one only very small time delay of <10 ms.

(48) FIG. 5a shows only one stage, which is used in the case of over 90% of braking operations. This phase can also be used for diagnosing the leak-tightness of the valves EA and AS. A leak from EA can be determined by two methods. Firstly by comparing pressure and piston travel and assessing the pressure-volume characteristic curve. In the case of a leak, the known association of pressure and volume (or piston travel) would be disrupted. Secondly, the pressure can be maintained by corresponding piston position in the case of pressure reduction P.sub.ab for x and assessed via t.sub.D. In the case of both tests, all leakages are detected in the brake circuits. When the SiV according to FIG. 2 is used, the valves EA can be tested separately by closing SiV.

(49) FIG. 5b shows the volume delivery in two stages. When the brake pedal from stage 2 is withdrawn, the corresponding pressure is reduced by opening the valve EA, controlled via the pressure sensor DG. The DHK piston 10 or SK piston 12 is thus prevented from moving with too much pressure over the breather bore in the main cylinder. The pressure is only reduced so much such that in stage 1 the normal association of pressure to piston travel occurs, such that optionally only low pressure is used to move over the collar.

(50) With the double stroke piston and the control possibilities described, a quick and continuous volume change is possible with relatively little effort which increases the application and acceptance of the system and is at the same time fail-safe.

(51) In FIG. 6, a different embodiment of the brake system according to the invention is depicted with a magnetic coupling 9a and a free travel LW between pedal plunger 3 and piston plunger 4, which corresponds to the control path of the travel simulator. In the case of this embodiment, the volume supply takes place with a modified valve connection.

(52) In this connection, in the case of the return stroke delivery is not carried out into the brake circuit via fully or partially opened valves SV or valves E, but rather into the pressure chambers 10b, 12b of the piston cylinder unit (THZ) 13. In this regard, all valves SV and E are closed. It is advantageous here to use a simple magnetic coupling, as is described in DE 10 2010 044754 from the applicant to which reference is hereby made also for the purposes of disclosure. This is possible with this embodiment because a comparatively low piston force is sufficient to deliver the fluid volume from the annular space 10a of the double stroke piston 10 via the valves EA into the working chambers of the main cylinder which are associated with the brake circuits A, B. In this connection, the delivery volume of the return delivery must match the uptake volume of the main cylinder circuits by corresponding dimensioning. The valve switch position in the case of the return stroke end is depicted in FIG. 6, i.e. valve EA open and valve SV or valve E to the wheel brake cylinder are closed. Furthermore, lower bearing forces in the drive result in the case of the return stroke. However, this embodiment can lead to a small time delay in the case of pressure build-up compared with the suction via negative pressure. Otherwise the valve connection according to FIG. 2 and the 3/2 way valve according to FIG. 3 can be used for this embodiment.

(53) FIG. 6a shows an embodiment similar to FIG. 6 wherein in the upper half of the figure, the spindle of the drive is connected to the piston by means of a connection element, in particular a bending rod and in the lower half by means of an, in particular mechanical coupling. Unlike FIG. 6, the volume of the auxiliary piston 16 here is, however, not directed to the rear side of the double stroke piston 10, but rather is directed in the fallback level RFE in the case of the vehicle electrical system or the ECU failing via a normally open valve ESV, with a normally closed valve WA, into the brake circuit. Since the breather bore at 40 of the compression rod piston (DK) circuit is open in the outlet position of the double stroke piston DHK 10, a shutoff valve AV to the reservoir 11 is used, which is closed at the beginning of braking. Thus no volume can flow into the reservoir 11 in the fallback level. The shutoff valve AV can be economised if the motor is driven back against the stop spring prior to the beginning of braking in order to open the breather bore. The situation in which the breather bore is closed persists even in the case of greater pressures or pedal travels such that in the case of the pedal plunger 3 impinging on the piston plunger 4, both surfaces of the auxiliary piston 16 and of the DK piston 10 deliver volume. In this case a higher pedal force results, which is comparable with conventional systems. However, if the ECU is intact, then the injection is controlled, as described via ESV and WA, until a certain pressure is reached. The volume uptake of the travel simulator WS is disrupted somewhat in the fallback level by the initially flatter course of the pedal force via the pedal travel. This can be eliminated by an additional normally closed shutoff valve WSA.

(54) This solution provides an additional possibility for structural length reduction by the stroke of the double stroke piston DHK 10 being equal to the difference of pedal stroke and free travel, e.g. 36 mm16 mm=20 mm, corresponding to the control travel of the travel simulator WS, which means a structural length reduction of 48 mm. This is possible since pressure is continuously built up via the double stroke piston DHK 10. The spindle length is thus also reduced and the expensive bore in the spindle 5 can be dispensed with. In this connection, the spindle can be connected to the double stroke piston DHK 10 via a bending rod (as depicted in FIG. 12). However, in this case the spindle with motor has to be moved in the fallback level RFE, which requires approximately 5% more power if the pedal plunger impinges the rear side of the spindle. Alternatively, the mechanical coupling 9 from FIG. 1 can also be used. The above-mentioned additional force is thus not required in the fallback level RFE with ECU function in the case of the motor failing. A further possibility of the structural length reduction is a greater diameter and shorter stroke of the floating piston (SK). This applies for all solutions.

(55) FIG. 7 shows an embodiment with a means for preventing the escape of leakage fluid to the outside. Seals in hydraulic systems tend to leak under unfavourable conditions. Double seals are often used which reduce the probability of leakages, but do not exclude them. However, seals of this type produce disadvantageous higher friction. Seals which affect the footwell and also power units or the motor compartment are affected. As a solution, a corresponding housing, advantageously an extended motor or motor connection housing 21, 22 is used which comprises both outlet channels 25 and an uptake volume for the leakage flow. A separation chamber 23 with a sponge 24 is expediently provided in the lower region of 22 in order to prevent sloshing of the fluid in particular in the case of the vehicle accelerating and decelerating.

(56) The corresponding leakage flow is detected by a level sensor 18. In this connection, it is also advantageous to combine the level sensor with the adjacent ECU. In this regard, sensors with high fail-safety can also be used. Alternatively, electrodes 20 can also be used which are arranged in the lower region of the collecting vessel and are connected to the ECU by means of an electrical line. With said electrodes, even very small fluid leakage quantities can be detected. For complete integration, the HCU, which comprises the solenoid valves and the pressure sensors, is integrated. This means that a so-called 1-box solution is achieved, which comprises a full integration of all components in one unit.

(57) The embodiments according to FIGS. 8 and 9 build on those of FIG. 4 such that only the changes are described in the following description. Large flow rates occur by way of the relatively large effective areas of the double stroke piston DHK 10 with quick piston actuation, in the case of which negative pressure cannot occur on the suction side of the piston. For this reason, suction valves S1 and S2 are arranged for both movement directions (prestroke and return stroke). For the case that the delivery quantities for prestroke are >return stroke, the surplus volume can be channelled off via a screen. The prestroke speed is greater in the borderline case than the return stroke speed. The volume in the prestroke is thus directed via the suction valve S1 to the rear side of the double stroke piston 10; the open solenoid valve AS acts as a suction valve. In the case of the return stroke, the lower flow rate quantity is directed through the solenoid valve AS and S2 acts as a suction valve. In the case of the volume delivery in the brake circuit, e.g. DK, the solenoid valve AS is closed and the solenoid valve EA is open, as already described.

(58) FIG. 9 shows a slightly changed arrangement of the solenoid valve AS and the suction valve. The volume is directed in this case through the solenoid valve AS in the prestroke. This version shows the expansion of the DK for prefilling the brake circuit in order to reduce the free travel on the pedal. In the prestroke, a pressure relief valve U operates, e.g. 4 bar such that corresponding volume reaches into the DK circuit via the primary collar or DK collar 10 and more volume is thus provided. Since this admission pressure is used only at the beginning of braking, the pressure relief valve U is opened via a plunger 33 after prefilling (VF). Different control possibilities are conceivable in this case, e.g. that the prefilling (VF) operates again for the fallback level in the case of the E-motor failing at low , i.e. pressure 0 in the DK circuit, which does not change anything on the principle of the volume supply by the DHK.

(59) FIG. 9a shows a double valve arrangement with two shutoff valves AS1 and AS2 which are installed instead of the valve AS provided in FIG. 9. The shutoff valves AS1 and AS2 are connected such that the current direction and current force act against the spring F.sub.AS. The current force is thus prevented from being greater than the spring force and the valve closing.

(60) FIG. 10 shows the basic structure of an actuation device with auxiliary piston 16, spindle 5 and coupling 9, in which the DK piston and the double stroke piston configured as an annular piston 28 are combined. The delivery chamber of the double stroke piston 28 is in this connection formed by an annular space 40 arranged concentrically to the pressure chamber of the DK piston, in which the annular piston 28 with seal collar 28a is arranged. The DK piston also draws in air via the delivery chamber of the double stroke piston as depicted for 41. The valve arrangement corresponds to that of FIG. 9. The different possibilities of the pressure modulation via inlet valves EV and outlet valves AV or multiplex operation (MUX) via solenoid valves SV are also depicted here. In the first case, the solenoid valve EA can be replaced with a simpler check valve RS since the pressure reduction, e.g. for the hydraulic free travel clearance can take place via corresponding outlet valves AV.

(61) FIG. 10a shows the sealing of the annular piston 28 by the collar 28a which slides in the annular bore or annular space 40, the inner diameter of which is secured via the seal 34. A further seal 35 is required for the rear side of the annular piston which acts as the primary seal as in the case of the main cylinder. As in the main cylinder, an additional secondary seal 35a can also be used here, wherein the sealed chamber is connected to the reservoir 3. This arrangement can also be used in FIG. 1.

(62) FIG. 10b shows a divided embodiment of annular piston 28 and DK piston 31 which are connected via a securing ring 32 in a non-positive manner. This embodiment is less tolerance-sensitive.

(63) FIG. 11 shows an arrangement also with structural length reduction by the piston cylinder unit being configured in a twin arrangement by using the SK piston 12 as the twin. The valve connection of the valves AS, S2 and S3 and the screen 26b is taken from FIG. 9. For the case of a double fault of the motor and thus failure of the double stroke piston DHK and brake circuit failure DK, pressure is no longer applied to the SK piston. In the case of an intact motor, the SK piston would be operated via the double stroke piston DHK in the return stroke if the brake circuit failed and the inlet valves EV in the DK circuit would be closed. In the case of a double fault, the SK piston 12 is fed by the auxiliary piston 16 via the ESV and closed isolation valve TV1.

(64) FIG. 12 shows a parallel arrangement of tandem main cylinder THZ with the pistons 12 and 12a and pressure modulation device consisting of motor 8, transmission and double stroke piston DHK 10. In this connection, the connection to the brake pedal with the pedal plunger is omitted in comparison to FIG. 1. The valve arrangement for pressure modulation and travel simulator WS is the same as in the preceding figures. Since the connection to the pedal plunger is no longer present here, a bending rod 30 is used instead of the bending tube and coupling, so that the spindle eccentricity does not cause large transverse forces on the double stroke piston 10. The unit located parallel consisting of tandem main cylinder THZ with piston SK 12, piston DK 12 and auxiliary piston 16 was already described in DE 10 2010 050133 from the applicant (to which reference is hereby made in this regard) which requires the travel simulator circuit with auxiliary piston, which is independent of the DK circuit, which has significant advantages in terms of fail-safety. In addition, the travel simulator WS can only be configured in a two-stage manner, which saves costs and volume. In the first flat area, the return spring acts as the 1st stage of the travel simulator WS, the WA valve is open in this regard.

(65) The travel simulator WS acts only in the second stage with progressive increase in force after the closing of the valve WA. In comparison to DE 10 2010 050133 from the applicant, an improvement for the fallback level is integrated here by using a changeover valve UV. This connects the auxiliary piston 16 to the rear side of the DK piston 12a in a currentless manner. Thus in the case of the ECU or the motor failing, the free travel LW required for e.g. recuperation does not lead to pedal failure, the volume of the auxiliary piston 16 is directed in this case to the rear side of the DK piston 12a. In the case of an intact ECU, the volume of the auxiliary piston 16 can also be injected into the brake circuit via ECU e.g. in the case of the motor failing.

(66) The diagnosis of the travel simulator with auxiliary piston and main cylinder (THZ) can take place by pressure generation in the brake circuits. In the case of the valve ESV opening, pressure medium can reach in the auxiliary piston circuit when the valve EA is closed. In the case of the normally open valve UV opening, pressure medium reaches in the elastic pressure medium chamber of the auxiliary piston 16 which can be measured at the piston stroke of the double stroke piston. By using the normally open 2/2 solenoid valve (not depicted) in the line of the auxiliary piston to the DK piston 12 and a normally closed 2/2 solenoid valve in the line of the auxiliary piston to the valve ESV, the diagnosis can be expanded by also applying pressure medium to the DK piston and it correspondingly moving.

(67) The piston cylinder unit (THZ) is separated from the pressure supply via isolation valves TV2, TV3 in the case of an intact motor and ECU, similar to the EHB or parallel systems as shown in DE 102010 040097. The advantage of the arrangement shown is the higher fail-safety and continuous volume delivery. The piston cylinder unit (THZ) from DE 102010 040097 or DE 102011 081601 can also be combined with the pressure supply dispensing with the fail-safety in the case of the travel simulator. Unlike DE 102010 040097, there is no pressure sensor used here since the most important parameters for diagnosis and function can be detected by motor current and piston travel.

(68) In order to reduce the structural length, the (twin) solution according to FIG. 11 can also be used here.

(69) FIG. 13 shows, proceeding from the depiction according to FIG. 6a, another embodiment of the double stroke piston 10. The double stroke piston 10 is neither stepped nor configured as an annular piston, but rather it corresponds in structure and sealing with primary and secondary collar to a conventional compression rod piston (DK). In this case, it is coupled to the spindle 5 via the piston plunger 4. A free travel LW is integrated therein, as in the case of the embodiment according to FIG. 6a. The rear side of the double stroke piston 10 is connected via a shutoff valve AS to the reservoir (VB) 11. If further volume is now required, the return stroke of the double stroke piston 10 then takes place in the case of the closed valve AS and at the same time the isolation valves TV2 and TV3 to the piston cylinder unit (tandem main cylinder THZ) are closed. In the case of the return stroke, volume is delivered via the check valve RS and the valve EA or alternatively via two valves EA into the brake circuits. At the same time, volume from the reservoir 11 is suctioned via suction valves S1 and S2 installed in the hydraulic lines leading to the reservoir 11 by the SK pistons 12 or 12b and the double stroke piston 10, said reservoir being available for further pressure build-up in the case of the next prestroke. An advantage of this construction consists of the shorter structural length and a simpler double stroke piston 10, which is, however, connected to more valves.

(70) The solution according to FIG. 13a builds on an arrangement as is described e.g. in the PCT/EP 2007/009683 from the applicant and is expanded with a double stroke piston. The inner piston 10 here corresponds to the DK piston with breather bore 40 and the outer differential piston 38 corresponds to the double stroke piston. The DK piston is, as usual, sealed by means of primary collar and secondary collar 27 and the differential piston via the seals 39, 35 and 34a. The valve connection of the double stroke piston with valve AS, valve RS etc. corresponds to that depicted in FIG. 13, supplemented by a suction valve (S2). This is required in order to suction the volume in the case of the closed valve AS back into the piston after the return stroke with volume delivery in the case of the subsequent prestroke. The arrangement has connection lines to the reservoir VB. The differential piston is connected to the ball screw transmission 7 via the spindle 7 and the DK piston is connected to the pedal plunger via the piston plunger 4. Since the spindle 5 acts on the differential piston for pressure modulation and the DK piston acts only in the fallback level, a coupling is no longer required. This solution can be combined with integrated free travel or with hydraulic free travel clearance via at least one inlet/outlet valve EA.

(71) A further advantageous embodiment is depicted in FIG. 14. In this embodiment, in particular two parallel pistons are arranged parallel to the piston cylinder unit (THZ), which are fixedly connected to the spindle. The return stroke of the spindle thus acts directly on these pistons for volume delivery. In this connection, a valve arrangement according to FIG. 9 or also FIG. 13 can be used. With this embodiment, which can also be operated in the multiplex method, the volume currents can be reduced, amongst other things, in the case of short structural length.

(72) Reference is then made to FIGS. 15 to 17. The entire structure of the embodiment depicted in FIG. 15 largely corresponds to the embodiment depicted in the preceding figures and is structured in functional blocks for better understanding. A Motor with spindle drive B Piston cylinder unit, in particular double stroke piston (DHK) and main cylinder piston C Auxiliary piston with travel simulator (WS) D Valve connection D1 for pressure regulation D2 for control of double stroke piston (DHK), prefilling (VF) and pressure supply of main cylinder (HZ) in the case of return stroke D3 Control of travel simulator (WS) with injection (ES)

(73) A drive with a motor 8 with a ball screw drive (KGT) 7 and spindle 5 is arranged in block A which acts on a coupling 9 and a piston cylinder device, in particular with a double stroke piston (DHK) 10. The coupling 9 is opened in the outlet position by a main cylinder return spring 123 acting via a coupling return spring 122 on a piston plunger 4 displaceably mounted in the spindle, said piston plunger being connected to a coupling plunger (KS). The piston plunger 4 then rests on a stop 121. If the motor 8 and the spindle 5, which acts on the double stroke piston 10, move, then the coupling 9 closes after a short coupling path and the spindle 5 is then coupled in both directions with the double stroke piston 10, which is required for the return stroke so that, as described, the double stroke piston (which can be configured as an annular piston) delivers volume into the brake circuits of compression rod piston (DK) 12a and floating piston (SK) 12 via EA valves. This coupling path has the advantage that the plunger is moved in the case of each braking. In the case of a jam, the piston does not return into the outlet position and can be diagnosed via residual pressure in the working chamber of the compression rod piston 12a and a motor sensor 6.

(74) If the motor drive fails, a pedal plunger 3 acts on the piston plunger 4 after the free travel (LW) and thus on the compression rod piston 12a, which is integrated in the double stroke piston 10. In this case, volume is injected during the free travel from an auxiliary piston 116 via a normally open solenoid valve ESV and a solenoid valve AS and an open breather bore 120 directly into the compression rod brake circuit. The free travel is thus not received as loss of travel in the volume balance of the compression rod piston 10. This is possible by dynamic pressure occurring by way of the floating piston 12 and a choke D (screen) to a travel simulator WS, which enables an injection of pressure medium. In order for further optimisation, a normally closed shutoff valve 124 can be used together with a pressure relief valve D.

(75) In a special case, if the drive (motor/transmission) is locked and thus also the two pistons (DK and SK) 12a, 12, pressure can also be built up or reduced from an auxiliary piston 116 via the valves EA.

(76) After bridging the free travel, the pedal plunger 3 impinges on the piston plunger 4 and in the subsequent movement overcomes the force jump which results through the main cylinder return spring 23 and the pressure generated by the compression rod piston 12a. The speed-dependent dynamic pressure acts on the auxiliary piston 16 in this connection as a hydrodynamic force on the choke D. In the case of the force jump, the speed briefly becomes low, such that the pressure on the compression rod piston 12a does not fully add up to the dynamic pressure prior to impinging=dynamic pressure.

(77) A small additional force jump thus occurs. The jump force can be defined by an elastic stop 21 with a transition function. This force jump is based on the pedal force prescribed by the legislator of 500 N for minimum braking in the fallback level in the range <10%, thus controllable by the driver. This jump force applies for the fallback level (RFE 3, i.e. failure of motor and vehicle electrical system). In the case of motor failure and intact ECU (=RFE 2), the auxiliary piston pressure in this range can be controlled by pulse width modulation (PWM) of the solenoid valve (ESV) and the solenoid valve (WA).

(78) If, depending on the valve connection, even in the case of longer travel of the auxiliary piston 16, dynamic pressure has an effect which requires a higher pedal force which reduces the maximum pressure at e.g. 500 N pedal force, then a bypass can be used here in the auxiliary piston bore. This causes an outflow of fluid in the return flow with the corresponding piston position. Without this feature, a return flow from the auxiliary piston to the reservoir (VB) 11 is not required.

(79) Unlike the embodiments described in the patent applications DE 10 2010 045 617.9 A1 and DE 10 2013 111 974.3 from the applicant, the valve ESV is, in addition to the valve WA, normally open, which enables the injection in the fallback level without significant disadvantages. Thus the variant with free travel and reduced main cylinder stroke is possible, which leads to notable structural length reduction and cost reduction. The lower delivery volume of the main cylinder with reduced stroke is balanced out by prefilling, as will be explained below in more detail.

(80) The function of the travel simulator (WS) with the valves ESV, WA, RV0, RV1, D are described further in the patent applications DE 10 2010 045 617.9 A1 and DE 10 2013 111 974.3 from the applicant to which reference is hereby made in this respect.

(81) The piston cylinder device with the main cylinder piston 12 and 12a and the double stroke piston 10 are contained in block B and the valve functions for ABS/ESP and pressure supply with control of the double stroke piston 10 are parallel.

(82) The injection via the breather bore 120 was already described further above which substantially only applies for the fallback level (RFE). In the case of an intact motor, pedal travel sensors 2a and 2b deliver a signal to the motor control for the pressure build-up even after short pedal plunger travel. In this regard, the prefilling immediately comes into operation by closing the AS valve. In this connection, the full double stroke piston delivers a large volume from the area of the annular space 10a and the compression rod piston 12a even in the case of short travel which is used for prefilling. In this connection, an additional effect occurs by the prefilling volume flowing through the collar of the compression rod piston 12a and preventing it from being worn out by the breather bore. The prefilling should be e.g. speed-dependent, in the case of stage 1 small V a low pressure<10 bar and stage 2 high V<40 bar. In this connection, the measured pressure of the pressure sensor D6 or the current or the piston position can be used as the control signal. In the case of the special design of the double stroke piston with two pistons in particular with an annular piston, both the prefilling and the additional volume delivery can be carried out in the return stroke via only one valve (AS). In the case of other designs of the double stroke piston, two or a plurality of valves can or must be used for the prefilling.

(83) The prefilling has two important advantages: a. In the case of short brake padplay, i.e. additional volume requirement, the pressure build-up so-called time to lock is faster which means brake travel reduction. b. In the case of play LS, e.g. with rollback, the additional volume is not notably included in time to lock. In this connection, the brake pad play control described in the patent application DE 10 2008 051316.4 from the applicant to which reference is made here in this respect lends itself to the play control by controlling the negative pressure in the brake piston. In this connection, the play can be variably designed e.g. vehicle speed-dependent or dependent on the RFE. This play is a significant contribution to CO.sub.2 reduction in the range of 1-2 g. c. In the case of a large volume requirement in the main cylinder for full braking and great pedal speed, 50% greater volume is generated in the case of <40 with the same HZ stroke. The advantageous variant with free travel (LW) and shorter main cylinder travel is thus justified. d. In the fallback level RFE1 (with failure of the travel simulator), a switch is carried out to a so-called slave booster because the pedal plunger here acts on the HZ piston (DK) in the case of the conventional brake force booster (BKV).

(84) Since however in order to achieve greater pressures at 500 N of pedal force, as is well known, a small main cylinder diameter is used, the pedal travel without travel simulator WS is correspondingly significantly longer. This can be reduced by approximately 30% with prefilling. The greater prefilling volume can influence the piston position such that the SK piston 12 is possibly at the stop at an early stage. This can be prevented by the SK piston 12 being given a larger diameter. Otherwise, the stop is detected by pressure=f (piston travel), measured by the motor sensor. In the case of the stop, the return stroke volume (i.e. the volume that is delivered in the case of the return stroke) is injected into the brake circuit of the floating piston. The association of the pistons can also be detected via a floating circuit piston travel sensor 15 with target 15a in the piston.

(85) In particular in the case of systems with recuperation, a pedal free travel between pedal plunger and the piston of the piston cylinder device, in particular double stroke piston 10 is advantageous, since due to the brake torque of the generator pressure does not have to be built up by the piston cylinder device. The brake torque is predetermined by a pedal travel sensor together with the travel simulator and divided into generator brake torque and brake torque corresponding to the pressure. If e.g. a small brake torque is predetermined by the driver, the generator brake torque is then sufficient. This applies up to a brake torque of approximately 30 bar which can be applied by the generator. The pedal travel range of approximately 5-8 mm corresponds to the free travel. The travel of the piston 10 of the piston cylinder device becomes shorter by this free travel since the pedal stroke is predetermined and a short stroke of the piston 10 results after the free stroke. In the fallback level, this stroke is omitted in the case of the entire volume delivery of the piston 10. According to the invention, volume from the auxiliary piston 116 is thus injected via the piston 10 and the open breather bore of the compression rod piston into the compression rod piston brake circuit.

(86) The prefilling with greater volume must, however, be taken into consideration in the case of the pressure reduction since based on the pedal travel range, in particular in stage 1 of the travel simulator WS, the travel simulator piston still does not operate (see Description FIG. 1a). A pressure reduction P.sub.ab takes place here depending on the pedal travel reduction in the reservoir 11 via the outlet valves, as in the case of ABS. In order to control the double stroke piston 10, the valve AS and suction valves S2 and optionally S3 to the reservoir are required. S2 operates in the case of closed valve AS in the case of the return stroke and volume delivery via EA into the brake circuit. S3 is optionally required since in the case of prefilling, the valve AS is closed and what occurs here in the case of negative pressure cannot be balanced out as quickly after prefilling in the case of a re-opened valve AS.

(87) In the case of the return stroke, a smaller spindle force and also motor torque operate in the case of corresponding dimensioning of the double stroke piston 10, which is advantageous in the case of high pressures. This phase can also be correspondingly designed by being used as a virtually free run in the case of applied prestroke for the high pressure range such that volume does not reach the pressure build-up P.sub.auf, but rather reaches the reservoir 11 in the return flow. Volume for the high pressure range is then delivered only in the case of the subsequent return stroke.

(88) The return stroke in the case of advantageous system variants with multiplex arrangement or operation (MUX in which the pressure build-up and the pressure reduction takes place in each case via only one valve in the brake lines) can take place during simultaneous pressure build-up P.sub.auf and pressure reduction P.sub.ab in separated brake circuits. To this end, an additional shutoff valve 17 is required.

(89) The valves for ABS/ESR pressure control are located in block D1, which were described e.g. in the patent application DE 10 2013 111974.3 from the applicant to which reference is made here in this respect. In the case of conventional pressure control with inlet valves (EV) and outlet valves (AV), the pressure reduction P.sub.ab takes place through the outlet valves (AV) in the return flow to the reservoir 11.

(90) The valve function of the valves AS and EA was already described in block D2. In the patent application DE 10 2013 111974.3 from the applicant, only one check valve is used instead of the valve EA. This is disadvantageous e.g. in the case of brake circuit failure, e.g. of the floating piston brake circuit, where supply by return stroke is not possible, since the return stroke volume is possibly delivered in the pressureless floating piston circuit. Since this is detected by diagnosis p=f (piston travel), no delivery takes place into the failed circuit in this case with the EA valve.

(91) In the embodiment with MUX, the valves for pressure regulation have no return flow. For the case described of larger prefilling volume and pressure reduction P.sub.ab to balance out with shorter pedal travels, a valve AV.sub.x for pressure reduction P.sub.ab must be used here.

(92) Block C contains the pedal interface with auxiliary piston 116, pedal travel sensors 2a and 2b and travel simulator WS. The functions are already described in previous applications from the applicant and also apply to the system design with double stroke pistons. The valve functions of block D3 were described in connection with injection ES. The diagnosis of the breather bore 120 in the compression rod piston 12a should also be mentioned which is not always possible with conventional brake systems. This case occurs by way of tolerance shifts or disruptions during operation. If the breather bore remains closed, pressure balance in the brake circuit is not possible. This results in a negative pressure in the case of lower temperatures with possible play if the brake piston reacts to this or in the case of high temperature a residual pressure in the brake circuit leads to a residual brake effect with possible temperature increase in the brake.

(93) In the case of the proposed system with prefilling, a residual pressure in the compression rod piston brake circuit still remains in the range of the free travel LW which can be controlled via the valves AV and ESV. In this case, valve ESV is closed and valve EA is open; differential pressure does not thereby occur on the collar since the pressure in the brake circuit of the compression rod piston DK and double stroke piston brake circuit is equal. In the case of pedal travel=0 (i.e. outlet position), the valve EA is closed and the valve ESV is open. The following pressure change is an indication that the breather bore is open. This method can be used for each braking or at large intervals.

(94) FIG. 15a shows the adaptive behaviour of the travel simulator WS. The travel simulator WS has at least three stages in terms of its characteristics: Stage 1: Pedal return effect is generated via the pedal return spring 118. Valve WA open. This stage is dimensioned e.g. with 7-8 mm pedal plunger travel and towards the end results in a system pressure of approximately 30 bar. This pressure corresponds approximately to the braking with a high recuperation torque of the generator. The described free travel LW of the pedal plunger corresponds to approximately the previously mentioned travel which means that in the case of recuperation the actuator with motor drive is not enabled which requires approximately 80% fewer load cycles. Stages 2 and 3: Valve WA closed, volume of the auxiliary piston 16 reaches in the travel simulator piston with specific force-pressure characteristics with stop.

(95) In the case of known systems, the stop of the travel simulator is associated with a fixed pedal travel via a valve WA. According to an advantageous inventive aspect, a solution is now proposed, in which the travel simulator is adaptive e.g. in the case of fading which is detectable due to the function p=f (vehicle deceleration). The stop is normally reached in the case of N. In the case of fading which is detectable by high pressure in relation to the vehicle deceleration, the stop can be shifted to F by control of the valve WA. In the case of low , this is also detected and the stop can be provided in the case of shorter pedal travels. As is well known, the conventional ABS operates even in the case of shorter pedal travels E1. This can also be generated by the pressure reaching in the auxiliary piston via open valves EA and ESV through prestroke and pushes back or modulates the latter or via closed valve EA and open valve ESV with return stroke.

(96) FIG. 16 shows simplified valve connections without details of the regions A-C. In the region D2, only one 3/2 way EA valve with check valve is used for the pressure supply of the brake circuits. The volume is delivered in the floating circuit without connecting the valve EA in the case of the return stroke of the double stroke piston. In the case of connecting the EA valve, delivery takes place in the floating piston brake circuit SK and the brake circuit of the compression rod piston DK. In the case of failure in the floating piston brake circuit SK, delivery is only carried out in the floating piston brake circuit. The compression rod circuit also has the advantage with the double stroke piston that a failure of the collar is very quickly detected by the pressure and piston travel monitor. In this case, delivery is nonetheless carried out in the compression rod brake circuit with closed valve ESV. In this connection, the DK piston pressure is balance out with open valve AS.

(97) A further simplification is possible in the case of the travel simulator WS. The normally open valve ESU is replaced with a check valve RVS. This solution has the disadvantage of the travel simulator pressure being shifted in the double stroke piston and causing additional seal friction. In an extreme case, the WS pressure may become greater than the pressure in the compression rod piston brake circuit in the case of very high pedal forces. In this case, the ABS function must be switched off. This can be avoided if the piston movement of the travel simulator WS (see dashed line) is expanded for additional closure of the check valve. In the case of this simplification, pedal reaction cannot be generated in the case of the adaptive travel simulator.

(98) FIG. 17 shows a constructive variant by the auxiliary piston being shifted from the pedal interface in block B. In this connection, the pedal plunger 3 acts on the annular auxiliary piston 119 via a bridge, said auxiliary piston being mounted between double stroke piston 10 and the housing 125 thereof. The pedal stroke 3 also acts on the coupling 9. The pedal return spring 18 acts on the auxiliary piston 119 analogously to FIG. 15. The movement of the auxiliary piston 19 can alternatively be detected here at another point by the slave pedal travel sensor 2b. The advantage is the overview of all hydraulic functions in one block without long supply lines to the pedal interface corresponding to FIG. 15.

(99) For future vehicle platform modularity, the systems should be able to be used via numerous models for left-hand drive vehicles and also for right-hand drive vehicles. In this regard, the right-hand drive vehicle has problems in the case of the transverse mounting of the combustion motor. A 2-box solution lends itself in this situation by only the main cylinder with small dimensions, in particular tandem main cylinder with auxiliary piston (16) being mounted on the bulkhead of the vehicle and the drive (or motor/transmission) valve module flexibly in the motor compartment of the vehicle.

LIST OF REFERENCE NUMERALS

(100) 1 Brake pedal

(101) 2 Pedal travel sensors

(102) 3 Pedal plunger

(103) 4 Piston plunger

(104) 5 Spindle

(105) 6 Motor sensor

(106) 7 KGT

(107) 8 EC motor

(108) 9 Coupling

(109) 9a Magnetic coupling

(110) 9b Direct coupling of spindle with DHK

(111) 10 DK double stroke piston (DHK)

(112) 10a Annular space

(113) 10b Pressure chamber

(114) 11 Reservoir

(115) 12 SK piston

(116) 12a DK piston

(117) 12b SK piston enlarged

(118) 13 Piston cylinder unit

(119) 14 Pedal interface

(120) 15 SK positioning sensor

(121) 15a Target for positioning sensor

(122) 16 Auxiliary piston

(123) 17 Plunger piston

(124) 18 Level sensor

(125) 19 Electrical connections to ECU

(126) 20 Electrodes

(127) 21 Leakage flow

(128) 22 Housing extension

(129) 23 Separation chamber

(130) 24 Sponge

(131) 25 Outlet channels

(132) 26 Screen

(133) 27 DK collar

(134) 28 Annular piston

(135) 28a Annular piston seal

(136) 29 Return spring

(137) 30 Bending rod

(138) 31 DK pressure piston

(139) 32 Securing ring

(140) 33 Plunger

(141) 34 Seal

(142) 35 Primary seal

(143) 36 Secondary seal

(144) 37 Stop spring

(145) 38 Differential piston

(146) 39 Differential piston seal

(147) 40 Breather bore

(148) 43 Working chamber

(149) 45 Piston cylinder unit

(150) 46 Piston cylinder unit

(151) 115 SK positioning sensor

(152) 116 Auxiliary piston

(153) 116a Bypass for Hiko

(154) 117 Shutoff valve for MUX

(155) 118 Pedal return spring

(156) 119 Annular auxiliary piston

(157) 120 Breather bore (DK)

(158) 121 Stop for piston plunger (KS)

(159) 122 Return spring for KS

(160) 123 HZ return spring

(161) 123a HZ return spring

(162) 124 Shutoff valve to WS

(163) 125 DHK housing

(164) WS Travel simulator connection

(165) AS Shutoff valve

(166) WA WS cut-off valve

(167) WSA WS shutoff valve

(168) ESV Injection valve

(169) EA Inlet/outlet valve

(170) SV Switch valve

(171) E Inlet valve

(172) A Outlet valve

(173) SiV Safety valve

(174) RZ Wheel cylinder

(175) R Return flow line

(176) BKV Brake force booster

(177) DG Pressure sensor

(178) RFE Fallback level

(179) VH Prestroke DHK

(180) RH Return stroke DHK

(181) T.sub.D Diagnosis time

(182) S1 Suction valve

(183) S2 Suction valve

(184) S3 Suction valve

(185) Pressure relief valve for prefilling (VF)

(186) R5 Check valve to the brake circuit

(187) TV1 HiKo isolation valve

(188) TV2 Isolation valve to the DK circuit

(189) TV3 Isolation valve to the SK circuit

(190) UV Changeover valve

(191) VB Reservoir

(192) LW Free travel