DE202019103814U1 - Pressure supply unit for a hydraulic system with at least one consumer circuit and with at least one rotary pump - Google Patents

Abstract

Pressure supply unit for a hydraulic system with at least one consumer circuit (BK1, BK2) and with at least one rotary pump (Pa, Pb), wherein
- either by means of at least one rotary pump (Pa, Pb) a volume delivery in at least one delivery direction in at least one consumer circuit (BK1, BK2) takes place in such a way that a certain required volume (V eg in [cm ³ ]) of hydraulic medium, in particular for a Pressure build-up (Pauf), pressure reduction (Pab) and / or an adjustment of a unit is promoted and / or
- That at least two rotary pumps (Pa, Pb) are provided, with at least one of the rotary pumps (Pa, Pb) being able to build up and reduce the pressure in at least one consumer circuit (BK1, BK2) by means of a corresponding energization of the respective electric motor drive (Ma, Mb) is.

Description

The present invention relates to a pressure supply unit for a hydraulic system with at least one consumer circuit and with at least one rotary pump.

State of the art

For brake systems with increased failure safety, in particular for the pressure supply, redundant systems are also used with two pressure supply devices and electric motors. This is justified and necessary because the failure rates for a pressure supply device are in the region of 100ppm / year or 200 FIT. It is well known that if the pressure supply fails, the foot forces to actuate the brake are also higher than normal by a factor of 5, which means that the inexperienced driver usually cannot control this situation.

Brake systems with two pressure supply devices either use two plunger systems, the piston of which is usually adjusted by means of a spindle drive, or only one plunger system in combination with a rotary piston pump.

Out DE 10 2015 221 228 A1 a brake system with two rotary piston pumps is previously known, which generate a brake pressure and which are both driven by an electric motor. The pressure in the individual wheel brakes is set via the inlet and outlet valves. No travel simulator is used with this braking system. Each pump is assigned to exactly one brake circuit. If one pump fails, the other still functioning pump cannot take over the function of the failed pump, ie no brake pressure can be built up in the wheel brakes assigned to the failed pump by means of the still functioning pump.

Out DE 102016208529 A1 a similar brake system with two pumps is previously known, each pump being assigned to a brake circuit.

DE 10 2016 211 982 A1 discloses a braking device, two rotary pumps being provided, each of which is used to supply pressure to a brake circuit and is driven jointly by a drive motor. In addition, a plunger pump driven by an electric motor is provided, which supplies the two brake circuits via feed valves.

Out WO 01/42069 A1 a gear pump driven by an electric motor is known for building up pressure for a brake system of a vehicle.

Out WO 2017/144390 A1 a method for operating a brake system of a motor vehicle is known in which a primary brake system and a secondary brake system are provided. The primary and secondary brake systems each have rotary pumps for generating pressure. In normal operation, the brake pressure is built up by means of the primary brake system. The secondary brake system only takes over the pressure generation in the event of a malfunction in the primary brake system, which is recorded by means of a pressure detection system.

Out DE 10 2013 227 089 A1 a brake system for a vehicle is known in which a motor drives two pumps, each pump serving to build up pressure in a brake circuit. Out DE 10 2012 223 497 A1 Furthermore, a brake system for a vehicle is known in which a pump is driven by a motor, which is used to build up pressure for both brake circuits.

WO 2012/103925 A1 discloses a dual internal gear pump for a braking system. The double internal gear pump is two-circuit, ie it has two hydraulic circuits which are separate and sealed from one another, the two gear wheels each assigned to a hydraulic circuit being driven by a drive motor via a common shaft. This double internal gear pump has a large structural volume and additional sealing measures for high pressures.

For vehicles with higher safety requirements in the event of component failure, redundant concepts are required.

Object of the invention

The object of the present invention is to provide a pressure supply unit which can provide a cost-effective and simple pressure control for a hydraulic system, in particular in the form of a brake system.

This object is achieved according to the invention with a pressure supply unit with the features of claim 1.

The pressure supply unit according to the invention can be used for a wide variety of hydraulic systems with at least one consumer circuit. In a consumer circuit, in turn, several consumers can be connected to the pressure supply unit via one or more hydraulic line (s). Switching valves can thus be assigned to one or each consumer, by means of which the respective consumer can be separated from the consumer circuit. The pressure supply unit can advantageously be used for a brake system the consumers described above are the wheel brakes.

The pressure supply unit according to the invention can have at least one rotary pump, by means of which a volume delivery can take place in at least one delivery direction in at least one consumer circuit, such that a certain required volume V , for example in cm ³ , of hydraulic medium, in particular for a pressure build-up, pressure reduction and / or adjustment of a unit of a consumer.

As an alternative or in addition, the pressure supply device according to the invention can have at least two rotary pumps which are used for different maximum pressure levels Plmax and P2max and / or different pressure ranges P1min P1 P1max; P2min P2 P2max are designed, with the condition Plmax ≠ P2max in particular being applicable for the different pressure ranges. For example, one rotary pump can be designed for a pressure range greater than 120 bar and the other rotary pump for a pressure range less than or equal to 120 bar, with 120 bar corresponding to the blocking limit without fading for this vehicle. For example, one pump with a range of up to 120 bar could be used to build up pressure for all wheel brakes of the vehicle in multiplex mode MUX be provided. However, as soon as a pressure higher than 120 bar is required, the other higher-rated rotary pump could be switched on or it could take over the pressure control alone. It is also possible that the two print areas overlap.

In addition, a stage pump or a series connection of at least two rotary pumps for one or more hydraulic circuits can be used to achieve a higher pressure level, e.g. greater than 100bar.

Alternatively or in addition, when two rotary pumps are provided, these can have different delivery rates.

At least the drive motor for the rotary pump for volume control should be an electric motor with brushes and with semiconductors, e.g. MOSFET control for forward and reverse. The drive motor for the pump for the higher pressure range can be a brushless motor. In a preferred embodiment both drive motors are electric motors with brushes and with semiconductors, e.g. MOSFET control for flow and return, so that both rotary pumps can be used to build up and reduce pressure.

The pressure supply unit described above is inexpensive, simple and has a small structural volume.

1. 1. Rotationskolbenpumpe, wie z.B. Drehkolbenpumpe, Drehschieberpumpe, Kreiskolbenpumpe, Flügelzellenpumpe, Zahnring- oder Zahnradpumpen;
2. 2. Radialpumpe, insbesondere in Form einer Radialkolbenpumpe;
3. 3. Strömungspumpe, insbesondere in Form einer Kreiselpumpe;
4. 4. Verdrängerpumpe mit rotierendem Rotor, welcher mit einer ihn umgebenden Wandung in sich geschlossene Volumina bildet, in denen das Medium durch die Rotation gefördert wird;

For the purposes of the invention, a rotary pump is understood to mean one of the pumps listed below:

1. 1. Rotary piston pumps, such as rotary piston pumps, rotary vane pumps, rotary piston pumps, vane pumps, gerotor pumps or gear pumps;
2. 2. Radial pump, in particular in the form of a radial piston pump;
3. 3. Flow pump, in particular in the form of a centrifugal pump;
4. 4. Displacement pump with a rotating rotor which, with a wall surrounding it, forms self-contained volumes in which the medium is conveyed by the rotation;

A rotary pump in the sense of the invention is in particular not understood to include a reciprocating piston pump in which the piston executes a straight (translational) movement.

The rotary pump within the meaning of the invention preferably has an electric motor drive whose rotor, e.g. which forms or drives at least one gear wheel of a gear pump or the impeller of a centrifugal pump.

In the context of the invention, a 1-circuit rotary pump is understood to mean a rotary pump with only one hydraulic circuit, i.e. it has only one input and one output, a rotor. The 1-circuit rotary pump, on the other hand, can have a single-stage or multi-stage design, the individual stages being arranged in series so that e.g. the first stage builds up a first pressure level and the following stage a higher pressure level.

In the context of the invention, a multi-circuit rotary pump is understood to mean a rotary pump which has a plurality of hydraulically separated and sealed hydraulic circuits, this having or being able to have only one electric drive for all hydraulic circuits.

The pressure supply unit according to the invention can e.g. advantageously replace a motor-driven piston-cylinder unit of known brake systems, which often have expensive spindle drives or ball screws. Such expensive screw drives are omitted in the pressure supply unit according to the invention, as a result of which it is small and inexpensive.

The above-described volume delivery can advantageously take place by means of a volume control, such that the proportionality between the angle of rotation Δφ of the rotor of the rotary pump and the volume conveyed V the necessary angle of rotation Δφ for a required volume V _should is calculated on hydraulic medium and then by means of the drive of the rotary pump, the rotor or the pump element is adjusted by the calculated angle of rotation.

In addition or as an alternative, the time can also be used for volume control Δt be taken into account within which the required volume V _should to be conveyed to hydraulic medium, the speed of the rotor of the rotary pump v _M the time available Δt is adjusted. In this way, a volume of hydraulic fluid to be conveyed can also be conveyed precisely.

By varying the motor current, the delivery rate and also the delivery direction can be determined. The direction of rotation or the conveying direction can thus be actively influenced by the direction of the motor current. It is also possible that the direction of flow of the hydraulic medium through the rotary pump changes simply by lowering the motor current, provided that a correspondingly high pressure is still included in a hydraulic circuit.

The pressure volume characteristic (PV characteristic) of one or both brake circuits and / or the respective wheel brake can also advantageously be used for quantitative pressure control. The PV characteristic curve can be determined before the vehicle starts.

The pressure supply unit according to the invention can advantageously have at least two pressure supply devices, each pressure supply device having at least one rotary pump and a drive for driving the respective rotary pump. It is also possible that the pressure supply unit according to the invention has only a single pressure supply device, this pressure supply unit either at least two hydraulically connected rotary pumps in series, in particular in the form of a two-stage or multi-stage rotary pump, or two series connections of at least two hydraulically connected rotary pumps in each case having, in the latter case each of the series-connected rotary pumps are driven by a single drive or each series connection is driven by its own drive.

The rotary pump can also be a multi-circuit rotary pump which has several hydraulic circuits that are separate and sealed from one another.

The rotary pump, at least for volume control, can be designed in one or more stages, with several stages being arranged hydraulically in series.

With a multi-stage design of the rotary pump, both pump stages can be driven by one and the same drive and e.g. supply one or more hydraulic circuits.

The rotary pump not provided for volume control can be a simple continuously delivering pump, in particular in the form of a piston pump, vane pump, rotary vane pump or gear pump. This generates a certain pressure depending on the drive power and the motor current. The pressure can be regulated by current regulation. However, it is also possible for valves controlled by pulse width modulation to regulate the pressure provided by the continuously conveying pump for the consumer or consumers.

If the pressure supply unit has at least two pressure supply devices or rotary pumps, it can supply a corresponding number of consumer circuits, in particular in the form of brake circuits, with hydraulic medium and corresponding pressure. Advantageously, e.g. a rotary pump can be assigned to each consumer circuit.

In order to provide a particularly fail-safe pressure supply unit, a hydraulic connection line can be provided in a hydraulic system with two consumer circuits, with at least one switchable valve, in particular two switchable bypass valves connected in series, for the optional opening and closing of the connection line, to increase safety. This advantageously results in the possibility that either the other still functioning pressure supply device or rotary pump takes over the function of the failed one in the event of a failure of one pressure supply device or rotary pump, or that both pumps cooperate via the hydraulic connecting line to build up pressure in one or both brake circuits. The latter case is used advantageously to enable the pressure to be built up within a very short time (time to lock = TTL). The individual pumps can be made smaller.

When two rotary pumps are provided, one rotary pump can advantageously be designed for a lower maximum pressure Plmax than the other rotary pump with P2max. Provided If higher pressures than Plmax are required, either the other pump with its higher maximum pressure P2max can be switched on or the pressure build-up can be done on its own. If the pump with the higher maximum pressure fails, a maximum pressure of Plmax can still be provided.

However, it is also possible, when two rotary pumps are provided that have the same maximum pressure, to connect the two rotary pumps in series by means of suitable valves in order to form a two-stage pump, with the delivery pressure of both pumps then being added. At least one non-return valve and a switching valve connected in parallel must then be provided here if necessary.

Different maximum pressures also result if the electrical drive power of the drive of one rotary pump is greater than the electrical drive power of the drive of the other rotary pump.

The pressure supply unit can also be used advantageously for the hydraulic system of an electric vehicle, with only one pressure supply device having to be provided, which in particular only serves to generate brake pressure in a brake circuit.

If present, both rotary pumps can advantageously be arranged in one housing. It is also possible for the axes of the rotary pumps to be aligned parallel to one another and for the axes to be arranged in particular parallel or perpendicular to the axis of the master brake cylinder, if this is present. The brake master cylinder can either be arranged in a separate housing or together with the rotary pumps in a common housing.

In addition, the solenoid valves, especially for all control and regulating functions ( ESP , SECTION ) be arranged in a housing. The electronic control and regulation unit ECU can be arranged in a separate ECU housing. The sensors can be arranged either in the ECU housing or on it. The ECU itself can be designed partially or fully redundant.

The brake system according to the invention can have a single or tandem master brake cylinder which can be actuated by a brake pedal. Alternatively, an electric pedal or just an actuation switch e.g. for level 5 for automatically driving vehicles (AD).

In the case of a non-redundant on-board network, an auxiliary on-board network, e.g. can be used with U-caps for some braking operations, so that if the on-board network fails while driving and thus also when the vehicle is driven, braking is still possible until the vehicle comes to a standstill.

With the aforementioned features, a 1-box solution with two pressure supply devices can advantageously be implemented cost-effectively and smaller than a conventional 1-box solution with plunger pistons.

At least one valve can be provided at the outlet of the pressure supply device, which valve is or are used for pressure regulation and prevents or prevents a backflow of hydraulic medium into the storage container.

The use of the pressure supply unit according to the invention in various possible embodiments of hydraulic systems is explained in more detail below with reference to drawings.

• 1: Eine erste mögliche Ausführungsform eines erfindungsgemäßen Hydrauliksystems mit einer fehlersicherer Ventilanordnung zur Verbindung beider Bremskreise, einem Hauptzylinder mit Betätigungseinrichtung sowie zwei Druckversorgungseinrichtungen mit elektronischer Steuer- und Regeleinrichtung als sogenannte Integrierte 1-Box-Anlage;
• 1a: eine zweite mögliche Ausführungsform eines erfindungsgemäßen Hydrauliksystems mit einer fehlersicheren Ventilanordnung zur Verbindung beider Bremskreise, einem Hauptzylinder mit Betätigungseinrichtung sowie zwei Druckversorgungseinrichtungen mit elektronischer Steuer- und Regeleinrichtung als sogenannte Integrierte 1-Box-Anlage;
• 1b: eine dritte mögliche Ausführungsform eines erfindungsgemäßen Hydrauliksystems mit einer fehlersicheren Ventilanordnung zur Verbindung beider Bremskreise, einem Hauptzylinder mit Betätigungseinrichtung sowie zwei Druckversorgungseinrichtungen mit elektronischer Steuer- und Regeleinrichtung als sogenannte Integrierte 1-Box-Anlage;
• 1c: eine vierte mögliche Ausführungsform eines erfindungsgemäßen Hydrauliksystems mit einer fehlersicheren Ventilanordnung zur Verbindung beider Bremskreise, einem Hauptzylinder mit Betätigungseinrichtung sowie mit einer Druckversorgungseinrichtung mit elektronischer Steuer- und Regeleinrichtung als sogenannte Integrierte 1-Box-Anlage;
• 1d: eine Fortentwicklung der vierten Ausführungsform gemäß 1c mit zwei zweistufigen Pumpenanordnungen;
• 2: Eine fünfte mögliche Ausführungsform eines erfindungsgemäßen Hydrauliksystems mit einem Hauptzylinder mit Betätigungseinrichtung sowie mit einer Druckversorgungseinrichtung mit elektronischer Steuer- und Regeleinrichtung;
• 3 und 3a: erste mögliche Ausführungsform einer Anordnung der einzelnen Komponenten, insbesondere Gehäuse der Druckversorgungseinheit in zwei Ansichten;
• 3b: perspektivische Ansicht der Druckversorgungseinheit gemäß 3 und 3a;
• 4 und 4a: zweite mögliche Ausführungsform einer Anordnung der einzelnen Komponenten, insbesondere Gehäuse der Druckversorgungseinheit in zwei Ansichten;
• 4b: perspektivische Ansicht der Druckversorgungseinheit gemäß 4 und 4a.

Show it:

• 1 : A first possible embodiment of a hydraulic system according to the invention with a fail-safe valve arrangement for connecting both brake circuits, a master cylinder with actuating device and two pressure supply devices with electronic control and regulating device as a so-called integrated 1-box system;
• 1a : a second possible embodiment of a hydraulic system according to the invention with a fail-safe valve arrangement for connecting both brake circuits, a master cylinder with actuating device and two pressure supply devices with electronic control and regulating device as a so-called integrated 1-box system;
• 1b : a third possible embodiment of a hydraulic system according to the invention with a fail-safe valve arrangement for connecting both brake circuits, a master cylinder with actuating device and two pressure supply devices with electronic control and regulating device as a so-called integrated 1-box system;
• 1c : a fourth possible embodiment of a hydraulic system according to the invention with a fail-safe valve arrangement for connecting both brake circuits, a master cylinder with an actuating device and a pressure supply device with an electronic control and regulation device as a so-called integrated 1-box system;
• 1d : a further development of the fourth embodiment according to FIG 1c with two two-stage pump arrangements;
• 2 : A fifth possible embodiment of a hydraulic system according to the invention with a master cylinder with actuation device and with a pressure supply device with electronic control and regulation device;
• 3 and 3a : first possible embodiment of an arrangement of the individual components, in particular the housing of the pressure supply unit in two views;
• 3b : perspective view of the pressure supply unit according to FIG 3 and 3a ;
• 4th and 4a : second possible embodiment of an arrangement of the individual components, in particular the housing of the pressure supply unit in two views;
• 4b : perspective view of the pressure supply unit according to FIG 4th and 4a .

1 shows the basic elements of a controllable braking system for vehicles, consisting of the master brake cylinder SHZ with path simulator WS and storage container VB as well as two pressure supply devices DV1 and DV2 . The pressure supply device DV1 in turn instructs the rotary pump Pa , the brushless DC motor Ma , the rotor angle encoder WGa of engine Ma with electrical connection Wea, the winding connection 3a of DC motor Ma as well as the shunt 4a from the DC motor Ma on. The pressure supply device DV2 instructs the rotary pump Pb , the DC motor Mb , the winding connection 3b of DC motor Mb as well as the shunt 4b from the DC motor Mb on. Both rotary pumps Pa and Pb of the two pressure supply devices DV1 and DV2 are, in particular 1-circuit, rotary pumps. The rotary pump Pa can preferably be a gear pump. The rotary pump Pa the pressure supply device DV1 is preferably driven by a brushless direct current motor (EC motor) Ma, while the rotary pump Pb the pressure supply device DV2 from a DC motor Mb , preferably with brushes. The rotary pump Pb can be a simple 1-circuit gear pump or a 1-circuit piston pump.

1. (1) Verbindung von der für den ersten Bremskreis BK1 vorgesehenen Druckversorgungseinrichtung DV1 zum zweiten Bremskreis BK2;
2. (2) Verbindung von der für den zweiten Bremskreis BK2 vorgesehenen Druckversorgungseinrichtung DV2 zum ersten Bremskreis BK1;
3. (3) Verbindung von dem Druckraum des Hauptbremszylinders SHZ über das Schaltventil FV hin zu den Bremskreisen BK1, BK2 über die Bypassventile BP1 und BP2;
4. (4) Verbindung von Schaltventil PD1 und Bypassventil BP1 zu den Radbremszylindern RZ1 und RZ2 über die jeweiligen den Radbremsen zugeordneten Schaltventile SV
5. (5) Verbindung von Bypassventil BP2 zu den Radbremszylindern RZ3 und RZ4 über die jeweiligen den Radbremsen zugeordneten Schaltventile SV;
6. (6) Verbindung von einem Bremskreis BK1, BK2 hin zum Vorratsbehältnis VB;
7. (7) Verbindungen zwischen Bremskreisen BK1, BK2 hin zu den Radbremszylindern RZ.

The pressure supply device DV1 is designed for the usual locking pressure, whereby locking pressure is understood to mean the minimum pressure at which all vehicle wheels lock. A blocking pressure of 120 bar is usual for most vehicles. Overheated brakes (fading) or overloading of the vehicle can cause the locking pressure to rise, so that the maximum pressure generated by the pressure supply device DV1 can be reached, eg 120bar, is not sufficient to lock all vehicle wheels. For this reason, the pressure supply device DV2 for higher pressures than the pressure supply device DV1 designed, e.g. for 200bar. Both pressure supply devices DV1 and DV2 can generate the wheel brake cylinder pressure individually or together, which is applied to the wheel brake cylinder by means of suitable valve positions of a valve circuit RZ1 , RZ2 , RZ3 , RZ4 , e.g. B. at SECTION , is set or regulated in the respective wheel brake cylinders. In principle, this is state of the art. The pressure supply unit according to the invention for a hydraulic system or brake system should, however, have a high level of error security, for example for highly automated (HAD) or fully automated driving (FAD). For this purpose, all failure-relevant components should be taken into account, such as B. Valves, sensors, seals, motors and brake circuits. The following components or hydraulic connections should therefore advantageously be designed to be fail-safe:

1. (1) Connection from that for the first brake circuit BK1 provided pressure supply device DV1 to the second brake circuit BK2 ;
2. (2) Connection from that for the second brake circuit BK2 provided pressure supply device DV2 to the first brake circuit BK1 ;
3. (3) Connection from the pressure chamber of the master cylinder SHZ via the switching valve FV towards the brake circuits BK1 , BK2 via the bypass valves BP1 and BP2 ;
4. (4) Connection of switching valve PD1 and bypass valve BP1 to the wheel brake cylinders RZ1 and RZ2 Via the respective switching valves SV assigned to the wheel brakes
5. (5) Connection of bypass valve BP2 to the wheel brake cylinders RZ3 and RZ4 via the respective switching valves assigned to the wheel brakes SV ;
6. (6) Connection from a brake circuit BK1 , BK2 towards the storage container VB ;
7. (7) Connections between brake circuits BK1 , BK2 towards the wheel brake cylinders RZ .

These hydraulic connections with possible failure errors of the individual components are described below.

The pressure supply device DV1 acts from the brake circuit BK1 in the brake circuit BK2 via the hydraulic lines 1 , 2 and 5 and via the switching valves SV to the wheel brake cylinder RZ1 , RZ2 , RZ3 , RZ4 . In the prior art, only a single bypass valve is used for this purpose. A failure of the single bypass valve can cause a total failure of the brake if there is also a sleeping error in another valve. Under " dormant error ”is understood to mean a single error that does not have an effect on braking, but which can, in combination with another error, have an effect on braking. The invention therefore provides two redundant bypass valves BP1 and BP2 in front of the connection to the brake circuit BK2 from the first pressure supply device DV1 to enable. Sleeping faults in the bypass valves BP1 and BP2 are by means of pressure transducers DG detected by the pressure supply device during a pressure change DV1 who have favourited bypass valves BP1 and BP2 are closed alternately one after the other over a short period of time. During the closing phase of the bypass valve BP1 or bypass valve BP2 must be the pressure in the brake circuit BK2 stay constant. If the first pressure supply device fails DV1 , e.g. if the DC motor fails Ma , will have an effect on the brake circuit BK2 via the two redundant bypass valves BP1 , BP2 and the switching valve PD1 prevented. The bypass valves BP1 and BP2 are preferably normally open valves so that the pressure supply equipment fails DV1 and DV2 the master cylinder SHZ via the open switching valve FV on both brake circuits BK1 and BK2 can work. Should the pressure in the wheel brake cylinders RZ1 , RZ2 , RZ3 and RZ4 this can be reduced by opening the switching valves ZAV or FV respectively. The two bypass valves BP1 and BP2 without their own electrical control, due to the differential pressure acting via these bypass valves BP1 and BP2 open automatically, which in the event of a fault, e.g. failure of the control electronics of the two bypass valves BP1 and BP2 , it is ensured that a pressure reduction is possible and, for example, locking of the wheels is reliably prevented.

The pressure supply device acts accordingly DV2 in the second brake circuit BK2 via the hydraulic lines 2 and 5 and via the switching valves SV to the wheel brake cylinders RZ3 and RZ4 , and via the bypass valves BP2 and BP1 in the hydraulic line 4th and from there via the switching valves SV to the wheel brake cylinders RZ1 and RZ2 . A failure of the brake circuit BK1 , for example due to a leak in a seal in one of the wheel brake cylinders RZ1 , RZ2 , can be diagnosed using one of the switching valves SV in brake circuit BK1 are recognized, then the bypass valves BP1 and BP2 are closed, causing a failure of the pressure supply device DV2 is prevented and by means of the pressure supply device DV2 in the brake circuit BK2 pressure regulation or control is still possible. A failure of the brake circuit BK2 , for example due to a leak in a seal in a wheel brake cylinder RZ3 or RZ4 , can be diagnosed using one of the switching valves SV in brake circuit BK2 are recognized, and then likewise the bypass valves BP1 and BP2 are closed, causing a failure of the pressure supply device DV1 is prevented and by means of the pressure supply device DV1 in the brake circuit BK1 pressure regulation or control is still possible. Here are leaks of all valves, for example SV , BP1 , BP2 to be regarded as a dormant error in terms of safety. The hydraulic medium flowing through the valves thus contains dirt particles which can prevent the respective valve from closing and the valves thus become leaky. In the present case, for example, if a seal in a wheel brake cylinder fails RZ1 or RZ2 and by the dormant fault of the associated switching valve SV although the brake circuit BK1 fail, the brake circuit BK2 is, however, due to the interposition of the two bypass valves BP1 and BP2 secured. In a similar way, if a seal in a wheel brake cylinder fails, for example RZ3 or RZ4 and by the dormant fault of the associated switching valve SV although the brake circuit BK2 fail, the brake circuit BK1 however, is also due to the interposition of the two bypass valves BP1 and BP2 secured. There should be a triple fault here, ie both bypass valves BP1 and BP2 would have to fail in addition, so that a total failure of both brake circuits BK1 and BK2 present. Each of the two brake circuits BK1 and BK2 is thus safely protected against double faults and prevents total brake failure. Security against double faults, when dormant faults can occur, is a crucial security feature for HAD and FAD . This also includes maintaining the pressure supply or the brake booster in the event of a brake circuit failure.

The pressure supply device DV2 can, with rapid pressure build-up, or pressure build-up above 120 bar, for example, the other pressure supply device DV1 support and / or perform the ABS function and / or if the other pressure supply device fails DV1 take over its function. A pressure reduction can be achieved by means of a rotary pump Pa , PBb or, if available, alternatively or simultaneously by means of at least one outlet valve ZAV , AV1 , AV2 respectively.

It is also possible that the pressure supply device DV1 takes over the pressure build-up for pressure ranges less than or equal to 120 bar and for the ABS function. The pressure reduction in a brake circuit takes place by reversing the direction of rotation of the rotary pump Pa . If the pressure supply device fails DV2 if the pressure supply device DV1 is only designed for a maximum pressure of eg 120 bar, only this maximum pressure of eg 120 bar for both brake circuits BK1 and BK2 to disposal.

With closed bypass valves BP1 and or BP2 can use the two pressure supply devices DV1 and DV2 in their brake circuits BK1 and BK2 adjust or adjust the pressure independently of each other. Here, too, the pressure can be reduced using the rotary pumps Pa respectively. If, however, additional outlet valves ZAV , AV1 , AV2 are present, the pressure in one or more wheel brakes can also be reduced via these. A simultaneous pressure reduction by means of a rotary pump, e.g. Pa , e.g. in the wheel brake RZ1 by reversing the direction of rotation of the rotary pump Pa take place at the same time, for example in the wheel brake RZ3 via the rotary pump Pb or via an outlet valve AV2 , ZAV the pressure is released.

The pedal movement is controlled by redundant pedal travel sensors PS measured at the same time on a KWS measuring element (force-displacement sensor) WO2012 / 059175 A1 Act. With the signals from the pedal travel sensors, the pressure supply device DV1 controlled, the rotary pump Pa the volume flow in the hydraulic line 1 in the brake circuit BK1 and via the redundant bypass valves BP1 and BP2 in the brake circuit BK2 causes. The pressure supply device DV1 can be designed so that they only up to the blocking pressure z. B. 120 bar acts. The pressure supply device then delivers for higher pressures DV2 Volume in the brake circuit BK2 and via the redundant bypass valves BP1 and BP2 , and with the switching valve closed PD1 , in brake circuit BK1 . The pressure supply device can DV2 be a continuously delivering pump. If the brake system is badly vented or if vapor bubbles develop with a higher volume requirement, this is recorded via the known pressure volume characteristic (PV characteristic) of the brake, which has the consequence that the pressure supply device DV1 must deliver more volume in order to maintain a certain pressure in the wheel brake cylinders RZ1 , RZ2 , RZ3 and RZ4 to reach. When the pedal is pressed, the piston Ko moves, which is applied to the known travel simulator via the pedal force proportional pressure WS acts and thus determines the pedal characteristics. The path simulator WS can usually be switched off via a valve, especially in the fall-back level if the pressure supply devices fail DV1 and DV2 . In the case of redundant pressure supply devices, this is in principle no longer relevant due to the very low probability of failure.

Over the line 3 can the master cylinder SHZ with the brake circuits BK1 or BK2 be connected, being in the hydraulic line 3 the switching valve FV is arranged to close the same. This connection is only in the fall-back level, ie when both pressure supply devices DV1 and DV2 have failed. Unless the hydraulic line 3 with the connection line VLa of the two bypass valves BP1 and BP2 is connected, form the two bypass valves BP1 and BP2 another redundancy. A common connection from the switching valve FV directly into one of the two brake circuits BK1 , BK2 would have if the switching valve leaks FV As a result, the brake circuit and thus the pressure supply act on the SHZ piston Ko, which must immediately result in the pressure supply being switched off.

A failure of the brake circuit BK2 can, for example, when using a 1-circuit gear pump as a rotary pump Pb due to a leak in the check valve RV1 arise. The failure of the pressure supply device DV2 can use a redundant check valve here RV2 be prevented. A hydraulic connection between the two check valves RV1 and RV2 to the storage container VB with the throttle Dr with small flow enables diagnosis, e.g. B. via measurable pressure drop.

For ABS control or for pressure reduction with the second pressure supply device DV2 is a central exhaust valve ZAV necessary. The volume flow also goes through the bypass valves BP1 or BP2 so that a leaky ZAV is not critical for normal operation, since there is a leak in the central outlet valve ZAV the pressure control in BK1 via the pressure supply device DV1 and the pressure control in BK2 via the pressure supply device DV2 takes place for pressure build-up. The pressure reduction in the brake circuit BK2 can continue even if the outlet valve is leaking ZAV via the bypass valve BP2 respectively. In addition, the bug, also dormant, is from ZAV equal by pressure change or increased volume delivery of the pressure supply device DV1 recognized.

The pressure supply device works with normal braking up to approx. 120 bar DV1 via open bypass valves BP1 and BP2 in both brake circuits BK1 and BK2 . A redundant outlet valve can also be used for extreme safety requirements ZAVr in the hydraulic line 6th from the central exhaust valve ZAV to the storage container VB to be built in.

The ABS function via multiplex operation MUX and the pressure supply device DV1 occurs as in WO 2006/111393 A1 described. However, in the case of the rotary pump, in particular in the form of a gear pump, the direction of rotation is reversed in order to reduce the pressure. Extended multiplex functions result from a central outlet valve ZAV . Is in the process of building up pressure Pauf in the brake circuit BK1 at the same time a pressure reduction Pab in the other brake circuit BK2 if necessary, this pressure reduction takes place via the central outlet valve ZAV with the bypass valve closed at the same time BP1 . This is the multiplex operation MUX only through two wheel brake cylinders RZ1 and RZ2 in the brake circuit BK1 burdened. For example, pressure cannot build up at the same time Pauf in wheel brake cylinder RZ1 and a depressurization Pab in wheel brake cylinder RZ2 of the brake circuit BK1 respectively. Alternatively, an outlet valve can also be used AV1 or. AV2 in the respective brake circuit BK1 or. BK2 to reduce pressure Pab to relieve the multiplex operation MUX be used. On the one hand, the outlet valve AV1 or. AV2 either between a switching valve SV and a bypass valve BP1 or. BP2 or between the wheel brake cylinder and the associated switching valve SV arranged or connected, and on the other hand to the storage container VB connected, so that a direct pressure reduction Pab via the outlet valve to the storage container VB can be done. This is especially to relieve pressure Pab makes sense in the wheel brake cylinders of the front wheels. The central outlet valve ZAV is not required with this alternative.

The ABS function by means of the second pressure supply device DV2 in this case is slightly restricted, in particular there is no pressure build-up Pauf in a wheel brake cylinder during depressurization Pab possible or provided in another wheel brake cylinder. A fully individual ABS control is still possible. The infrequent use of the pressure supply device must be taken into account DV2 at pressures greater than 120 bar and if the first pressure supply device fails DV1 .

Typical for the above-mentioned multiplex operation MUX in ABS operation, for example, is that the pressure control with the pressure supply device DV1 via the volume metering, which by means of the rotor rotation or the rotor rotation angle of the rotary pump, which by means of the rotor angle encoder WGa is measured, is calculated. The pressure-volume characteristic of the brake (PV characteristic) can also be taken into account here.

When using a simple eccentric piston pump as a rotary pump Pb at the pressure supply device DV2 this cannot be done via the piston movement, but via the delivery time, which is proportional to the delivered volume with additional speed measurement and, if necessary, pressure measurement. Thus, a volume measurement for the pressure build-up by means of the pressure supply device is also possible DV2 possible. A serial and not simultaneous pressure build-up is advantageous here Pauf in the individual wheel brake cylinders.

The valve dimensioning of the back pressure at the valve must be taken into account, particularly with the bypass valves BP1 and BP2 with rapid pressure build-up Pauf in the brake circuits. The back pressure at the bypass valves BP1 and BP2 acts as a pressure difference between the brake circuits BK1 and BK2 . This can be reduced considerably if both pressure supply devices are in this operating state DV1 and DV2 be switched on. A 1-circuit gear pump is also available for the pressure supply device DV2 instead of a piston pump. This can reduce the pressure Pab and pressure build-up Pauf can also be done via the gear pump. This is done instead of the check valves RV1 and RV2 a switching valve, not shown, in the return line to the storage container VB necessary. This also applies to the second pressure supply device DV2 a full multiplex operation MUX possible.

The control and regulation device ECU in housing B. is part of the entire system and packaging. A redundant or partially redundant function is required for a fail-safe function ECU necessary. This partially redundant ECU can also be used for certain functions in addition to redundant ECU be used. In any case, the valves are or should be driven redundantly via separate valve drivers and disconnectors, which switch off a failed valve driver.

For redundancy of the control and regulation device ECU in housing B. is also a redundant on-board network connection BN1 or. BN2 , or an auxiliary electrical system connection with e.g. U-caps BN2 ' if the redundant on-board power supply connection BN2 is not available, necessary. A connection with 48V can also be used to connect the motors. The advantage of 48V is higher dynamics. In the event of a motor failure from the pressure supply device DV1 at 48V there is emergency operation with 12V with approx. 50% power with reduced dynamics, which advantageously results in cost savings. For this purpose, the motor must be designed for e.g. 24V.

Preferably in the brake circuit BK2 a pressure transducer DG , possibly also in BK1 (as shown in dashed lines) used. If the pressure transducer fails, the pressure can be regulated via the current measurement of the motors and the angle control of the rotors, in particular in the form of gears, via the pressure-volume characteristic (PV characteristic).

In the hydraulic line 2 the pressure supply device DV2 can also have a pressure relief valve ÜV be arranged to protect the drive, which opens at about 120 bar, for example.

1a shows a second possible embodiment of a hydraulic system according to the invention, which is based on the in 1 shown builds up. The difference to the in 1 The first possible embodiment shown is the configuration of the pressure supply device DV2 . From the axis From of the DC motor Mb become two rotary pumps Pb and Pb1 , especially in the form of gear pumps, instead of the individual rotary pump Pb according to 1 , powered. Are there the rotary pumps Pb and Pb1 hydraulically connected in series. Rotary pump Pb is on the input side directly via hydraulic line HL1 with the storage container VB connected. The rotary pump Pb is on the output side directly with the input side of the rotary pump Pb1 connected. The hydraulic line 2 connects the output side of the rotary pump Pb1 with the brake circuit BK2 . In the hydraulic line 2 is a normally closed switching valve PD2 introduced, which when the DC motor is energized Mb is opened. When the pressure in the hydraulic line 2 should no longer be increased, the switching valve PD2 closed so that no volume from the hydraulic line 2 by the rotary pumps Pb and Pb1 and through the hydraulic line HL1 back to the storage container VB can flow. Likewise, if the rotary pumps fail or leak Pb and Pb1 , or if the DC motor fails Mb , the switching valve PD2 closed.

The series connection of the rotary pumps Pb and Pb1 , which are in particular gear pumps, forms a two-stage pump, by means of which the pressure supply device DV2 higher pressures in the hydraulic line 2 than when using a single rotary pump Pb , with the same volume delivery. Are both rotary pumps Pb and Pb1 designed for a maximum pressure of 100 bar, for example, then by connecting the two rotary pumps in series Pb and Pb1 a maximum pressure in the hydraulic line 2 which corresponds roughly to the sum of the two maximum pressures 100bar + 100bar = 200bar.

1b shows a third possible embodiment of a hydraulic system according to the invention, which is based on the in 1 hydraulic system shown builds. The difference to the in 1 The hydraulic system shown is the configuration of the pressure supply device DV2 . The pressure supply device DV2 consists of the rotary pump Pb , which is in particular a gear pump, a brushless DC motor Mb to drive the rotary pump Pb , the rotor angle encoder WGb of the DC motor Mb with electrical connection Web , the winding connection 3b of the DC motor Mb as well as the shunt 4b of the DC motor Mb . As with the pressure supply device DV1 is the rotary pump Pb and the DC motor Mb designed for the blocking pressure, eg 120bar. This design of the pressure supply device DV2 it is possible with the switching valve open PD2 , the brake pressure in the brake circuit BK2 and in the wheel brake cylinders RZ3 and RZ4 with the rotary pump Pb to increase and also with the rotary pump Pb to reduce. To reduce the brake pressure in the wheel brake cylinders RZ3 and RZ4 and in the brake circuit BK2 becomes the motor torque of the DC motor Mb reduced, reducing the direction of rotation of the rotary pump Pb due to the pressure still prevailing in the brake circuit BK2 is reversed compared to the direction of rotation of the rotary pump Pb at the pressure increase. Hydraulic medium then flows out of the wheel brake cylinders RZ3 and RZ4 , through the associated switching valves SV , the hydraulic line 5 , the open switching valve PD2 who have favourited the rotary pump Pb and the hydraulic line HL1 back to the storage container VB .

The rotary pump Pa the pressure supply device DV1 can, as already to 1 described to increase the brake pressure in the wheel brake cylinders RZ1 and RZ2 Hydraulic medium through the hydraulic lines 7th , 7a and HL2 from the storage container VB suck in. The difference from the embodiment according to 1 is that in the hydraulic line 7th , 7a a check valve RV3 is arranged. The check valve RV3 has a large cross-section, so that the throttling losses through the check valve RV3 when sucking in hydraulic medium from the storage container VB are low. As with 1 described, the brake pressure in the wheel brake cylinder RZ1 and RZ2 with the switching valve open PD1 , and the associated switching valves SV by means of the rotary pump Pa be reduced by reducing the motor torque by reducing the current supply to the DC motor Ma is reduced, thereby changing the direction of rotation of the rotary pump Pa is reversed due to the pressure in the wheel brakes compared to the direction of rotation of the rotary pump Pa during pressure build-up. However, as the check valve RV3 blocks when the pressure is reduced, is another normally closed switching valve PD4 necessary, which is parallel to the check valve RV3 is arranged, and which is opened when the pressure is reduced. When the pressure in the wheel brake cylinders is reduced RZ1 and RZ2 Hydraulic medium then flows out of the wheel brake cylinders RZ1 and RZ2 , through the open associated switching valves SV who have favourited hydraulic lines 4th and 1 , the open switching valve PD1 who have favourited the rotary pump Pa , the hydraulic line 7th , 7a , the open switching valve PD4 and the hydraulic line HL2 back to the storage container VB . The higher throttling losses of the switching valve PD4 compared to the throttling losses of the check valve RV3 play no significant role in the pressure reduction gradient.

The inlet side of the rotary pump Pa is with the output side of the rotary pump Pb via a hydraulic line 6th connected. The hydraulic lines 6th and 7th are in the point A. connected with each other. In this hydraulic line 6th is a normally closed switching valve PD3 contain. Is the braking with the help of the pressure supply device DV1 initiated, and a high pressure of 160 bar, for example, is generated in the wheel brake cylinders RZ1 , RZ2 , RZ3 and RZ4 required, which is higher than the maximum pressure of the pressure supply device DV1 is, e.g. 120bar, it becomes, with the switching valves closed PD2 and PD4 and open switching valve PD3 , the pressure supply device DV2 turned on by the DC motor Mb is energized, whereby a series connection of the pressure supply devices DV1 and DV2 results. Thus becomes the rotary pump Pa from the actuator DV1 on the input side, through the hydraulic line 6th , the open switching valve PD3 and the hydraulic line 7th with the output pressure of the rotary pump Pb acted upon, with the effect that the output pressure of the rotary pump Pa the pressure supply device DV1 the sum of the differential pressures (rotary pump on the inlet side to the outlet side) of the rotary pump Pa from the pressure supply device DV1 , e.g. 120bar, and the rotary pump Pb from the pressure supply device DV2 , is, for example, 120bar + differential pressure of the rotary pump Pb . This total value can be used when the bypass valves are open BP1 and BP2 with the value of the pressure transducer DG can be compared, and the motor current of the DC motor Mb be set so that the measured pressure of the pressure transducer DG the required pressure of e.g. 160 equals, the differential pressure of the rotary pump Pb then in this example is 40bar.

Should the brake pressure in the wheel brake cylinder RZ1 , RZ2 , RZ3 and RZ4 be reduced from eg 160bar, to eg 100bar, then the motor torque of the DC motor Mb reduced by undercurrent or, if the pressure is to be reduced very quickly, reversed in sign, while the motor torque of the DC motor Ma is initially held at the maximum value, reducing the direction of rotation of the rotary pumps Pa and Pb is reversed. Hydraulic medium then flows out of the wheel brake cylinders RZ1 and RZ2 , through the associated switching valves SV who have favourited hydraulic lines 4th and 1 , the open switching valve PD1 who have favourited the rotary pump Pa , the open switching valve PD3 who have favourited Gear Pump Pb and the hydraulic line HL1 back to the storage container VB . Hydraulic medium also flows out of the wheel brake cylinders RZ3 and RZ4 through the associated switching valves SV , the hydraulic line 5 , the open bypass valves BP1 and BP2 , Hydraulic line 1 , the open switching valve PD1 who have favourited the rotary pump Pa , the switching valve PD3 who have favourited the rotary pump Pb and the hydraulic line HL1 back to the storage container VB . When the pressure has dropped to 120bar, or the motor current from a DC motor Mb was reduced to 0 amps, then the pressure in the wheel brake cylinders is further reduced RZ1 , RZ2 , RZ3 and RZ4 the pressure supply device DV2 switched off and the switching valve PD3 closed, and the further pressure reduction then takes place, as already described, with the switching valve open PD4 via the control of the pressure supply device DV1 instead of.

As both pressure supply devices DV1 and DV2 by reversing the direction of rotation of the rotary pumps Pa or. Pb multiplexing is the ability to both increase and decrease the pressure MUX at both pressure supply devices DV1 and DV2 even without using the exhaust valves ZAV , AV1 , AV2 possible.

The ABS function via multiplex operation MUX and the pressure supply device DV1 occurs as in WO 2006/111393 A1 described. Via the pressure supply device DV1 then all wheel brake cylinders are multiplexed MUX regulated in print, as it was already at 1 is described. The same applies to the pressure supply device DV2 . The back pressure of the bypass valves BP1 and BP2 acts as a pressure difference between the brake circuits BK1 and BK2 . This can be significantly reduced if both pressure supply devices DV1 and DV2 be switched on, as already described - parallel operation of the two pressure supply devices DV1 and DV2 . Multiplex operation will continue MUX through the parallel operation of the pressure supply facilities DV1 and DV2 relieved. Is in the process of building up pressure Pauf in the brake circuit BK1 at the same time a pressure reduction Pab in the other brake circuit BK2 necessary, this pressure reduction takes place via the opening of the switching valve PD2 with the bypass valve closed at the same time BP2 , and by reversing the direction of rotation of the gear pump Pb . This is the multiplex operation MUX at the pressure supply device DV1 only through two wheel brake cylinders RZ1 and RZ2 in the brake circuit BK1 burdened. For example, pressure cannot build up at the same time Pauf in wheel brake cylinder RZ1 and a depressurization Pab in wheel brake cylinder RZ2 of the brake circuit BK1 respectively.

Extended multiplex functions result from a central outlet valve ZAV . Is when pressure is building up Pauf in the brake circuit BK1 at the same time a pressure reduction Pab in the other brake circuit BK2 If necessary, this pressure reduction can also be achieved by opening the bypass valve BP2 with the bypass valve closed at the same time BP1 and switching valve PD2 , and by opening the central exhaust valve ZAV happen. Alternatively, an outlet valve can also be used AV1 or. AV2 in the respective brake circuit BK1 or. BK2 to reduce pressure Pab to relieve the multiplex operation MUX be used. On the one hand, the outlet valve AV1 or. AV2 either between a switching valve SV and a bypass valve BP1 or. BP2 or between the wheel brake cylinder RZ1 , RZ2 , RZ3 or RZ4 and the associated switching valve SV arranged or connected and on the other hand to the storage container VB connected, so that a direct pressure reduction Pab via the outlet valve AV1 or AV2 towards the storage container VB can be done. This is especially true for instantaneous Depressurization Pab makes sense in the wheel brake cylinders of the front wheels. The central outlet valve ZAV is not required with this alternative.

This is typical for the above-mentioned multiplex operation MUX at e.g. SECTION , the pressure control also with the pressure supply device DV2 , via the volume measurement which is carried out by means of the rotor or gear wheel movement or the rotor angle of the rotary pump Pb , which by means of the rotor angle encoder WGb is measured, is calculated, also taking into account the pressure-volume characteristic of the brake (PV characteristic). Thus, there is also a volume measurement or volume control for the pressure build-up and pressure reduction via the pressure supply device DV2 possible.

Is the maximum pressure of the two pressure supply devices sufficient DV1 and DV2 , of, for example, 120bar in each case, the locking pressure of, for example, 160bar in the wheel brake cylinders RZ1 , RZ2 , RZ3 and RZ4 to achieve, so will the pressure supply facilities DV1 and DV2 connected in series, as with 1b already described. A parallel operation of the pressure supply facilities DV1 and DV2 for multiplex operation MUX , as already described, is then not possible. Pressure build-up and pressure reduction in the wheel brake cylinders RZ1 , RZ2 , RZ3 and RZ4 in multiplex operation MUX can then with the pressure supply device DV2 or with the pressure supply device DV1 or with both pressure supply devices DV1 and DV2 respectively. Is when pressure is building up Pauf in the brake circuit BK1 and at the same time a pressure reduction Pab in the other brake circuit BK2 necessary, this pressure reduction takes place with the bypass valve open BP2 , via the central outlet valve ZAV with the bypass valve closed at the same time BP1 . This is the multiplex operation MUX only through two wheel brake cylinders RZ1 and RZ2 in the brake circuit BK1 burdened, eg it cannot build up pressure at the same time Pauf in wheel brake cylinder RZ1 and a depressurization Pab in wheel brake cylinder RZ2 of the brake circuit BK1 respectively. Alternatively, an outlet valve can also be used AV1 or. AV2 in the respective brake circuit BK1 or. BK2 to reduce pressure Pab to relieve the multiplex operation MUX be used. On the one hand, the outlet valve AV1 or. AV2 either between a switching valve SV and a bypass valve BP1 or. BP2 or between the wheel brake cylinder and the associated switching valve SV arranged or connected, and on the other hand to the storage container VB connected, so that a direct pressure reduction Pab via the outlet valve to the storage container VB can be done. This is particularly important for the immediate pressure reduction Pab makes sense in the wheel brake cylinders of the front wheels. The central outlet valve ZAV is not required with this alternative.

If the pressure supply device fails DV1 can the pressure supply device DV2 the function of the pressure supply device DV1 via the open bypass valves BP1 and BP2 take over, whereby also the multiplex operation MUX , e.g. with ABS operation is possible for all wheel brake cylinders. However, the pressure in the wheel brake cylinder RZ1 , RZ2 , RZ3 and RZ4 then to the maximum pressure of the pressure supply device DV2 , eg 120bar, limited.

1c shows a fourth possible embodiment of a hydraulic system according to the invention, which is also based on the in 1 hydraulic system shown builds. A difference to the hydraulic system according to 1 is that there is only a single pressure supply device DV1 having. The second difference to the hydraulic system according to 1 is that a second electrical connection is missing. The third difference is the design of the single pressure supply device DV1 .

The pressure supply device DV1 consists of two rotary pumps Pa and Pa1 , which together form a two-stage pump, a brushless DC motor Ma , a rotor angle encoder WGa for the DC motor Ma with electrical connection Wea, a winding connection 3a for the DC motor Ma as well as the shunt 4a of the DC motor Ma . Here are the rotary pumps Pa and Pa1 connected in series, ie the output of the rotary pump Pa is with the input of the rotary pump Pa1 hydraulically connected. At least one of the two rotary pumps Pa , Pa1 can be designed as a gear pump. Both rotary pumps Pa are off the axis Aa of the DC motor Ma driven. As with the pressure supply device DV1 in 1 is the rotary pump Pa designed for the blocking pressure, eg 120bar. The rotary pump Pa1 is also designed for blocking pressure. This design of the pressure supply device DV1 it is possible with the switching valve open PD1 , the brake pressure in the brake circuit BK1 , and with the bypass valves open BP1 and BP2 in brake circuit BK2 , except for the total pressure of the two rotary pumps Pa and Pa1 , for example to a maximum of 240bar. To reduce the brake pressure in the brake circuit BK1 , and with the bypass valves open BP1 and BP2 also in brake circuit BK2 , becomes the motor torque of the DC motor Ma reduced by insufficient power supply, thereby reducing the direction of rotation of the rotary pumps Pa and Pa1 is reversed compared to the direction of rotation of the rotary pumps Pa and Pa1 at the pressure increase. Hydraulic medium then flows out of the brake circuits BK1 and BK2 , through the bypass valves BP1 , BP2 , the hydraulic line 1 , the open Switching valve PD1 who have favourited Rotary Pumps Pa1 and Pa and the hydraulic line HL1 back to the storage container VB .

As with 1 is described by the possibility of that with the pressure supply device DV1 the pressure in the brake circuits BK1 and BK2 can be reduced, the well-known multiplex operation MUX possible. The multiplex operation MUX with the pressure supply device DV1 is already at 1 described. There are pressure modulations in the wheel brake cylinders RZ1 , RZ2 , RZ3 and RZ4 for functions like SECTION , ASR , ESP and driver assistance systems possible.

1d shows an alternative embodiment to the in 1c illustrated and explained fourth embodiment, wherein the pressure supply device DV1 two series connections of rotary pumps Pa , Pa1 and Pa ' and Pa1 ' having. All four rotary pumps Pa , Pa1 and Pa ' and Pa1 ' can from a single drive M. be driven and / or gear pumps. However, it is also possible that the series connection Pa and Pa1 and the series connection Pa ' and Pa1 ' are each driven by their own drive (not shown). The output side is the series connection of the rotary pumps Pa , Pa1 via the hydraulic line 1 with the brake circuit BK1 in connection, the switching valve PD1 to separate the rotary pumps from the brake circuit BK1 serves. The series connection of the rotary pumps Pa ' , Pa1 ' is on the output side via the hydraulic line 10 with the brake circuit BK2 in connection, this line also by means of an optional isolating valve PD2 is lockable. The drive or drives M. the rotary pumps can, for example, have redundant phase windings (2x3 phases), so that if one phase winding fails, the drive can at least still be operated with lower power.

1. 1. Die Räder der elektrisch angetriebenen Achse können durch Regeneration elektrisch gebremst werden;
2. 2. Während dem regenerativen Bremsen der Räder an der angetriebenen Achse soll die hydraulische Bremsung dieser Räder auf ein Minimum reduziert werden (Blending), um eine größtmögliche Effizienz der Regeneration zu erzielen, unter Beibehalt der erforderlichen Bremskraft an den Rädern;
3. 3. An der nicht angetriebenen Achse findet keine Regeneration statt. Häufig findet an den Rädern der nicht angetriebenen Achse auch keine Bremskraftverstärkung statt.

2 shows a brake booster which can be used, for example, in Formula E vehicles. Typical for such brake boosters is:

1. 1. The wheels of the electrically driven axle can be braked electrically through regeneration;
2. 2. During the regenerative braking of the wheels on the driven axle, the hydraulic braking of these wheels should be reduced to a minimum (blending) in order to achieve the greatest possible efficiency of the regeneration, while maintaining the required braking force on the wheels;
3. 3. There is no regeneration on the non-driven axle. Often there is also no brake force boost on the wheels of the non-driven axle.

2 shows the brake pedal BP which is operated by the driver. This displaces hydraulic medium from the tandem master brake cylinder THZ instead, which goes directly into the brake circuit BK1 and in the wheel cylinder RZ1 and RZ2 of the non-driven wheels, which are thereby hydraulically braked.

A pressure supply device provides the hydraulic braking force on the driven wheels DV1 which can contain a rotary pump according to the invention, in particular in the form of a piston or gear pump or some other piston displacement mechanism. The output of the pressure supply device DV1 is with the brake circuit BK2 via a hydraulic line 1 connected. In this hydraulic line 1 is a normally closed valve, the feed valve ESV , contain. In the brake circuit BK2 is a normally open isolating valve TV intended. When the driver presses the brake pedal BP actuated, the isolating valve is activated TV closed, the feed valve ESV opened and the pressure supply device DV1 activated to achieve the desired hydraulic braking effect on the driven wheels. The pressure supply device falls DV1 off, the isolating valve remains TV open and the feed valve ESV closed so that by pressing the brake pedal BP by the driver, now also hydraulic medium from the tandem master brake cylinder THZ in the brake circuit BK2 is displaced, which in the wheel cylinder RZ3 and RZ4 of the non-driven wheels, which are thereby hydraulically braked.

By activating the pressure supply device DV1 Depending on the regeneration level, hydraulic medium flows through the hydraulic line 1 and through the open feed valve ESV in the wheel brake cylinder RZ3 and RZ4 , whereby the driven wheels are braked hydraulically. If the driven wheels are not to be braked hydraulically, for example because the regenerative braking is sufficient, then the pressure supply device DV1 not activated or their effect reduced to zero and no hydraulic medium flows into the wheel brake cylinder RZ3 and RZ4 . When the pressure supply device DV1 eg contains a gear pump, then it can be used to increase the pressure in the wheel brake cylinders RZ3 and RZ4 Hydraulic medium through the hydraulic line HL1 from the storage container VB be sucked in.

With high demands on the reliability of the pressure supply device DV1 can be a redundant pressure supply device DV1r are provided. This pressure supply device DV2 is parallel to the pressure supply device DV1 switched. This is the output of the pressure supply device DV2 about the Hydraulic line 2 with the hydraulic line 1 the pressure supply device DV1 connected. Next is the pressure supply device DV2 on the input side via the hydraulic line HL1 with the storage container VB connected so that the pressure supply device DV2 also from the storage container VB Can suck in hydraulic medium.

To further increase the reliability of the hydraulic braking of the driven wheels, the output of the pressure supply device DV1r via a hydraulic line 3 with the wheel brake cylinders RZ3 and RZ4 get connected. In this hydraulic line 3 is a normally closed switching valve in the form of a redundant feed valve ESVr , intended. If the feed valve falls ESV off, you can use the redundant feed valve ESVr the pressure supply facilities DV1 and DV1r via the hydraulic line 3 with the wheel brake cylinders RZ3 and RZ4 get connected.

The brake circuit can also, to further increase the reliability of the hydraulic braking of the driven wheels BK2 with the wheel brake cylinders RZ3 and RZ4 via a hydraulic line 4th get connected. In the hydraulic line 4th is a normally open switching valve, the redundant isolating valve TVr , intended. The isolation valve falls TV off, the brake circuit can BK2 via the redundant isolating valve with the wheel cylinders RZ3 and RZ4 get connected.

This system can also be used to control the first brake circuit BK1 be expanded accordingly.

1. A Hydraulikgehäuse HCU
2. B elektrisches Steuergerät ECU
3. C Hauptzylinder HZ, optional mit Wegsimulator WS, Vorratsbehältnis VB und/oder Pedalsensor PS

The 3 shows a possible embodiment of the packaging or structure according to the invention for the pressure supply unit according to the invention. The following main function blocks must be taken into account:

1. A hydraulic housing HCU
2. B electrical control unit ECU
3. C master cylinder HZ , optionally with path simulator WS , Storage container VB and / or pedal sensor PS

These main function blocks are in DE 10 2015 104 246 A1 and DE 10 2016 105 232 A1 described in detail, and these documents can serve to explain details not described here.

The hydraulic housing A. is an essential component of the pressure supply unit according to the invention, in which at least one - preferably all - rotary pump (s) Pa , Pb, Pb1 of at least one pressure supply device DV1 , DV2 is or are arranged. If motor housing for the rotary pumps Pa , Pb are provided, so these motor housings Ma , Mb of rotary pumps Pa , Pb either in or on the housing A. be arranged.

In the case A. can also make the mechanical and / or electrical connections to the housing B. the electrical control unit ECU to be placed. Furthermore, in the housing A. Solenoid valves, check valves and / or pressure transducers can be arranged, in particular with a connection to the master brake cylinder HZ , the wheel brake cylinders RZ1-RZ4 as well as the pressure supply facilities DV1 , DV2 . Both the solenoid valves and the pressure transducers need a connection to the ECU . The single or tandem master cylinder HZ , THZ with in the case A. be arranged.

The case or the block B. is tight, in particular resting over a large area, on the housing A. arranged or connected to this and contains the components and (plug) contacts of the control electronics, which are on a circuit board PCB are arranged. Likewise, the plugs to the vehicle electrical system are in or on the housing B. arranged or attached.

The control unit ECU can be fully redundant or only partially redundant (hereinafter referred to as partially redundant). For example, a double on-board power supply connection or a second redundant circuit board can be provided.

On the housing A. are the hydraulic connection lines to the brake circuits and wheel brake cylinders RZ1-RZ4 connected. The hydraulic connections for the connecting lines can be on the side or on the front of the housing A. be arranged. It is also possible that the hydraulic connections at an angle, for example 45 ° to the horizontal, on the housing A. are arranged, so that a favorable connection angle results and / or the pressure supply unit is as small and compact as possible.

If the single or tandem master brake cylinder HZ , THZ not in the case A. is arranged, so there is a further housing C. to be provided. In this case C. a possibly existing path simulator can also be used WS and / or pedal sensor PS be included. There is an electrical and / or mechanical interface to the housing B. or the electronic control unit ECU .

Preferably the housings are A. and C. in the direction of the axis A _HZ arranged one behind the other, the housing B. in axial direction A _HZ Next the housing A. is arranged. The axes Aa , From of the engines Ma , Mb are preferably perpendicular to A _HZ aligned.

The filler cap of the storage container VB can in front of the housings A. , B. and C. or laterally and / or above the center thereof.

The 3a shows the view from the front or in the direction of the axis A _HZ . In the case A. are the rotary pumps Pa , Pb arranged. The electric motors Ma , Mb for the rotary pumps Pa , Pb can with their housings on the housing A. adjoin or be attached to this. However, it is also possible that the motors Ma , Mb with in the case A. are arranged. The motor axles Aa and From are preferably aligned parallel to one another. As in 3 shown are the motor axles Aa , From perpendicular to the axis A _HZ of the master cylinder arranged.

The solenoid valves MV , and the electrical and mechanical connections 3a , 3b and 5c towards ECU or to the housing B. are also in the housing A. arranged.

3a also shows the alternative front connection of the hydraulic connections for the wheel brake cylinders RZ1-RZ4 . The position of the inlet connection for the storage container is also important VB in front or in the middle is shown. Overall, the arrangement of the individual components shown represents a compact unit with very small dimensions.

The block C. or the housing C. can be separated from the housings A. and B. For example, they can be arranged directly on the bulkhead of the vehicle with a connection to the pedal interface. The blocks A. and B. can be arranged at a suitable point in the engine compartment or engine compartment, with the axles Aa , From of the engines Ma , Mb no longer perpendicular to the axis of the master brake cylinder HZ , THZ must be arranged.

The 3b shows a perspective view of the pressure supply unit according to FIG 3 and 3a . The case A. is next to the case B. arranged, the housing C. on the front sides A1 , B1 the housing A. and B. is applied. The filler neck VBE for the storage container VB is at the front and above the case A. , B. , C. arranged.

The 4th and 4a show another possible structural embodiment in which the motor axes Aa , From parallel to the axis A _HZ of the master cylinder HZ ; THZ are aligned. The block A. is through a in the direction of the axis A _HZ flat casing formed. The same applies to the case B. . The surface normals of the flat sides of the housing A. and B. are preferably parallel or almost parallel to the axis A _HZ of the master cylinder HZ ; THZ aligned.

The case C. is attached to the housing A. screwed on. Of course, as with 3a described the case C. also spatially separated from A. and B. be arranged in the vehicle, for example on the bulkhead. The ones in the housings A. , B. and C. intended components do not differ from those of the 3 and 3a . The same also applies to the storage container VB .

The dashed line 9 '' shows the outline of a vacuum brake booster and shows the small dimensions of the pressure supply unit according to the invention.

The 4b shows a perspective view of the pressure supply unit according to FIG 4th and 4a . The housing A. , B. and C. are arranged in series one behind the other, with the storage container VB encompasses the housing at the side and Aldes housing on the rear face A. is applied. The filler neck VBE for the storage container VB is at the front and above the case A. , B. , C. arranged, the housing C. under the rear area VB _H of the storage container VB is arranged.

List of reference symbols

1

Hydraulic line

2

Hydraulic line

3a

Motor winding connection from motor Ma

3b

Motor winding connection from motor Mb

4th

Hydraulic line

4a

Shunt from motor Ma

4b

Shunt from motor Mb

5

Hydraulic line

5a

On-board network connection to the on-board network BN

6

Hydraulic line

7th

Hydraulic line

Aa

Axis of the motor Ma

From

Axis of the motor Mb

SECTION

Anti-lock braking system

A _HZ

Axis of the hydraulic housing

ASR

Drive slip control

AV1

first exhaust valve in the brake circuit BK1

AV2

first exhaust valve in the brake circuit BK2

B.

Housing of the control and regulation device ECU

BK1

first brake circuit

BK2

second brake circuit

BN

Electrical system

BN1

first electrical system connection

BN2

second on-board power supply connection

BN2 '

Auxiliary power supply connection

BP1

first bypass valve

BP2

second bypass valve

BP

Brake pedal

DG

Pressure transducer

Dr

throttle

DV1

first pressure supply device

DV1r

redundant pressure supply device

DV2

second pressure supply device

Δφ

Angle of rotation of the rotor of the rotary pump

Δt

Time within which the volume V _should should be promoted

EC

electrically commutated

ECU

Control and regulating device

ESP

Electronic stability Program

ESV

Feed valve, normally closed switching valve

ESVr

redundant feed valve, normally closed switching valve

FV

Switching valve

HL1

first hydraulic line to the storage container VB

HL2

second hydraulic line to the storage container VB

Ko

Master cylinder piston SHZ

KWS

Force-displacement sensor

M.

drive

Ma

DC motor of the pressure supply device DV1

Mb

DC motor of the pressure supply device DV2

MUX

hydraulic multiplex operation

MV

magnetic valve

Pa

Rotary pump of the pressure supply device DV1

Pa1

Rotary pump of the pressure supply device DV1

Pa '

Rotary pump of the pressure supply device DV1

Pa1 '

Rotary pump of the pressure supply device DV1

Pab

Depressurization

Pauf

Pressure build-up

Pb

Rotary pump of the pressure supply device DV2

Pb1

Rotary pump of the pressure supply device DV2

PD1

Switching valve

PD2

Switching valve

PD3

Switching valve

PD4

Switching valve

PS

Pedal travel sensor

PV

Pressure volume

RV1

check valve

RV2

check valve

RV3

check valve

RZ1

first wheel brake cylinder

RZ2

second wheel brake cylinder

RZ3

third wheel brake cylinder

RZ4

fourth wheel brake cylinder

SHZ

Single master cylinder

SV

Switching valve

St.

plug

THZ

Tandem master cylinder

TV

Isolation valve, normally open switching valve

TVr

redundant isolating valve, normally open switching valve

ÜV

Pressure relief valve

V

Volume of hydraulic medium

VB

Storage container

VL

Hydraulic connection line

VLa

Connection line from bypass valve BP1 to bypass valve BP2

v _M

Angular rotation speed of the rotor of the rotary pump

V _should

Required volume of hydraulic mediumWea electrical connection of the angle encoder WGa

Web

electrical connection of the angle encoder WGb

WGa

Angle encoder of the rotor of the motor Ma

WGb

Angle encoder of the rotor of the motor Mb

WS

Path simulator

ZAV

central exhaust valve

ZAVr

redundant exhaust valve

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent literature cited

• DE 102015221228 A1 [0004]
• DE 102016208529 A1 [0005]
• DE 102016211982 A1 [0006]
• WO 0142069 A1 [0007]
• WO 2017/144390 A1 [0008]
• DE 102013227089 A1 [0009]
• DE 102012223497 A1 [0009]
• WO 2012/103925 A1 [0010]
• WO 2012/059175 A1 [0058]
• WO 2006/111393 A1 [0063, 0079]
• DE 102015104246 A1 [0097]
• DE 102016105232 A1 [0097]

Claims (38)

Pressure supply unit for a hydraulic system with at least one consumer circuit (BK1, BK2) and with at least one rotary pump (Pa, Pb), whereby - either by means of at least one rotary pump (Pa, Pb) a volume delivery in at least one delivery direction in at least one consumer circuit (BK1, BK2 ) takes place in such a way that a certain required volume (V eg in [cm ³ ]) of hydraulic medium, in particular for a pressure build-up (Pauf), pressure reduction (Pab) and / or an adjustment of an aggregate is conveyed and / or - that at least two Rotary pumps (Pa, Pb) are provided, with at least one of the rotary pumps (Pa, Pb) being able to build up and reduce the pressure in at least one consumer circuit (BK1, BK2) by means of a corresponding energization of the respective electric motor drive (Ma, Mb). Pressure supply unit according to Claim 1 , characterized in that at least two rotary pumps (Pa, Pb) are designed for different maximum pressure levels (P1 _max , P2 _max ) and / or different pressure ranges (P1 _min ≤ P1 ≤ P1 _max ; P2 _min ≤ P2 ≤ P2 _max ), wherein in particular Plmax ≠ P2 _max . Pressure supply unit according to Claim 1 or 2 , characterized in that the volume is conveyed by means of a volume control, in such a way that the necessary angle of rotation (Δcp) for a required volume (V _soll ) is determined via the proportionality between the angle of rotation (Δφ) of the rotor of the rotary pump and the volume (V) being conveyed Hydraulic medium is calculated and then the rotor is adjusted by the calculated angle of rotation by means of the drive (Ma) of the rotary pump (Pa). Pressure supply unit according to one of the Claims 1 to 3 , characterized in that the volume control takes into account the time (Δt) within which the required volume (V _soll) of hydraulic medium is to be conveyed, the speed (v _M ) of the rotor of the rotary pump (Pa) being equal to the available Time (Δt) is adjusted. Pressure supply unit according to one of the Claims 1 to 4th , characterized in that the pressure supply unit has at least two pressure supply devices (DV1, DV2), one pressure supply device (DV1, DV2) each having at least one rotary pump (Pa, Pb; Pb, Pb1) and a drive (Ma, Mb) for driving the rotary pump having, the pressure supply devices (DV1, DV2) designed for the same or different maximum pressure levels (P1 _max , P2 _max ) and / or the same, overlapping or different pressure ranges (P1 _min ≤ P1 ≤ P1 _max ; P2 _min ≤ P2 ≤ P2 _max ) are. Pressure supply unit according to one of the Claims 1 to 4th , characterized in that the pressure supply unit has only one pressure supply device (DV1), the pressure supply device (DV1) either - at least two hydraulic series-connected rotary pumps (Pa, Pa 1), in particular in the form of a two-stage or multi-stage rotary pump, or - two series circuits of at least two hydraulic series-connected rotary pumps (Pa, Pa1; Pa ', Pa1'), the rotary pumps (Pa, Pa1; Pa ', Pa1') connected in series being driven by a drive (M) will. Pressure supply unit according to one of the preceding claims, characterized in that at least one rotary pump (Pa), in particular the rotary pump for volume control and / or the rotary pump for pressure build-up and reduction, is a rotary pump with piston, a gear pump, a vane pump or a rotary vane pump . Pressure supply unit according to one of the Claims 1 to 7th , characterized in that at least the rotary pump (Pa) for volume control is either - a rotary piston pump, in particular in the form of a rotary piston pump, rotary vane pump, vane pump, rotary piston pump, toothed ring or gear pump, or - is a radial pump, in particular in the form of a radial piston pump, or - is a flow pump, in particular in the form of a centrifugal pump, or - is a positive displacement pump with a rotating rotor which, with a wall surrounding it, forms self-contained volumes in which the hydraulic medium is conveyed by the rotation. Pressure supply unit according to one of the preceding claims, characterized in that the rotary pump (Pa, Pb) is a 1-circuit rotary pump which has only one hydraulic circuit, in particular in the form that it has only one inlet and one outlet and one rotor. Pressure supply unit according to one of the Claims 1 to 8th , characterized in that the rotary pump (Pa, Pb) is a multi-circuit Is a rotary pump that has several separate and sealed hydraulic circuits. Pressure supply unit according to one of the preceding claims, characterized in that the rotary pump (Pa, Pb) has a single-stage or multi-stage design, several stages being arranged hydraulically in series. Pressure supply unit according to Claim 11 , characterized in that the rotary pump (Pb) is a multi-stage pump, a drive (Ma, Mb) driving the multi-stage pump, which has at least two hydraulic series-connected rotary pumps (Pa, Pa1; Pb, Pb1). Pressure supply unit according to one of the preceding claims, characterized in that the rotary pump (Pb) not intended for volume control is a continuously conveying pump, in particular in the form of a piston pump, vane pump, rotary vane pump or gear pump. Pressure supply unit according to Claim 13 , characterized in that the continuously conveying pump (Pb, Pb1) is driven by means of an electric motor drive (Mb) and sets or regulates a predetermined pressure in a consumer circuit (BK2). Pressure supply unit according to one of the preceding claims, characterized in that by means of the at least two rotary pumps (Pa, Pb) at least two consumer circuits (BK1, BK2), in particular in the form of brake circuits, are supplied with hydraulic medium, with at least one consumer (RZ) in each case a consumer circuit (BK1, BK2) is arranged, a rotary pump (DV1, DV2) being assigned to a consumer circuit (BK1, BK2). Pressure supply unit according to Claim 15 , characterized in that the consumer circuits (BK1, BK2) can be connected via a hydraulic connection line (VL, VLa), with at least one switchable valve (BP1, BP2), in particular two switchable bypass valves connected in series, for the optional opening and closing of the connection line (VL) are provided. Pressure supply unit according to one of the preceding claims, characterized in that the minimum pressure (P1 _min ) of the first rotary pump (Pa) is less than or equal to the minimum pressure (P2 _min ) of the second rotary pump (Pb) and the maximum pressure (P1 _max ) of the first rotary pump (DV1) is less than the maximum pressure (P2 _max ) of the second rotary pump (DV2). Pressure supply unit according to one of the preceding claims, characterized in that the electrical power of the drive (Ma) of the rotary pump (Pa) of the first pressure supply device (DV1) is greater than the electrical power of the drive (Mb) of the rotary pump (Pb) of the second pressure supply device ( DV2). Pressure supply unit according to one of the preceding claims, characterized in that the rotary pumps (Pa, Pb) of two pressure supply devices (DV1, DV2) can be hydraulically connected in series via a connecting line (6). Pressure supply unit according to Claim 19 , characterized in that the connecting line (6) can be optionally shut off or opened by means of a switchable, in particular normally closed, valve (PD3). Pressure supply unit according to one of the preceding claims, characterized in that the inlet of the rotary pump (Pa) is connected to a storage container (VB) via a connecting line (7), this connecting line (7) with the connecting line (6) at point (A ), and in the line section (7a) between point (A) and the storage container (VB) a check valve (RV3), in particular with a large flow cross-section, is arranged, which prevents hydraulic medium from flowing from point (A) to the storage container (VB ) can flow. Pressure supply unit according to Claim 21 , characterized in that a switchable, in particular normally closed, valve (PD4) is arranged parallel to the check valve (RV3), such that when the switching valve (PD4) is open, hydraulic medium can flow from the rotary pump (Pa) to the storage container (VB). Pressure supply unit according to one of the preceding claims, characterized in that the hydraulic connection of the output side of a rotary pump (Pa, Pb; Pb1) to the respectively assigned consumer circuit (BK1, BK2) and / or the hydraulic connection of the input side of a rotary pump (Pa, Pb) towards the storage container (VB) can be shut off by means of a switchable, in particular normally closed, valve (PD1, PD2). Pressure supply unit according to one of the preceding claims, characterized in that the current and / or the voltage for the electric motor drive (Ma, Mb) for a required delivery rate and / or delivery direction is set or regulated by means of a converter. Hydraulic system, in particular in the form of a brake system with a pressure supply unit according to one of the preceding claims. Hydraulic system according to Claim 25 , characterized in that the hydraulic system is part of an electric vehicle, only one pressure supply device (DV1) being provided, which in particular only serves to generate brake pressure in a brake circuit (BK2). Hydraulic system according to Claim 26 , characterized in that the hydraulic connection line between the pressure supply device (DV1) and the brake circuit (BK2) can optionally be shut off or opened by means of a switching valve (ESV). Hydraulic system according to Claim 26 or 27 , characterized in that a brake cylinder (THZ) that can be actuated by means of a brake pedal (BP), in particular in the form of a tandem master brake cylinder with floating piston, is provided, with a brake pressure in one or, in particular in the event of failure of the pressure supply device ( DV1), both brake circuits (BK1, BK2) can be built. Hydraulic system according to one of the Claims 26 to 28 , characterized in that a further pressure supply device (DV1r) is arranged parallel to the pressure supply device (DV1), which takes over or supports its function, in particular in the event of failure of the pressure supply device (DV1), and that if both pressure supply devices (DV1, DV1r) fail via the brake cylinder (THZ) a pressure build-up can take place in both brake circuits. Hydraulic system according to one of the Claims 26 to 29 , characterized in that if the pressure supply device (DV1) or pressure supply devices (DV1, DV1r) fail, a switchable, in particular normally open, isolating valve (TV) is opened in such a way that hydraulic medium is removed from the brake cylinder (THZ) via this isolating valve (TV) in the brake circuit (BK2), the pressure builds up. Hydraulic system with a pressure supply unit according to one of the Claims 1 to 24 and / or according to one of the Claims 25 to 30th , characterized in that the at least one rotary pump (Pa, Pb) is or are arranged in a housing (A), in particular their axes being aligned parallel to one another. Hydraulic system according to Claim 31 , characterized in that a master cylinder in the form of a single or tandem master cylinder (SHZ, THZ) is provided which can be actuated by means of a brake pedal (BP), the single or tandem master cylinder (SHZ, THZ) in the housing (A) is arranged together with the rotary pumps (Pa, Pb) or in a housing (C) formed separately therefrom. Hydraulic system according to Claim 31 or 32 , characterized in that the axis of the at least one rotary pump (Pa, Pb) are arranged parallel or perpendicular to the axis of the master brake cylinder (SHZ, THZ). Hydraulic system according to one of the Claims 31 to 33 , characterized in that solenoid valves, in particular the valves required for all control and regulating functions (ESP, ABS), are also arranged in the pump housing (A). Hydraulic system according to one of the Claims 31 to 34 , characterized in that the electronic control and regulating unit (ECU) is arranged in an ECU housing (B), in particular the sensors are arranged in the ECU housing (B) or are arranged on this, and / or the control and control unit (ECU) is partially or fully redundant. Hydraulic system according to one of the Claims 31 , 34 or 35 , characterized in that the hydraulic system has an electric pedal or an actuation switch, in particular for level 5 in automatically driving vehicles (AD). Hydraulic system according to one of the Claims 31 to 36 , characterized in that if the on-board network is not redundant, an auxiliary on-board network, e.g. with U-Caps (BN2 '), is provided for some braking operations, in particular so that braking until the vehicle comes to a standstill is possible if the on-board network fails while driving and thus also when the vehicle is driven. Hydraulic system according to one of the Claims 31 to 37 , characterized in that the housings (A, B, C) together form a module, in particular a 1-box module.

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