Non-man power pressure device provided with cylinder chamber

Abstract

To provide a non-man power pressure device which has a compact and low-cost structure type for pressure generation and has special operation dependability.SOLUTION: In a non-man power pressure device (10) for a hydraulic pressure unit (12) of a vehicle brake system, it comprises a housing (18). The housing includes a motor side (26) on which a motor (16) for driving the non-man power pressure device is arranged, and a control device side (28), which is opposite the motor side and on which a control device is arranged, and comprises a cylinder (46) disposed within the housing. The cylinder comprises a piston (22) which extends from the motor side to the control device side along a cylinder axis (48), and is guided to be movable in an axial direction within the cylinder. In the non-man power pressure device in which a cylinder chamber (80) is demarcated by a piston end face (76) of the piston, the cylinder chamber is a first cylinder chamber, and an additional second cylinder chamber (84) is provided within the cylinder.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] The present invention relates to a non-manual pressure device, in particular a non-manual pressure device for a hydraulic unit of a vehicle brake system, comprising a housing which has a motor side for receiving a motor for driving the non-manual pressure device and a control device side located on the side opposite to the motor side for receiving a control device for controlling the motor, and a cylinder arranged in the housing, the cylinder extending from the motor side to the control device side along the cylinder axis of the cylinder and having a piston which is guided axially movably within the cylinder, and a cylinder chamber is defined by the piston end face of the piston. Further, the present invention relates to the use of such a non-manual pressure device within a hydraulic unit of a vehicle brake system.

Background Art

[0002] Known vehicle brake systems are used in motor vehicles, such as motorcycles, passenger cars or freight vehicles, to provide a controlled brake pressure to the corresponding wheel brakes, thereby enabling slip control. The core piece of such a controllable brake system is a hydraulic unit having hydraulic components conventionally connected to the master brake cylinder. The master brake cylinder can be operated by the driver using a pedal and is used as a source for generating a brake pressure in the wheel brakes connected by brake lines. In order to control the brake pressure, there are provided hydraulic components that can be controlled by a control device, such as solenoid valves, sensors and in most cases a pressure device that can be operated electrically.

[0003] In today's braking systems, especially in brake-by-wire braking systems, the non-manpower pressure device itself that can be operated by an electric motor is used to generate braking pressure for the wheel brakes as a non-manpower source. The braking pressure generated by the non-manpower pressure device is then transmitted to the wheel brakes by a hydraulic or electromechanical actuator. In the case of such a normal brake, the master brake cylinder is disconnected from the wheel brakes and is used to detect the driver's braking request. In the event of a failure of the non-manpower source, the master brake cylinder provides a hydraulic fallback level that can be operated by the driver via the pedal.

[0004] Recent vehicle development has made it possible to drive with an increased degree of automation, which poses new requirements on the braking system. In this case, especially the pressure generation by the non-manpower source must be possible with particularly high reliability and driving certainty so that driver intervention is no longer necessary. SUMMARY OF THE INVENTION

[0005] The object of the present invention is to provide a non-manpower pressure device in which a particularly compact and low-cost structural form is provided for pressure generation and in which the pressure generation has, in particular in addition to this, special driving certainty.

[0006] According to the present invention, a non-manual pressure device, in particular a non-manual pressure device for a vehicle braking system or a hydraulic unit of a braking system, comprises a housing or a hydraulic housing, the housing or the hydraulic housing having a motor side for accommodating a motor for driving the non-manual pressure device and a control device side located on the side opposite to the motor side for accommodating a control device for controlling the motor, and comprises a cylinder disposed in the housing, the cylinder extending from the motor side to the control device side along the cylinder axis of the cylinder and comprising a piston movably guided axially in the cylinder, the piston end face of the piston defining a cylinder chamber. At this time, this cylinder chamber is a first cylinder chamber, and an additional second cylinder chamber is provided in the cylinder. At this time, the second cylinder chamber is configured to be separated from each other such that the pressure medium accommodated in the first cylinder chamber does not come into contact with the pressure medium accommodated in the second cylinder chamber.

[0007] Thereby, the second cylinder chamber according to the present invention between the motor side and the control device side provides a non-manual cylinder having two cylinder chambers separated from each other, particularly with respect to the pressure medium. From each cylinder chamber, a braking pressure can thereby be generated in at least one corresponding wheel brake of the corresponding brake circuit. Thereby, the braking pressure generated by the non-manual pressure device can be introduced into two brake circuits separated from each other. A redundant operating mode is made possible.

[0008] In addition, due to the arrangement of both cylinder chambers between the motor side and the control device side, a particularly compact arrangement within the housing is achieved. At this time, the cylinder axis of the cylinder extends perpendicularly to the motor side or the control device side, whereby the Y-axis or the Y-direction is defined. Along the Y-axis, the housing thickness of the housing extends, and the housing thickness is preferably configured to be relatively slim compared to the housing height extending along the Z-axis or the housing length extending along the X-axis. This preferably slim housing thickness is penetrated by the cylinder with both cylinder chambers of the cylinder. Preferably, the cylinder is extended by a cup-shaped cylinder cover that closes a corresponding cylinder opening provided therein on the control device side, depending on the required volume. For the same purpose, the cylinder is preferably extended by a housing overhang forming portion protruding from the control device side. Particularly preferably, the cylinder is completely accommodated within the housing with the cylinder axis of the cylinder, and when the required volume is larger, the housing is adapted in terms of the housing thickness of the housing, or the cylinder is correspondingly enlarged in terms of the diameter of the cylinder. By enlarging the diameter, for a larger volume, the space required in the X-direction and the Z-direction is less than expanding the length in the Y-direction, and it is compact.

[0009] In contrast, a conventionally conventional master brake cylinder, particularly operable by a pedal, is arranged within the housing parallel to the motor side with the axis of the master brake cylinder, and thus, parallel to the X-axis or along the housing length. Preferably, such a master brake cylinder is not provided within the hydraulic unit corresponding to the non-manual pressure device according to the present invention, saving space and components.

[0010] Rather, advantageously according to the invention, the non-manual pressure device is provided to be used, alone or only, within the hydraulic unit to generate brake pressure for at least one wheel brake of the corresponding brake system. That is, the non-manual pressure device is, advantageously, a single brake pressure generator within the corresponding hydraulic unit and brake system. Thereby, a very compact arrangement within a housing having only a single brake pressure generator is achieved, and the brake pressure generator extends through the housing in the axial direction from the motor side to the control device side. In addition, the corresponding brake system is, in this case, a true brake-by-wire brake system, i.e., a so-called true brake-by-wire brake system. Thereby, a considerable number of components, weight, and costs are saved.

[0011] Advantageously, in the non-manual pressure device according to the invention, the second cylinder chamber is arranged axially rearward of the first cylinder chamber in the pressurizing direction of the piston. Such an axial arrangement of both cylinder chambers can be realized particularly compactly and particularly simply in terms of construction technology. Alternatively, although more laborious in terms of construction technology, an arrangement that is extremely compact in terms of structural form and can be used as required is possible. Preferably, in that case, in particular, a radial arrangement of both cylinder chambers in which one cylinder chamber surrounds the other cylinder chamber in the radial direction, or alternatively, preferably, an arrangement in which both cylinder chambers are located side by side.

[0012] In addition, according to the present invention, advantageously, another piston is arranged to be connected to the piston so as to transmit a force axially rearward of the piston in the pressurizing direction of the piston. Thereby, the piston is a primary piston, and the other piston is a secondary piston that is subordinate to the movement of the primary piston. Preferably, in this case, the other piston is connected to the piston so as to transmit a force by a spring, and the spring is arranged particularly axially between the two pistons and is preferably configured as a coil spring. Further, the other piston is also preferably supported by a cylinder by a return spring configured as a coil spring. Thereby, a piston system and a support system known per se are selected from a conventionally used tandem master brake cylinder, and as a result, costs can be saved and known components can be used.

[0013] Furthermore, according to the present invention, advantageously, the piston is axially movable by a threaded mechanism that can be driven by a motor. Thereby, the rotational movement of the motor shaft belonging to the motor can be mechanically converted into the translational movement of the piston. The reverse conversion is also easily possible. For this purpose, the threaded mechanism has a spindle having a thread and a nut that surrounds the spindle in a hollow cylindrical shape and engages with the thread. The piston can thereby be moved in a very finely adjustable manner. Preferably, the threaded mechanism or the spindle mechanism is configured as a trapezoidal threaded mechanism, saving components, and in the case of a trapezoidal threaded mechanism, the nut directly slides on the trapezoidal thread of the spindle. Particularly preferably, the spindle mechanism is configured as a ball screw mechanism with extremely low friction, and in the case of a ball screw mechanism, balls used as rolling bearings are provided between the spindle and the nut.

[0014] Advantageously, according to the invention, a first delivery line is led out of the first cylinder chamber, and the first delivery line enables a pressure medium to be supplied to the first brake circuit. Further, a second delivery line is led out of the second cylinder chamber, and the second delivery line enables a pressure medium to be supplied to the second brake circuit. In this case, both brake circuits belong to an adjustment device, and by means of the adjustment device, the brake pressure generated by the non-manual pressure device can be adjusted for slip control or for an electronic stability program in at least one wheel brake corresponding to each brake circuit. Thereby, both delivery lines provide a connection of the adjustment device to an actuating device to which the non-manual pressure device advantageously belongs as a single brake pressure generator.

[0015] In addition, advantageously according to the invention, a first supply line leads into the first cylinder chamber, the first supply line being connected to the first reservoir chamber of the reservoir divided into two, and a second supply line leads into the second cylinder chamber, the second supply line being connected to the second reservoir chamber of the reservoir divided into two. In particular, one radial seal element is provided on each side of each supply line in the axial direction along the cylinder axis. In this case, the seal elements are each arranged in one seal groove or in the groove provided in the corresponding cylinder wall, projecting radially from the seal groove into the cylinder and engaging radially so as to surround the piston. By means of this type of sealing, separation of the two cylinder chambers with respect to the pressure medium is achieved. In addition, separated pressure medium supply is achieved by two reservoir chambers which are separated from each other and which are each in communication with a corresponding cylinder chamber for exchanging the pressure medium. Thereby, even in the case where a fault occurs, for example a leak in one of the pressure medium supplies, the brake pressure can always still be formed in the corresponding brake circuit, in at least one corresponding wheel brake therein, by means of the other pressure medium supply. In particular, separation of the brake circuit is achieved in the combination of both delivery lines each leading from a respective cylinder chamber into a respective corresponding brake circuit, and a redundant brake system having two hydraulically separated brake circuits is provided by the separation of the brake circuit.

[0016] Advantageously, the motor is arranged on the motor side of the housing, the control device is arranged on the control device side of the housing, and a channel extending through the housing is arranged from the motor side to the control device side. Through this channel, the electrical connection between the motor and the control device is guided. Thereby, a compact and short control connection through the housing thickness is provided.

[0017] In addition, advantageously according to the invention, a pressure detection device is provided, by means of which the pressure present in the first cylinder chamber and / or the pressure present in the second cylinder chamber can be detected. In this case, the pressure is in particular the pressure of the pressure medium present in each cylinder chamber. By detecting this pressure, in particular pressure monitoring is realized, and by means of the pressure monitoring, it is possible to simultaneously monitor whether the corresponding sealing elements are still sufficiently tight. For this purpose, the pressure detection device is preferably configured to have a pressure sensor, and the pressure sensor is easily installed in the housing and can be directly read out by the electronic system of the control device board. Thereby, in particular, a highly reliable non-manual pressure device is provided.

[0018] In addition, the present invention is also directed to the use of this kind of non-manual pressure device in the hydraulic unit of a vehicle braking system. In the hydraulic unit, advantageously, the braking pressure is generated in at least one corresponding wheel brake only by this kind of non-manual pressure device and a motor for driving the non-manual pressure device. In particular, in this case, the non-manual pressure device belongs to an operating device for generating the braking pressure in at least one corresponding wheel brake.

[0019] Advantageously, the hydraulic unit additionally has an adjusting device for the operating device, and by means of the adjusting device, the generated braking pressure in at least one corresponding wheel brake is adjusted. In this case, the adjusting device has a pump motor for driving at least one pump for adjusting the braking pressure generated by the non-manual pressure device. In this case, the adjusting device is a system known per se of the electronic stability program (ESP system).

[0020] Furthermore, the invention is directed to the use of such a non-manual pressure device for generating hydraulic pressure in a hydraulic unit of a vehicle brake system having a first brake circuit and a second brake circuit, respectively, in at least one corresponding wheel brake. In this case, advantageously, the brake pressure is generated by the non-manual pressure device alone in at least one first wheel brake and / or at least one second wheel brake.

[0021] Correspondingly, the invention is also directed to a hydraulic unit of a vehicle brake system and a vehicle brake system, the hydraulic unit and the vehicle brake system having a non-manual pressure device configured in such a way. In this case, the non-manual pressure device is advantageously used alone or solely for generating the brake pressure, so that as a result, no further pressure generator and in particular no pedal-operable master brake cylinder are provided. This provides a very compact hydraulic unit and in particular a brake system without driver intervention, these hydraulic units and brake systems enabling highly autonomous driving with a high level of safety.

[0022] Overall, in the non-manual pressure device according to the invention, preferably, the primary piston, and advantageously the secondary piston, as well as the advantageous spring and also the advantageous sealing element are configured similar to the technology of a known tandem master brake cylinder. In the best case, the components required for this are taken over from conventional and customary pressure generation concepts. By using known components and the amount of effect achievable thereby, the manufacturing costs can be significantly saved.

[0023] Hereinafter, an embodiment of the solution according to the invention will be described in detail based on the attached schematic drawings.

Brief Description of the Drawings

[0024]

Figure 1

Figure 2

Embodiments for Carrying Out the Invention

[0025] FIG. 1 shows the non-human power pressure device 10 or the pressure device 10 of the hydraulic unit 12 shown in an extract of the electro-hydraulic vehicle brake system 14 or the brake system 14 schematically shown in FIG. 2. The brake system 14 is provided for a vehicle brake device of a four-wheel vehicle (not shown). With this brake system, the functions of an anti-lock system (ABS), an electronic stability program (ESP) and / or a traction control (ASR) can be fulfilled.

[0026] The pressure device 10 is configured as a plunger device that can be driven by a motor 16 configured as an electric motor. The motor 16 is known per se and is shown only highly schematically. The motor 16 forms the non-human power drive part of the brake system, and this brake system is thereby part of a non-human power vehicle brake device. At that time, the motor 16 belongs to the pressure device 10, and this pressure device 10 is thereby used as a brake pressure generator that generates brake pressure. Thereby, the pressure device 10 is an external pressure source provided in the brake system 14, and this brake system 14 is configured here as a true brake by wire brake system. At that time, the energy required for the brake pressure is provided only by a corresponding external energy source.

[0027] Structurally, in addition to this, the hydraulic unit 12 has a hydraulic housing 18 or housing 18, which is only partially shown, and the hydraulic housing 18 or housing 18 is configured as a hydraulic block. Inside the housing 18, a channel 20 is arranged, and the channel 20 is configured as a stepped hole. The channel 20 forms a non-manpower cylinder accommodating portion, and inside the non-manpower cylinder accommodating portion, a piston 22 used as a non-manpower piston is accommodated, and the piston 22 is configured as a plunger or a plunger piston. Further, the channel 20 extends axially perpendicular to the motor side 26, which is used on one side of the housing, and extends to the housing side used as the control device side 28, which is located on the opposite side, with a channel axis 24 that coincides with the piston axis of the channel 20. The channel axis 24 defines the Y-axis of the virtual Cartesian coordinate system, and along the Y-axis, between the motor side 26 and the control device side 28, the housing 18 extends with the housing thickness 29 of the housing 18. At this time, the motor 16 is arranged on the motor side 26 with the motor housing 30 of the motor 16, and the electronic control device 32 is arranged on the control device side 28. Parallel to the channel axis 24, another channel 34 is provided that completely penetrates from the motor side 26 to the control device side 28, and this another channel 34 has a diameter that is significantly smaller than that of the channel 20 when viewed in cross-section. Through this another channel 34, an electrical connection 36 is guided, and through the electrical connection 36, the control device 32 and the motor 16 are connected so as to transmit signals to each other.

[0028] Channel 20 is configured to be open at a first end 38 of channel 20 facing the motor 16, and reaches up to the control device side 28 leaving a gap 42 at a second end 40 of channel 20 facing the control device 32. Thereby, the gap 42 provides a cylinder bottom 44 of a cylinder 46 formed by the channel 20, and the cylinder 46 has a cylinder axis 48 that coincides with the channel axis 24. Here, the cylinder 46 is completely formed by the channel 20. Alternatively, the cylinder 46 is formed by the channel 20 and a cup-shaped cylinder cover that extends coaxially with the channel 20, or a housing overhang molding that extends coaxially with the channel 20 (not shown respectively).

[0029] The piston 22 is configured in a cup shape and has a circular cross section as a first piston or a primary piston, and is axially reciprocally movable by the motor 16 by means of a screw mechanism 50. When the piston 22 moves so as to enter the cylinder 46, in this case, pressure is generated in the cylinder 46 along the pressurizing direction 52. Another piston 56 is arranged to be connected to the piston 22 so as to transmit force by a spring 54 arranged coaxially behind the piston 22 in the pressurizing direction 52 of the piston 22, and this another piston 56 is correspondingly moved together with the first piston 22. This another piston 56 is supported by the cylinder bottom 44 by a return spring 58 arranged coaxially as a second piston or a secondary piston.

[0030] In addition, a spindle 60 is accommodated inside a cup-shaped first piston 22, and the spindle 60 is surrounded by a hollow cylindrical thin-walled nut 62. The nut 62 is engaged in a form-fitting manner with a spindle thread 64 formed on the spindle 60 from the outside. Further, the nut 62 is surrounded by a rotary bearing 66 on the end face side facing the motor 16, and the rotary bearing 66 is held in a fixed position by a cup-shaped bearing cover 68 that is fixedly connected to the housing 18 from the outside. The nut 62, which is rotatably supported by the rotary bearing 66, is rotatable by the motor 16, and thus this rotational movement causes the spindle 60, and hence the piston 22, to move in the cylinder 46 via the spindle thread 64. For this purpose, the spindle 60 is driven here by a transmission mechanism 70 configured as a planetary transmission mechanism, and the transmission mechanism 70 is connected to a motor shaft 72 belonging to the motor 16 so as to transmit force. The motor shaft 72, the transmission mechanism 70, the spindle 60 and the nut 62 belong to one actuator 74 together with the motor 16, and by means of the actuator 74, the piston 22 can be selectively reciprocated in the cylinder 46 depending on the rotational direction of the motor 16.

[0031] In addition, the piston 22 has a piston end face 76 at an end of the piston 22 located on the side opposite to the actuator 74. The piston end face 76, together with the housing 18 surrounding the channel 20 and the piston end face 78 of the second piston 56 facing the piston 22, defines a first cylinder chamber 80. At this time, the second piston 56 is configured in a double T-shape when viewed in a longitudinal sectional view of the second piston 56. Specifically, the piston end face 78 of the second piston 56 is configured in a cup shape and is open toward the first piston 22. Inside this cup shape, a spring 54, which is configured as a coil spring here, is partially axially accommodated with the outer periphery of the spring 54 and is supported axially and radially there. On the side opposite to the piston end face 78, another cup-shaped piston end face 82 exists on the second piston 56, and this another cup-shaped piston end face 82 is configured to be open toward the cylinder bottom 44. Correspondingly, there, a return spring 58, which is also configured as a coil spring, is partially axially accommodated with the outer periphery of the return spring 58 inside the cup shape and is supported axially and radially. The cylinder bottom 44, the housing 18 surrounding the channel 20 and the like, and the piston end face 82 define a second cylinder chamber 84, and the second cylinder chamber 84 is arranged axially rearward of the first cylinder chamber 80 in the pressurization direction 52. Thereby, both cylinder chambers 80 and 84 are configured to be axially movable according to the positions of the corresponding two pistons 22 and 56 and to be changeable with respect to the axial extension dimensions of both cylinder chambers 80 and 84.

[0032] The first cylinder chamber 80 is connected by a first supply line 86 to a first reservoir chamber 88 so as to conduct fluid or a pressure medium. The first reservoir chamber 88 belongs to a reservoir 90, which stores and is used to compensate for a pressure medium or brake fluid as a pressure medium storage container. With respect to the pressure medium, a second reservoir chamber 92 is provided in the reservoir 90, separated from the first reservoir chamber 88. The second reservoir chamber 92 is connected by a second supply line 94 to a second cylinder chamber 84 so as to conduct fluid. Preferably, for this purpose, both supply lines 86 and 94 each penetrate into a relatively small groove 96 arranged in the channel 20.

[0033] On both sides of the first supply line 86 in the axial direction, and arranged in the channel 20, one ring-shaped sealing element 100 that surrounds in the radial direction is arranged in each of one groove 98 that surrounds in the radial direction. Each sealing element 100 projects from the groove 98 into the channel 20 in the radial direction at this time and surrounds the first piston 22 so as to act as a radial seal. Similarly, on both sides of the second supply line 94 in the axial direction, one ring-shaped sealing element 104 that surrounds in the radial direction is arranged in each of one groove 102 that surrounds in the radial direction. The sealing element 104 surrounds the second piston 56 so as to act as a radial seal accordingly. Thereby, the corresponding two cylinder chambers 80, 84 are each sealed from each other and are thus configured to be separated from each other with respect to the pressure medium. A pressure detection device 106 is provided to monitor the sealing performance of the sealing elements 100, 104. The pressure detection device 106 is connected to the first cylinder chamber 80. The pressure detection device 106 is configured as a pressure sensor and is connected so as to transmit a signal to the control device 32.

[0034] Furthermore, from the first cylinder chamber 80, in the vicinity of the second piston 56 in the pressurizing direction 52, a first delivery pipeline 108, which is only shown here in a highly schematic manner, is led out. By means of the first delivery pipeline 108, pressure medium can be supplied from the first cylinder chamber 80 to the first brake circuit 110 of the brake system 14. Correspondingly, from the second cylinder chamber 84, in the vicinity of the cylinder bottom 44, a second delivery pipeline 112 is led out, and by means of the second delivery pipeline 112, pressure medium can be supplied to the second brake circuit 114 of the brake system 14.

[0035] During operation, when the first piston 22 and the second piston 56 connected to the first piston 22 withdraw from the cylinder 46, fluid is sucked into both cylinder chambers 80, 84 through the feed pipelines 86, 94 used as suction pipelines. At this time, the cylinder chambers 80, 84 are used as suction chambers. When the first piston 22 and the second piston 56 connected to the first piston 22 enter the cylinder 46, the sucked fluid is pressurized. At this time, the cylinder chambers 80, 84 are used as pressure chambers, and the pressure chambers can generate pressure for the brake system 14. From the cylinder chambers 80, 84, the fluid is pushed out through the delivery pipelines 108, 112 into the corresponding brake circuits 110, 114 respectively to generate brake pressure in the corresponding wheel brakes 116. Thereby, the pressure device 10 forms an operating device 118 as the source for generating brake pressure.

[0036] FIG. 2 shows that in the corresponding brake system 14, the pressure device 10 is a single brake pressure generator in the operating device 118. To adjust the generated brake pressure, an ESP system is connected to the operating device 118 as an adjusting device 120.

[0037] Specifically, for this purpose, the first delivery pipeline 108 is connected to the first supply pipeline 122 to conduct fluid, or corresponds to the first supply pipeline 122 of the first brake circuit 110. Further, a first control valve 124 or a plunger control valve is arranged in the first supply pipeline 122. The first control valve 124 or the plunger control valve is configured as a normally open two-port two-position directional control solenoid valve and can be closed by applying current when necessary. The first supply pipeline 122 leads to two corresponding wheel brakes 116 arranged in a parallel circuit through the paths of branched pipelines, one through each of the two first inlet valves 126. At this time, both wheel brakes 116 of the first brake circuit 110 are connected to the suction side of the first pump 132 by means of a common first return pipeline 130 through one corresponding first outlet valve 128 each. At this time, it should be understood that the concept of a pipeline includes, in some cases, the paths of branched or recombined pipelines.

[0038] Correspondingly, in the second brake circuit 114, the second delivery pipeline 112 is connected to the second supply pipeline 134 to conduct fluid, and a normally open second control valve 136 is arranged in the second supply pipeline 134. The second supply pipeline 134 leads to two second inlet valves 138, and one wheel brake 116 is connected to each of the second inlet valves 138. Both wheel brakes 116 of the second brake circuit 114 are connected to the suction side of the second pump 144 by means of a common second return pipeline 142 through one corresponding second outlet valve 140 each. Further, a pump motor 146 is provided between both brake circuits 110 and 114, and both pumps 132 and 144 can be driven by the pump motor 146. By means of the pumps 132, 144 and the pump motor 146, and by the corresponding switching of the inlet valves 126, 138 and the outlet valves 128, 140, which are known per se, the brake pressure generated by the pressure device 10 in the wheel brake 116 can be adjusted as required.

[0039] Thus, the non-manual pressure device 10 according to the present invention for a brake-by-wire braking system provides an optimized brake pressure generator that is combined with a known standard regulating device 120 (ESP system) by means of both hydraulic delivery pipelines 108, 112, and thus forms a redundant braking system 14. In particular, this enables a structure that is optimized in terms of cost, especially by utilizing components that already exist in large-scale production, such as the motor 16, pistons 22 and 56, spring 54, return spring 58, and seal elements 100, 104. Additionally, the concept of arranging the motor 16 on one side of the housing 18 and the control device 32 on the control device side 28 located on the opposite side enables assembly on a unified ESP assembly line. This significantly reduces production costs as no special investment is required.

Explanation of Reference Numerals

[0040] 10 Non-manual pressure device, pressure device 12 Hydraulic unit 14 Vehicle braking system, braking system 16 Motor 18 Hydraulic housing, housing 20 Channel 22 Piston 24 Channel axis 26 Motor side 28 Control device side 29 Housing thickness 30 Motor housing 32 Control device 34 Another channel 36 Electrical connection 38 First end 40 Second end 42 Spacing 44 Cylinder bottom 46 Cylinder 48 Cylinder axis 50 Thread mechanism 52 Pressing direction 54 Spring 56 Another piston, the second piston 58 Return spring 60 Spindle 62 Nut 64 Spindle thread 66 Rotary bearing 68 Bearing cover 70 Transmission mechanism 72 Motor shaft 74 Actuator 76 Piston end face 78 Piston end face 80 First cylinder chamber 82 Piston end face 84 Second cylinder chamber 86 First supply pipeline 88 First reservoir chamber 90 Reservoir 92 Second reservoir chamber 94 Second supply pipeline 96 Groove 98 Groove 100 Seal element 102 Groove 104 Seal element 106 Pressure detection device 108 First delivery pipeline 110 First brake circuit 112 Second delivery pipeline 114 Second brake circuit 116 Wheel brake 118 Actuating device 120 Adjusting device 122 First supply pipeline 124 First control valve 126 First inlet valve 128 First outlet valve 130 First return pipeline 132 First pump 134 Second supply pipeline 136 Second control valve 138 Second inlet valve 140 Second outlet valve 142 Second return pipeline 144 Second pump 146 Pump motor

Claims

1. A non-manual pressure device (10), in particular a non-manual pressure device (10) for a hydraulic unit (12) of a vehicle brake system (14), comprising a housing (18), the housing (18) having a motor side (26) for receiving a motor (16) for driving the non-manual pressure device (10) and a control device side (28) located on the side opposite to the motor side (26) for receiving a control device (32) for controlling the motor (16), a cylinder (46) disposed within the housing (18), the cylinder (46) extending from the motor side (26) to the control device side (28) along a cylinder axis (48) of the cylinder (46), and a piston (22) movably guided axially within the cylinder (46), a cylinder chamber (80) being defined by a piston end face (76) of the piston (22). In the non-manual pressure device (10), the cylinder chamber (80) is a first cylinder chamber (80), and an additional second cylinder chamber (84) is provided within the cylinder (46). A non-manual pressure device, characterized in that.

2. The non-manual pressure device (10) is provided so as to be used alone within the hydraulic unit (12) to generate a braking pressure for at least one wheel brake (116) of the corresponding vehicle brake system (14). The non-manual pressure device according to claim 1, characterized in that.

3. The non-manual pressure device according to claim 1 or 2, characterized in that the second cylinder chamber (84) is disposed axially rearward of the first cylinder chamber (80) in the pressurizing direction (52) of the piston (22).

4. The non-manual pressure device according to any one of claims 1 to 3, characterized in that another piston (56) connected to the piston (22) for transmitting a force is disposed axially rearward of the piston (22) in the pressurizing direction (52) of the piston (22). The other piston (56) is connected to the piston (22) by a spring (54) for transmitting a force, characterized in that.

5. The non-manual pressure device according to any one of claims 1 to 4, wherein the piston (22) is axially movable by a threaded mechanism (50) drivable by the motor (16).

6. The first delivery pipeline (108) is led out from the first cylinder chamber (80), and the pressure medium can be supplied to the first brake circuit (110) through the first delivery pipeline (108), and the second delivery pipeline (112) is led out from the second cylinder chamber (84), and the pressure medium can be supplied to the second brake circuit (114) through the second delivery pipeline (112). The non-manual pressure device according to any one of claims 1 to 5, characterized in that.

7. A first supply pipeline (86) communicates with the first cylinder chamber (80), the first supply pipeline (86) is connected to the first reservoir chamber (88) of the reservoir (90) divided into two, and a second supply pipeline (94) communicates with the second cylinder chamber (84), the second supply pipeline (94) is connected to the second reservoir chamber (92) of the reservoir (90) divided into two, and in particular, one radial seal element (100, 104) is provided on each side of each supply pipeline (86, 94) axially along the cylinder axis (48). The non-manual pressure device according to any one of claims 1 to 6, characterized in that.

8. The non-manual pressure device according to any one of claims 1 to 7, characterized in that it is provided with a pressure detection device (106), and the pressure detection device (106) can detect the pressure existing in the first cylinder chamber (80) and / or the pressure existing in the second cylinder chamber (84).

9. Use of the non-manual pressure device (10) according to any one of claims 1 to 8 for generating hydraulic pressure in at least one corresponding wheel brake (116) in the hydraulic unit (12) of a vehicle brake system (14) having a first brake circuit (110) and a second brake circuit (114), The first brake circuit (110) has a first supply pipeline (122), and at least one first wheel brake (116) can be connected to the first supply pipeline (122), and The second brake circuit (114) has a second supply line (134), and at least one second wheel brake (116) can be connected to the second supply line (134). Furthermore it comprises an electrically controllable non-manual pressure device (10), the non-manual pressure device (10) being configured to have a housing (18), the housing (18) having a motor side (26) on which a motor (16) for driving the non-manual pressure device (10) is arranged, and a control device side (28) located on the side opposite to the motor side (26) on which a control device (32) for controlling the motor (16) is arranged, the non-manual pressure device (10) being configured to have a cylinder (46) arranged in the housing (18), the cylinder (46) extending from the motor side (26) to the control device side (28) along a cylinder axis (48) of the cylinder (46), and the non-manual pressure device (10) being configured to have a piston (22) guided axially movably within the cylinder (46), a cylinder chamber (80) filled with a pressure medium being defined by a piston end face (76) of the piston (22). In use the cylinder chamber (80) is a first cylinder chamber (80) filled with a pressure medium, and an additional second cylinder chamber (84) filled with a pressure medium is provided within the cylinder (46), the first cylinder chamber (80) being connectable to selectively conduct the pressure medium to the first supply line (122), and the second cylinder chamber (84) being connectable to selectively conduct the pressure medium to the second supply line (134). Use of a non-manual pressure device for generating hydraulic pressure in at least one corresponding wheel brake respectively in a hydraulic unit of a vehicle brake system having a first brake circuit and a second brake circuit, characterized in that. **Claim 10** Use of the non-manual pressure device according to claim 9, characterized in that brake pressure is generated in at least one of the first wheel brakes (116) and / or at least one of the second wheel brakes (116) only by the non-manual pressure device (10).

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