Hydraulic housing for hydraulic external vehicle brake system having simulator receptacle

Abstract

The invention relates to a hydraulic housing for a hydraulic external vehicle brake system, in which a master brake cylinder receptacle, a reservoir connection receptacle connected to the master brake cylinder receptacle, and a simulator receptacle for receiving a pedal feeling simulator configured with a simulator piston are arranged, the simulator piston is guided in the simulator receiving part in an axially movable manner, the simulator piston is axially provided with a front side and a rear side, a pipeline connected with the main brake cylinder receiving part is guided into the simulator receiving part, and the pipeline is arranged in the axial direction of the simulator receiving part, so that in the received state of the simulator piston, the pipeline is connected with the main brake cylinder receiving part. A line is located on the front side of the simulator piston, the return line further leads into the simulator receptacle, and the return line is arranged in the axial direction of the simulator receptacle in such a way that, in the state in which the simulator piston is received, the return line returns to the simulator receptacle; a return line is located on the rear side of the simulator piston and the simulator receptacle is connected to the master brake cylinder receptacle by means of the return line.

Description

Technical Field

[0001] The present invention relates to a hydraulic housing for a hydraulic external-force vehicle brake device, in which a master brake cylinder receiving portion, a reservoir connector receiving portion connected to the master brake cylinder receiving portion, and a simulator receiving portion for receiving a pedal feel simulator are arranged. The present invention also relates to the use of the hydraulic housing in a hydraulic unit of a hydraulic vehicle brake device. Background Art

[0002] A hydraulic vehicle brake system for a motor vehicle having a master brake cylinder is known, which operates in an electronically regulated brake system. In this case, during normal operation of the brake system, a brake pressure is generated on the associated wheel brakes by means of a pressure medium from an electrically controllable pressure build-up device. During this period, the master brake cylinder is decoupled from the wheel brakes. During this decoupling, the hydraulic connection between the pedal operated by the driver and the wheel brakes, which is basically present, is disconnected. The hydraulic connection can be reestablished by means of a corresponding switching of the associated valve, so that the brake system can be operated with the pressure medium of the master brake cylinder when necessary. Thus, a hydraulic return level is achieved, in which the master brake cylinder can be operated by the driver as an emergency brake pressure generator by operating the pedal in the event of a fault. In the fault-free state of the brake system, when the pedal is operated, the driver's braking desire is detected by a sensor and transmitted to the electrically controllable pressure build-up device by means of a control device. Here, when the pedal is operated, the pedal feel perceived by the driver is only generated by means of a pedal feel simulator.

[0003] Here, the pedal feel simulator, the master brake cylinder, the electrically controllable pressure build-up device and the associated valves are received as hydraulic components in the hydraulic housing of the hydraulic unit and are fluidically connected therein via corresponding lines. For this purpose, the hydraulic housing is usually designed as a hydraulic block in a rectangular and block-like manner, in which various holes are provided. These holes serve as pipes and receptacles for the hydraulic components. Here, for their production, these holes are usually milled into the hydraulic block using a cutting method.

[0004] There is a need to optimize hydraulic housings with regard to their receptacles and lines and to save costs during production. Summary of the invention

[0005] According to the present invention, a hydraulic housing for a hydraulic external-force vehicle brake system is realized, in which a master brake cylinder receiving part, a reservoir connector receiving part connected to the master brake cylinder receiving part for connecting a reservoir for brake fluid, and a simulator receiving part for receiving a pedal feeling simulator or a simulator are arranged, wherein the simulator is configured with a simulator piston that can be movably guided in the simulator receiving part, and the simulator piston has a front side and a rear side in the axial direction, wherein a pipeline connected to the master brake cylinder receiving part is guided into the simulator receiving part, and the pipeline is arranged in the axial direction of the simulator receiving part so that the pipeline is located on the front side of the simulator piston when the simulator piston is received. Here, a return pipeline is also guided into the simulator receiving part, and the return pipeline is arranged in the axial direction of the simulator receiving part so that the return pipeline is located on the rear side of the simulator piston when the simulator piston is received, and the simulator receiving part is also connected to the master brake cylinder receiving part by means of the return pipeline.

[0006] By means of the connection according to the invention of the return line to the master brake cylinder receptacle, at least the simulator receptacle, the return line and the master brake cylinder receptacle can be arranged particularly compactly in the hydraulic housing. Otherwise, the return line conventionally usually leads from the simulator receptacle to the reservoir connection receptacle in such a way that the master brake cylinder receptacle is bypassed. This requires more installation space than the hydraulic housing according to the invention.

[0007] Furthermore, during operation of the associated vehicle brake system with the return line according to the invention to the master brake cylinder receptacle, a return flow of the pressure medium present in the simulator receptacle from the simulator receptacle can be achieved in a functionally simple manner and without significant hydraulic resistance. In particular, compared to conventional return lines, which are usually of completely tubular configuration and connect the simulator receptacle to the reservoir connection receptacle, a relatively large volume is provided according to the invention with the aid of the master brake cylinder receptacle, into which the pressure medium can flow out of the simulator receptacle. Thus, according to the invention, a return flow with significantly less hydraulic resistance is achieved.

[0008] In particular, in the assembled state, the master brake cylinder is received in the master brake cylinder receptacle, in which the piston is guided movably. Both the line and the return line are then connected to the master brake cylinder in a fluid-conducting manner. The master brake cylinder is advantageously connected in a fluid-conducting manner to a reservoir connected to the reservoir connection receptacle, which reservoir is used to supplementally store brake fluid as pressure medium.

[0009] The simulator receiving part or in particular the associated simulator cylinder and the simulator received therein in the assembled state are supplied with brake fluid by means of brake fluid received in a reservoir. The supply is carried out at two locations, namely through a line on the front side of the received simulator piston and through a return line on the rear side of the simulator piston. The simulator is therefore supplied with brake fluid on both sides of the simulator piston and is therefore configured as a wet-wet simulator. This configuration brings advantages in terms of lubrication of the simulator piston and advantageous coupling to the spring element on the simulator piston on the rear side. In addition, an additional damping effect for the spring element is achieved in the simulator cylinder by means of the brake fluid leading to the rear side of the simulator piston.

[0010] Preferably, the master brake cylinder is configured as a dual-circuit master brake cylinder or a tandem master brake cylinder with two chambers. For this purpose, a first chamber and a second chamber arranged axially downstream of the first chamber in the actuation direction or pressure direction are provided. In the first chamber, a first piston is guided axially movably as a master piston, which is coupled to a second piston as a floating piston or slave piston in a force-transmitting manner by means of a spring preferably arranged in the first chamber. The slave piston is supported on the cylinder bottom of the master brake cylinder there by means of a reset element in the second chamber. In addition, the pipeline is preferably guided into the first chamber, and the return pipeline is guided into the second chamber.

[0011] Furthermore, the reservoir is preferably configured with at least two reservoir chambers, which are configured to be open upward in the installed position. The first reservoir chamber is advantageously connected to the first chamber by means of a first reservoir line which is fluidically connected to the first reservoir connection receptacle. Furthermore, the second reservoir chamber is fluidically connected to a second reservoir line by means of the above-mentioned reservoir connection receptacle which forms the second reservoir connection receptacle, which is connected to the second reservoir chamber. Therefore, the second reservoir chamber is connected to the simulator receptacle or the simulator by means of the second chamber of the master brake cylinder via a return line which leads to the simulator piston at the rear.

[0012] Furthermore, preferably, a first supply line leads from the first chamber to the first brake circuit, and a second supply line leads from the second chamber to the second brake circuit. In particular, the first supply line corresponds to a line that leads into the simulator receptacle on the front side of the simulator piston to be received, in order to save installation space. By means of a branch, this line is led into the first brake circuit as a first supply line.

[0013] Advantageously according to the invention, the return line leads from the simulator receiver through the master brake cylinder receiver to the reservoir connection receiver. This results in a very compact construction, in which the master brake cylinder receiver is passed through by the return line. The return line also corresponds to the reservoir line that connects the reservoir to the master brake cylinder receiver, saving installation space. For this purpose, the master brake cylinder receiver is particularly configured as a hollow cylinder, in whose cross section not only the return line but also the reservoir line is preferably led completely oppositely to or out of the hollow cylinder as the only return line. Therefore, the return line can be manufactured particularly simply by means of a hole passing through the master brake cylinder receiver. Here, the hole particularly passes through the master brake cylinder receiver in the center and extends perpendicularly to its axis. This results in a particularly uniform distribution of the fluid through the master brake cylinder receiver or the associated master brake cylinder.

[0014] Furthermore, according to the invention, advantageously, the master brake cylinder receptacle is configured as a hollow cylinder, on the cylinder wall of which a radially circumferential groove is provided, which groove is part of the return line. Here, the groove is connected to the return line at two locations. The two locations are preferably arranged opposite each other. Thus, a first line section of the return line leads from the simulator receptacle to the groove, and a second line section of the return line leads from the groove to the reservoir connector receptacle. Thus, the second line section corresponds to the reservoir line. Preferably, the groove is configured to at least partially surround and particularly preferably completely surround the hollow cylinder. Furthermore, in the assembled state, radially circumferential sealing elements are respectively provided on both sides of the circumferential groove, in particular axially. Thus, a piston seal in the master brake cylinder, in particular for a floating piston, is realized at the input end of the return line.

[0015] Furthermore, according to the invention, a valve receptacle is advantageously provided which is connected to the return line. In a particularly compact manner, the valve receptacle is connected to a radially circumferential groove of a master brake cylinder valve receptacle as part of the return line. In this case, the valve receptacle is particularly preferably connected directly to the return line, preferably directly to the groove.

[0016] "Directly" here means that no line sections are required or that very short line sections are used. In addition to the compact design, line losses during operation are thus greatly minimized. Furthermore, in the assembled state, depending on the type of valve received in the valve receptacle, the return line is used compactly and in a component-saving manner for the further outflow, inflow and return flow of the brake fluid.

[0017] Advantageously, according to the invention, the valve receiving part is additionally connected to an external cylinder receiving part for receiving an external brake pressure generator or an electrically controllable pressure build-up device. Here, the valve receiving part serves as a receiving part for a valve, by means of which the external brake pressure generator can be selectively connected to the pedal feel simulator. Such a valve is preferably a solenoid valve that is closed without current and can be opened by means of an electronic controller when power is supplied.

[0018] Advantageously or alternatively, the valve receiving part is additionally connected to a wheel brake cylinder connection receiving part for connecting a wheel brake cylinder. The valve receiving part serves here as an outlet valve receiving part for receiving an outlet valve, which is preferably a solenoid valve closed without current. The brake pressure can be released from the associated wheel brake by means of a corresponding switching of the outlet valve for regulating the brake pressure, for example within the scope of slip control. In particular, the valve receiving part is here provided as an outlet valve for a second brake circuit, in particular for an outlet valve connected to a second chamber. Preferably, a further outlet valve of the second brake circuit is connected only to the second reservoir chamber and bypasses the master brake cylinder.

[0019] Furthermore, advantageously according to the invention, the return line has a first line section which leads from the simulator receptacle to the master brake cylinder receptacle and is configured with an inclined section and a first longitudinal section. Here, the inclined section extends with its longitudinal axis obliquely to the receiving axis of the simulator receptacle and leads from the simulator receptacle to the first longitudinal section, which extends with its longitudinal axis perpendicular to the receiving axis. Thus, the inclined section is used for the rear-side connection of the simulator. Such an inclined section can be manufactured particularly simply during the manufacturing process by means of inclined drilling. In particular, for this purpose, the simulator receptacle is first drilled into the hydraulic block as a cup-shaped groove. The hydraulic block is then rotated and an inclined groove drilling is performed on the cylinder wall surrounding the groove, by means of which the inclined groove drilling forms the inclined section. Here, the inclined section is arranged in such a way that the operating area of ​​the simulator piston is not damaged during operation. Preferably, the inclined section has a confluence into the simulator receptacle arranged in the fourth quadrant in a cross section of the simulator receptacle viewed in the direction of the cup bottom belonging to the simulator receptacle. Preferably, the simulator receiver is arranged with its receiving axis parallel to and perpendicular to the controller side of the hydraulic housing and extends into the controller side. The controller side is the wide side on which the electronic controller is arranged. In addition, preferably, the external force cylinder receiver is arranged perpendicular to the controller side and therefore parallel to the simulator receiver, which is configured to extend through the hydraulic block to the opposite motor side of the hydraulic housing. Here, viewed in the direction of the controller side, the simulator receiver is positioned laterally with an oblique offset to the external force cylinder receiver, so that the confluence of the inclined section is located on one side of the external force cylinder receiver. Starting from the confluence, the inclined section extends with its longitudinal axis oblique to the receiving axis of the simulator receiver toward the motor side and the master cylinder receiver until the inclined section transitions into the first longitudinal section. The first longitudinal section preferably extends parallel to the controller side and thus parallel to the motor side, and merges into the master brake cylinder receiver perpendicular to the receiving axis of the master brake cylinder receiver.

[0020] Advantageously according to the present invention, the simulator receiving part is also configured as a hollow cylinder, on the cylinder wall of which a radially circumferential groove is arranged, so that in the received state of the simulator piston, the groove is located on the rear side of the simulator piston and the inclined section is introduced into the groove. Here, the groove is particularly configured to receive a stop element, by means of which the travel of the simulator piston axially away from the simulator receiving part or the simulator cylinder can be limited. To this end, the stop element is arranged in the groove in the assembled state and at the same time radially extends into the simulator receiving part and is preferably annularly configured, in particular, as an open ring or a C-ring. In addition, preferably, the groove is configured in a trapezoidal manner along the receiving axis of the simulator receiving part with its longitudinal section. It is thus achieved that the inclined section is connected to the groove in a low-resistance flow-guiding manner and there to the simulator receiving part. The volume flow of the brake fluid can achieve the effect of forcing the simulator piston to return to its initial position in a determined time sequence.

[0021] Furthermore, according to the invention, the return line advantageously has a second line section which leads from the master brake cylinder receptacle to the reservoir connection receptacle and is configured with a second longitudinal section, the longitudinal axis of which coincides with the longitudinal axis of the first longitudinal section. Thus, a single longitudinal section is formed by means of the first and second longitudinal sections, which passes through the master brake cylinder receptacle. Such a single longitudinal section can be produced in a simple and time-saving manner in terms of production technology by means of a single hole which then intersects the inclined section which is preferably drilled chronologically before the longitudinal section.

[0022] Preferably, the second longitudinal section is guided into a reservoir connection receptacle, in particular to which a second reservoir chamber to be connected is connected. Particularly preferably, the second longitudinal section is guided there centrally into the bottom of the reservoir connection receptacle, which delimits the reservoir connection receptacle, so that all relevant longitudinal axes coincide. Such a line guidance is particularly advantageous in hydraulic housings, in which the master brake cylinder and the external force cylinder for generating the brake pressure are accommodated in a single module as a so-called one-box solution or integrated power brake (IPB). The actuating and modulation elements of the relevant vehicle brake system are accommodated in a single unit.

[0023] Alternatively, the second longitudinal section is preferably located in the hydraulic housing extending parallel to the longitudinal axis of the reservoir connector receptacle and is transversely guided into the reservoir connector receptacle by means of a transverse section extending perpendicularly to the second longitudinal section. Here, the transverse section is preferably configured as a hole, which is performed before drilling the longitudinal section during the manufacturing process. This line guidance is particularly advantageous in a hydraulic housing used as an actuating unit separate from the modulation element. The actuating member for generating the brake pressure is received in the actuating unit, while the brake pressure is regulated in another hydraulic housing. The vehicle brake system thus formed is a so-called dual-tank system or a decoupled dynamic brake (DPB).

[0024] In addition, the invention also relates to the use of such a hydraulic housing in a hydraulic unit of a hydraulic external-force brake device. The invention also relates to a hydraulic unit having such a hydraulic housing. Thus, a corresponding hydraulic unit with a compact structure and capable of being manufactured at low cost is achieved. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] An exemplary embodiment of the solution according to the invention is explained in detail below with reference to the drawings.

[0026] The accompanying drawings show:

[0027] Figure 1A , 1B: Hydraulic circuit diagram of a vehicle brake system configured with a first embodiment of a hydraulic housing according to the present invention,

[0028] Figure 2 : A top view of the first embodiment according to FIG. 1 ,

[0029] Figure 3 :according to Figure 2 The III-III section,

[0030] Figure 4 :according to Figure 3 A part of the IV-IV section with a master brake cylinder mounted thereon,

[0031] Figure 5 :according to Figure 2 A portion of section III–III with a pedal feel simulator mounted thereon,

[0032] Fig. 6A , 6B: Hydraulic circuit diagram of a vehicle brake system configured with a second embodiment of a hydraulic housing according to the present invention,

[0033] Figure 7 :The basis of the second embodiment Figure 2 The III-III section, and

[0034] Figure 8 : Parts of the oblique views of the two embodiments. DETAILED DESCRIPTION

[0035] exist Figure 1A , 1B 1 shows a circuit diagram of a brake system or hydraulic external-force vehicle brake system 10 with two units 12, 14. Here, the first unit 12 as an actuating unit comprises an element for generating brake pressure. For this purpose, the external-force brake pressure generator 16 is configured as a plunger, which has an external-force piston 20 that can move axially in an external-force cylinder 18 and is connected to a motor 22 configured as an electric motor in a force-transmitting manner. Here, the motor 22 is coupled to a worm gear 24 in such a way that the rotational movement of the worm gear 24 is converted into a translational movement of the external-force piston 20. When the external-force piston 20 is moved into the cylinder 18, the fluid or pressure medium present there is squeezed out of the cylinder 18 via a pipeline 26, which leads to a first and a second supply connection 28 and 30 respectively by means of a branch pipeline 27. A pressure sensor 31 is connected to the pipeline 26 between the two branch pipelines 27. In addition, a solenoid valve closed without current is arranged in each branch line 27 between the cylinder 18 and the two supply connections 28, 30 as a selectively openable plunger control valve 32 or an external force valve. In the open state, the brake pressure can be provided on each supply connection 28 and 30. Here, the first supply connection 28 is connected to the first brake circuit 34, and the second supply connection 30 is connected to the second brake circuit 36. The two brake circuits 34 and 36 can be connected to the two associated wheel brakes 38 by means of the second unit 14 in a fluid-conducting manner and actuated by the generated brake pressure. Here, the second unit 14 is configured as a driving dynamics control device or a modulation unit, which includes various elements for regulating or modulating the generated brake pressure, by means of which, for example, ABS, ASR and / or ESP / FDR regulation is realized. These control devices and elements are all known and are only partially described here. For this purpose, an inlet valve 40 belonging to each wheel brake 38 is provided, which is connected to the cylinder 18 and is used to input pressure medium to the wheel brake 38. Furthermore, an outlet valve 42 is assigned to each wheel brake 38 , by means of which pressure medium can be discharged again from the wheel brake 38 when necessary.

[0036] The first unit 12 also includes a pressureless reservoir 44 or a brake fluid storage container. The reservoir 44 is divided into two reservoir chambers 46 and 48. The first reservoir chamber 46 is fluidically connected to the first chamber 52 via a first reservoir line 50, and the second reservoir chamber 48 is fluidically connected to the second chamber 56 of the dual-circuit master brake cylinder 58 via a second reservoir line 54. The master brake cylinder 58 is operated by the driver with the aid of a pedal 60. A pedal rod 62 is connected to the pedal 60, which axially moves the coupled first piston 64 into the first chamber 52 when the pedal is operated. Here, the second piston 68 is moved into the second chamber 56 by means of a spring 66, and the second piston is supported on its cylinder bottom 72 by means of a return spring 70, axially connected to the first piston 64 in the operating direction.

[0037] Axially in the actuation direction, near the end of the first chamber 52, a line 74 leads from the first chamber 52 through a simulator control valve 76 that is closed without current to a pedal feel simulator or simulator 78. Here, a line 80 branches off from the line 74 upstream of the simulator control valve 76, which leads to the first supply connection 28 through a circuit separation valve 82 that is open without current. Thus, the lines 74 and 80 form a first supply line for the first brake circuit 34. In addition, the line 84 leads through the cylinder bottom 72 of the second chamber 56 through a circuit separation valve 86 that is open without current to the second supply connection 30, which serves as a second supply line for the second brake circuit 36. Here, a pressure sensor 88 is arranged on the line 84 between the circuit separation valve 86 and the second chamber 56.

[0038] In parallel with the two circuit separation valves 82, 86, a line 90 leads from each of the two reservoir chambers 46, 48 to the correspondingly associated supply connection 28, 30. In each line 90, a nonreturn valve 92 is arranged, which blocks the direction of the reservoir 44. Thus, the second unit 14 can be supplied with pressure medium when necessary without the external brake pressure generator 16 and the master brake cylinder 58.

[0039] The external force brake pressure generator 16 is supplied with pressure medium by means of a line 94 branching from the first reservoir line 50 and leading to the brake cylinder 18. In addition, the line 26 leading from the cylinder 18 is arranged on the front side of the external force piston 20 and can be selectively connected to the simulator 78 by means of a valve 96. The valve 96 is currently a 2-position / 2-way solenoid valve closed without current, which can be opened when powered by means of an electronic controller not shown here. In addition, the valve 96 is arranged in a branch line 98, which branches out from a return line 100 leading from the simulator 78 to the master brake cylinder 58.

[0040] The return line 100 is arranged to lead out of the simulator cylinder 104 or into the simulator cylinder 104 on the rear side 102 of the simulator piston 106, and the simulator piston is guided axially movably in the simulator cylinder 104 of the simulator 78. In addition, a spring element 108 is arranged on the rear side of the simulator piston 106 for applying a reverse force that resists the movement of the simulator piston 106 into the simulator cylinder 104. In addition, the simulator cylinder 104 is fluid-conductingly connected to the line 80 on the front side 110 of the simulator piston 106 opposite to the rear side 102. Therefore, the simulator 78 is supplied with pressure medium on the front side 110 and the rear side 102 of the simulator piston 106 and is therefore configured as a wet-wet simulator.

[0041] During the operation of the externally-forced vehicle brake system 10, at each nominal braking consciously initiated by the driver by actuating the pedal 60, for example, at partial braking or even at a skid-controlled braking, the simulator control valve 76 is opened by means of the controller and the circuit separation valves 82 and 86 are closed. When the pedal 60 is actuated, the braking intention desired by the driver is received by means of the linear position sensor 112 arranged on the pedal rod 62, and a corresponding signal is transmitted to the controller. Based on this signal, when the plunger control valve 32 is powered on to open, the required pressure medium volume is delivered from the externally-forced brake pressure generator 16 to the wheel brake 38 into the correspondingly-associated wheel brake cylinder 114. Here, braking is achieved by closing the pressure plunger 116 present there and the associated wheel brake cylinder 114, respectively.

[0042] During anti-slip control, the pressure medium volume on the wheel brakes 38 is adjusted by correspondingly switching the corresponding inlet valves 40 and outlet valves 42 to prevent the corresponding wheels 118 from locking. When the outlet valves 42 are open, a certain volume of pressure medium flows back from the corresponding wheel brakes 38 in the direction of the reservoir 44.

[0043] Therefore, braking is normally not achieved by moving the pressure medium volume from the master brake cylinder 58, but from the brake cylinder 18. For this purpose, the two circuit separation valves 82, 86 are usually closed when energized and thus separate the master brake cylinder 58 from the wheel brakes 38. In addition, the simulator control valve 76 is opened when energized. Therefore, the simulator cylinder 104 is supplied with pressure medium from the first chamber 52 of the master brake cylinder 58 through the pipeline 74 on the front side 110 of the simulator piston 106. Therefore, when the pedal 60 is operated, the volume of the pressure medium moves from the first chamber 52 to the front side 110, so that the simulator piston 106 is forced to enter the simulator cylinder 104. Here, the pedal feel known to the driver is simulated basically in accordance with the spring force of the spring element 108 arranged on the rear side 102 of the simulator 78. In addition, on the rear side 102 of the simulator piston 106, the pressure medium present there is guided out from the simulator cylinder 104 by means of the return line 100. In this case, the rear side 102 and the front side 110 are formed by means of a seal 120 (see Figure 5 ) are isolated from each other in terms of fluid conduction.

[0044] Therefore, the same volume of pressure medium that is moved into the simulator cylinder 104 on the front side 110 or pressure side must simultaneously be moved out of the simulator cylinder 104 on the side facing away from the seal 120 or rear side 102. For this purpose, the pressure medium is guided out of the simulator cylinder 104 by means of the return line 100 and is guided through the master brake cylinder 58, in particular through its second chamber 56 and into the reservoir 44 via the second reservoir line 54. The second reservoir line 54 is a component of the return line 100, and atmospheric pressure equalization is ensured on the reservoir 44 via the pressure valve 122.

[0045] When the pedal 60 is relieved, the spring element 108 of the simulator 78 is designed so that the pedal 60 is pressed back into its initial position in a certain time sequence by means of the force acting in the brake system by the spring element 108. In this case, even at high viscosities, the acting hydraulic resistance must not exceed this time sequence in order to avoid inflation of the simulator 78.

[0046] Figures 2 to 5 In particular, the arrangement and design of the return line 100 in the associated hydraulic housing 124 of the hydraulic unit 125 are shown in detail.

[0047] The hydraulic housing 124 has a rectangular parallelepiped shape and is composed of a hydraulic block, which is preferably manufactured from aluminum by means of an extrusion method. Various receptacles and lines are drilled into the hydraulic block by a subsequent cutting method. The receptacles are usually configured as stepped holes or blind holes. Here, only selected receptacles and lines are known. This includes a master brake cylinder receptacle 126, which extends with its receptacle axis 128 in parallel in the hydraulic housing 124 between a wide motor side 130 and an opposite controller side 132. Here, the motor side 130 is used to mount the motor 22, and the controller side 132 is used to arrange a controller that is not shown. In Figure 2 In the view of FIG. 1 , the controller side 132 is shown transparently.

[0048] Furthermore, two reservoir connection receptacles 134 are arranged extending parallel to the motor side 130 and above the master brake cylinder receptacle 126 in the installed position of the hydraulic housing 124, which are designed as blind holes that are open upward in the installed position. Accordingly, each reservoir connection receptacle 134 projects into a reservoir side 136 of the hydraulic housing 124 that is adjacent to the motor side 130. Furthermore, each reservoir connection receptacle 134 is arranged with its receiving axis 138 offset from the receiving axis 128 in the direction of the control side 132.

[0049] The blind hole which is open toward the controller side 132 is arranged perpendicularly to the motor side 130 and serves as a simulator receptacle 140. The simulator receptacle 140 is located on the side of the master brake cylinder receptacle 126 which faces away from the reservoir side 136 and is therefore arranged below the master brake cylinder receptacle 126 in the installed position. In addition, an external force cylinder receptacle 142 which extends continuously from the controller side 132 toward the motor side 130 is arranged below the master brake cylinder receptacle 126 and above the simulator receptacle 140. The external force cylinder receptacle 142 extends with its receptacle axis 144 parallel to the receptacle axis 146 of the simulator receptacle 140.

[0050] The simulator receiving portion 140 is configured as a stepped hole, which has a cross-section that widens in the direction of the controller side 132. In detail, the simulator receiving portion 140 is a hollow cylinder 148, on whose cylinder wall 150 a radially circumferential groove 152 is arranged. The groove 152 is configured in a trapezoidal manner with its longitudinal section along the receiving axis 146. In addition, the groove 152 is located in a piston section 154 of the simulator receiving portion 140, and the cross-section of the piston section is smaller than the cross-section of a cover section 156 of the simulator receiving portion 140 that is connected to the piston section in the direction of the controller side 156. Here, the simulator piston 106 is received in the piston section 154 in such a way that the rear side 102 of the simulator piston faces the groove 152 ( Figure 3 and Figure 5 ).

[0051] The cup-shaped cover 158 is received in the cover section 156, and the simulator receiving portion 140 is closed by means of the cup-shaped cover ( Figure 5 ). Here, the cover 158 is configured with a radially outwardly directed flange 160 on its open end side. In addition, the cover section 156 is configured with a radially outwardly directed step 162 at the connection with the piston section 154, and the flange 160 rests on this step. In addition, a radially outwardly directed step 164 is arranged axially behind the step 162 in the cover section 156 in the direction of the controller side 132, and an operating space for assembling the simulator 78 is realized by means of this step. In addition, in the assembled state, the cup-shaped cover 158 and the piston section 154 constitute the simulator cylinder 104. For this purpose, the cover 158 is preferably screwed into the simulator receiving portion 140.

[0052] The return line 100 is connected to the simulator cylinder 104 or the simulator receptacle 140 in the groove 152. For this purpose, the return line 100 is configured with a first line section 166, which has an inclined section 168 and a first longitudinal section 170. Here, the inclined section 168 extends obliquely with its longitudinal axis 172 relative to the receptacle axis 146 and leads from the groove 152 to the first longitudinal section 170, which extends perpendicularly to the receptacle axis 146 with its longitudinal axis 174. The first longitudinal section 170 is then guided into the master brake cylinder receptacle 126. Thus, the first line section 166 connects the simulator receptacle 140 to the master brake cylinder receptacle 126.

[0053] Here, the master brake cylinder receptacle 126 is designed as a hollow cylinder 176, on whose cylinder wall 178 a radially circumferential groove 180 is provided as an undercut, which serves as a connection to the reservoir 44. For this purpose, the second reservoir line 54 is guided from the associated reservoir connection receptacle 134 into the groove 180 and thus into the second chamber 56 in the assembled state. The second reservoir line 54 is simultaneously a second line section 182 of the return line 100, which has a transverse section 184 and a second longitudinal section 186. Here, the transverse section 184 leads radially from the reservoir connection receptacle 134 to the second longitudinal section 186, which extends with its longitudinal axis 188 coinciding with the longitudinal axis 174 of the first longitudinal section 170. Thus, the return line 100 is guided through the master brake cylinder receptacle 126 with its two longitudinal sections 170, 186 which face each other at the groove 180. Valve receptacle 190 is arranged with a very short branch line 98 directly on groove 180 and extends with its receptacle axis 192 perpendicularly to longitudinal axis 174 or 188. In the present assembled state, valve 96 is received in valve receptacle 190, which connects master brake cylinder 58 to external force cylinder 18.

[0054] Figure 4A part of hydraulic housing 124 is shown in the assembled state with master brake cylinder 58. Here, it can also be seen that a further radially circumferential groove 194 is provided axially on both sides of groove 180, in which an annular piston seal 196 is respectively received in the assembled state.

[0055] Figure 5 The hydraulic housing 124 is shown in the assembled state with another part of the simulator 78. Here, the simulator piston 106 is received in the piston section 154 and is pressed into the piston section 154 by means of the spring element 108 arranged in the cup-shaped cover 158. Here, the front side 110 of the simulator piston 106 is located opposite the spring element 108 on the simulator piston, and the rear side 102 of the simulator piston faces in the direction of the cover 158. At the front side 110, the pressure medium is supplied via the line 74 (at Figure 5 The pressure medium is guided to the simulator cylinder 104, from which the pressure medium is guided on the rear side 102 via the return line 100. Here, the pressure medium flows past the stop element 198 or the C-ring which is partially received in the groove 152 into the inclined section 168 and via two longitudinal sections 170, 186 through the groove 180 of the master brake cylinder 58 into the reservoir 44.

[0056] exist Fig. 6A and 6B , a circuit diagram of a vehicle brake system 10 in a further embodiment of the invention is shown. This is a one-box solution (IPB), in which the actuating element and the modulation element are accommodated in the hydraulic housing 124 and are interconnected. In addition, in contrast to the previous embodiment, a third reservoir chamber 200 is provided for this purpose, which is connected to the cylinder 18 of the external brake pressure generator 16 by means of a third reservoir line 202 and a non-return valve 204 arranged therein. Furthermore, no connection possibility is provided between the cylinder 18 and the return line 100. Instead, a branch line 206 is arranged on the return line 100, to which an outlet valve 208 of the second brake circuit 36 ​​is connected. In this case, the outlet valve 208 enables a return flow from the wheel brake cylinder 114 to which it belongs via the return line 100 through the master brake cylinder 58 into the second reservoir chamber 48. The outlet valve 208 is received in the valve receiving part 190 or is received there in the assembled state and is connected almost directly to the tank 180 by means of a very short branch line 206 ( Figure 7 Furthermore, valve receptacle 190 is connected to a wheel cylinder connection receptacle (not shown) belonging to wheel brake cylinder 114 .

[0057] Figure 7The further differences are shown visually. Thus, second line section 182 extends axially with its second longitudinal section 186 directly into reservoir connection receptacle 134 of second reservoir chamber 48. Thus, the receiving axis 138 of the reservoir connection receptacle coincides with longitudinal axes 188, 174 of second and first longitudinal sections 186, 170. In addition, there is a transverse line 210 which is led from motor side 130 into second longitudinal section 186 and from there to reservoir connection receptacle 134. Transverse line 210 serves as a return line for a further outlet valve 212 of second brake circuit 36.

[0058] Figure 8 An oblique view of the control side 132 is shown, in which it should be made clear how the hydraulic housing 124 is machined in a cutting method, in particular for the production of the inclined section 168. The steps up to the production of the inclined section 168 are implemented identically for both embodiments. For this purpose, a stepped hole is produced in the hydraulic block during the first clamping in the clamping device as a circular recess of the simulator receptacle 140. The hydraulic block is then rotated by pivoting the clamping device and a chamfer 214 is milled on the cylinder wall 150 in the position for the inclined section 168, thereby forming a dome-shaped bulge of the cylinder wall 150 there. Therefore, when performing the inclined drilling, the drill bit hits the cylinder wall 150 there in a flat manner and prevents the drill bit from slipping. Therefore, the inclined drilling is performed in the area of ​​the chamfer 214 to produce the inclined section 168. Here, viewed in the direction of the simulator receptacle 140, the inclined hole is approximately located at 10:30 or in the fourth quadrant of its circular recess. After the oblique drilling, the clamping device is pivoted back again and the simulator receiving part 140 is machined. By means of circular machining, the trapezoidal groove 152 is produced at the level of the bevel section 168. In addition, two edges are milled, by means of which the steps 162 and 164 are formed. In this case, the steps 162 and 164 extend perpendicularly to the receiving axis 146.

[0059] In the second clamping, the first and second longitudinal sections 166, 182 are produced as a single longitudinal hole or vertical hole. The longitudinal hole extends parallel to the reservoir connector receptacle 134 for the second reservoir chamber 48. In addition, the longitudinal hole penetrates the already existing master brake cylinder receptacle 126 directly perpendicular to the receiving axis 146 of the simulator receptacle 140 or between 12:00 and 6:00. Such a central penetration is important because the drilling of the master brake cylinder receptacle 126 is performed first. Otherwise, the drill will deviate. In addition, the groove 180 is penetrated in the area of ​​the second chamber 56 and the penetration is achieved axially between the two grooves 194 for the piston seal 196. In addition, the longitudinal hole intersects with the described inclined hole. In the previous clamping, the valve receptacle 190 for the valve 96 is connected to the groove 180. In addition, the transverse section 184 has been drilled into a transverse hole here, and the longitudinal hole intersects with the transverse hole in the direction of the reservoir side 136.

[0060] To produce the hydraulic housing 124 of the second exemplary embodiment, a longitudinal bore is bored directly in the center of the reservoir connection receptacle 134 from its base to the groove 180 between 12:00 and 6:00 and intersects the inclined section 168. In this case, the valve receptacle 190 for the outlet valve 208 is already connected directly to the master brake cylinder receptacle 126 at the groove 180 during the previous clamping. In addition, the outlet valve 212 is connected by means of a transverse or horizontal bore for producing the transverse line 210 and a bore at right angles to the motor side 130.

Claims

1. A hydraulic housing (124) for a hydraulic external force vehicle brake device (10), wherein a master brake cylinder receiving portion (126), a reservoir joint receiving portion (134) connected to the master brake cylinder receiving portion (126), and a simulator receiving portion (140) for receiving a pedal feeling simulator (78) are arranged in the hydraulic housing, wherein the pedal feeling simulator (78) is configured with a simulator piston (106), the simulator piston is guided in the simulator receiving portion (140) so as to be axially movable, the simulator piston having a front side (110) and a rear side (102) in the axial direction, and wherein a pipeline (80) connected to the master brake cylinder receiving portion (126) is guided into the simulator receiving portion (140), the pipeline is arranged along the axial direction of the simulator receiving portion (140) so that when the simulator piston (106) is received, the pipeline (80) is located on the front side (110) of the simulator piston, It is characterized in that A return line (100) is also guided into the simulator receiving part (140), and the return line is arranged along the axial direction of the simulator receiving part (140) so that when the simulator piston (106) is in the received state, the return line (100) is located on the rear side (102) of the simulator piston and the simulator receiving part (140) is connected to the master brake cylinder receiving part (126) by means of the return line (100).

2. The hydraulic housing according to claim 1, It is characterized in that The return line (100) leads from the simulator receiving part (140) through the master brake cylinder receiving part (126) to the reservoir connection receiving part (134).

3. The hydraulic housing according to claim 1 or 2, It is characterized in that The master brake cylinder receptacle (126) is designed as a hollow cylinder (176), in the cylinder wall (178) of which a radially circumferential groove (180) is provided, which is part of the return line (100).

4. The hydraulic housing according to any one of claims 1 to 3, It is characterized in that A valve receiving portion (190) is provided, and the valve receiving portion is connected to the return pipeline (100).

5. The hydraulic housing according to claim 4, It is characterized in that The valve receiving portion (190) is additionally connected to an external force cylinder receiving portion (142) for receiving an external force brake pressure generator (16).

6. The hydraulic housing according to claim 4, It is characterized in that The valve receptacle (190) is additionally connected to a wheel brake cylinder connection receptacle for connecting a wheel brake cylinder (114).

7. A hydraulic housing according to any one of claims 1 to 6, It is characterized in that The return line (100) has a first line section (166), which leads from the simulator receiving part (140) to the master brake cylinder receiving part (126) and is configured with an inclined section (168) and a first longitudinal section (170), wherein the inclined section (168) extends with its longitudinal axis (172) obliquely relative to the simulator receiving part (140) together with its receiving axis (146) and leads from the simulator receiving part (140) to the first longitudinal section (170), and the first longitudinal section extends with its longitudinal axis (174) perpendicular to the receiving axis (146).

8. The hydraulic housing according to claim 7, It is characterized in that The simulator receiving portion (140) is configured as a hollow cylinder (148), and a radially circumferential groove (152) is arranged in the cylinder wall (150) of the hollow cylinder, so that when the simulator piston (106) is in a received state, the groove (152) is located on the rear side (102) of the simulator piston, and the inclined section (168) is guided into the groove (152).

9. The hydraulic housing according to claim 7 or 8, It is characterized in that The return line (100) has a second line section (182) which leads from the master brake cylinder receptacle (126) to the reservoir connection receptacle (134) and is configured with a second longitudinal section (186), the longitudinal axis (188) of which coincides with the longitudinal axis (174) of the first longitudinal section (170).

10. Use of a hydraulic housing (124) according to any one of claims 1 to 9 in a hydraulic unit (125) of a hydraulic externally-powered vehicle brake system (10).

Images