Pump housing of hydraulic unit with discharge valve receiver

Abstract

A pump housing (108) of a hydraulic unit (23) of a vehicle brake system (10) includes at least one wheel brake cylinder connection (53, 57) for connecting a wheel brake cylinder (54, 58) to the pump housing (108), a discharge valve receptacle (64) associated with each wheel brake cylinder connection (53, 57) for receiving a discharge valve (46, 48) provided for discharging brake fluid from the wheel brake cylinder (54) into the pump housing (108), and a corresponding closing force (102) applied by a closing body (102). and a valve inlet (86) closed by a closing force (100) in which the discharge valve receptacle (64) has an inlet (84) for drawing brake fluid from the wheel brake cylinder (54) into the discharge valve (46), the inlet (84) being adapted to guide brake fluid in a flow direction (110) directed against the closing force (100) when drawing brake fluid into the discharge valve (46) when the discharge valve (46) is received in the discharge valve receptacle (64).

Description

[Technical field]

[0001] The invention relates to a pump housing of a hydraulic unit of a vehicle braking system, which has at least one wheel brake cylinder connection for connecting a wheel brake cylinder to the pump housing, a discharge valve seat belonging to the respective wheel brake cylinder connection for receiving a discharge valve provided for discharging brake fluid from the wheel brake cylinder into the pump housing, and a valve inlet closed by a closing body with an associated closing force, the discharge valve seat having an inlet for drawing brake fluid from the wheel brake cylinder into the discharge valve. The invention also relates to the use of a pump housing of this type in a hydraulic unit of a vehicle braking system. [Background technology]

[0002] Hydraulic units are used in motor vehicles, in particular in passenger cars or freight vehicles, to provide a controlled brake pressure to the brake system thereof. In particular, the functions of an antilock braking system (ABS), a traction slip control (ASR) and / or an electronic stability program (ESP) are realized by means of hydraulic units of this type. For this purpose, a brake pressure is generated in a master cylinder of the brake system via the brake pedal. For the distribution of the brake pressure, the hydraulic unit has a pump with a number of pump plungers, a motor for driving the pump as well as a number of valves. These valves are generally controlled electromagnetically, so that different brake pressures can be provided to the individual brakes or brake circuits. For the fluid connection of the hydraulic unit with the wheel brake cylinders of the associated wheel brakes, a number of wheel brake cylinder connections are formed in the hydraulic unit.

[0003] The pump housing of such hydraulic units is usually made of aluminum in the shape of a rectangular parallelepiped or block and has holes for arranging components, in particular valves and lines. At least one outlet valve holder configured as a hole is provided in which an outlet valve is received for discharging brake fluid from the associated wheel brake cylinder into the pump housing. For this purpose, the outlet valve has a valve inlet for drawing brake fluid into the outlet valve and a closing body which closes this valve inlet with a closing force. In this case, the brake fluid is guided in a transverse direction, perpendicular to the closing force, through the valve inlet and the inlet of the outlet valve holder arranged at this valve inlet. Summary of the Invention

[0004] According to the invention, a pump housing for a hydraulic unit of a vehicle brake system is provided, which has at least one wheel brake cylinder connection for connecting a wheel brake cylinder to the pump housing, a discharge valve seat belonging to the respective wheel brake cylinder connection for receiving a discharge valve provided for discharging brake fluid from the wheel brake cylinder to the pump housing, and a valve inlet closed by a closing body with an associated closing force, whereby the discharge valve seat has an inlet for drawing brake fluid from the wheel brake cylinder into the discharge valve, whereby the inlet is adapted to guide the brake fluid in a flow direction directed against the closing force when drawing it into the discharge valve when the discharge valve is received in the discharge valve seat.

[0005] By means of the inlet of the outlet valve seat adapted according to the invention, the brake fluid is guided in the further or subsequent inlet through the valve inlet in an axial direction against the closing force into the outlet valve. The brake fluid therefore acts with its flow direction and thus with the flow force acting in the flow direction directly in the axial direction against the vector of the closing force. Directly in the axial direction means that the brake fluid does not flow axially against the closing force of the closing body after and by pre-deflection due to other components in the outlet valve. Such deflection is known in conventional controllable outlet valves, in which the brake fluid flows in a transverse direction perpendicular to the closing force through the conventional inlet and the valve inlet. For deflection, deflection components with expensive manufacturing costs are provided inside the outlet valve, by means of which the brake fluid flowing in a transverse direction perpendicular to the closing force is deflected in its flow path so that it acts axially against the closing force.

[0006] By contrast, the inlet adapted according to the invention achieves that the brake fluid acts directly axially against the closing force without the friction losses, pressure losses and energy losses that would otherwise occur due to deflection. The brake fluid therefore flows axially against the closing body in a particularly energy-efficient manner when flowing through the inlet and the valve inlet arranged at the inlet. The brake fluid therefore pushes the closing body, and in particular the tappet that is connected to transmit a force to the closing body, away from the valve inlet in the longitudinal direction of the tappet.

[0007] In addition to this type of energy efficiency, it is particularly advantageous that with an inlet adapted according to the invention, a controllable delivery valve can be accommodated in the delivery valve carrier. Controllable means, in particular, that the flow rate per time unit of brake fluid can be adapted as required by the delivery valve. For the controllability of such a delivery valve, which can be appropriately controlled to relieve the brake pressure of the wheel brake cylinder, a counterflow is required that opposes the closing force of the closing body in the axial direction. Such a counterflow is possible in a simple manner and manner with an inlet adapted according to the invention. The delivery valve can thus be constructed in a simple manner, without expensive deflection components, and can be inserted into the delivery valve carrier and controlled despite its simple construction.

[0008] The pump housing according to the invention therefore offers a cost-optimized solution for implementing a controllable delivery valve of a hydraulic unit of a vehicle braking system or brake control system. By means of such a controllable delivery valve, the brake pressure in the wheel brake cylinders can be appropriately controlled and released when the brake fluid is discharged from the wheel brake cylinders into the pump housing. This allows the recuperation efficiency of a hybrid electronic vehicle-system (HEV system) to be optimized. In particular, the recuperation or recovery of otherwise lost brake energy is improved. Furthermore, the performance of conventional control algorithms for antilock braking systems (ABS), traction slip control (ASR) or traction control systems (TCS), adaptive cruise control (ACC) and electronic stability programs (ESP) can be optimized. The required pressure required for pressure reduction can be released exactly. It has been found that the pump housing according to the invention and the control of the delivery valve connected to this pump housing allow optimal system costs with improved recuperation efficiency. The additional costs incurred in adapting the inlet and possibly the lines connected to it according to the invention are significantly overcompensated by the possible simplification of the design of the delivery valve.

[0009] According to the invention, the outlet valve holder preferably has an axis along which a closing force acts when the outlet valve is received in the outlet valve holder. The inlet is then arranged axially relative to this axis. This type of arrangement results in a particularly uniform distribution of forces between the outlet valve holder and the outlet valve when the brake fluid flows through the inlet into the outlet valve. The inlet and in particular the valve inlet arranged at this inlet are purposefully passed through by the brake fluid through their center, the brake fluid correspondingly flowing centrally and purposefully in a flow direction counter to the closing force acting on the closing body. In this case, in particular, the axis of the outlet valve holder corresponds to the longitudinal axis of the outlet valve holder, along which the longitudinal axis of the outlet valve is arranged.

[0010] Furthermore, according to the invention, preferably, a discharge valve is accommodated in the discharge valve receptacle, which has a valve inlet that is closed by the associated closing force of the closing body. In this case, the closing force is applied by a spring element. As a result, the closing body is pressed by the spring element towards the valve inlet, and the closing force is determined by the spring element. The spring element has a spring characteristic curve, which is preferably adapted in such a way that the brake pressure can be controlled appropriately by the wheel brake cylinder and released by the discharge valve. For this purpose, in particular, the flow rate of brake fluid per time unit can be controlled by the spring element. By means of the spring element, the discharge valve can be constructed in a simple manner and can be controlled inexpensively. In particular, deflection components that would otherwise be required are not necessary. Furthermore, a discharge valve that can be controlled in this way has the advantage that it is controllable from the outset compared to electromagnetic switching valves, which are often used as discharge valves. Otherwise, with conventional switching valves, the pressure of the brake fluid applied to the wheel brake cylinder would be reduced in an uncontrolled manner when the brake fluid is discharged from the wheel brake cylinder. Instead, overshoots or overshoots frequently occur. Re-regulation then becomes necessary by means of an easily controllable intake valve, which is usually closed against the brake fluid flow by means of magnetic forces and can thereby be easily controlled.

[0011] Furthermore, according to the invention, the pump housing is preferably provided with a motor side for arranging the drive motor and a control unit side for arranging the control unit, which is located opposite to the motor side. In this case, the inlet is adapted for directing the flow direction between the motor side and the control unit side against the closing force. This flow direction corresponds in its axial length to the axial length which is conventionally customary between the motor side and the control unit side. Therefore, only minor structural adaptations are required for the inlet of the delivery valve holder and the pump housing for the delivery valve received in this delivery valve holder. The outer dimensions of the pump housing remain constant, making it possible to utilize cost-effective installation space, particularly in the vehicle brake system. In this case, the flow direction is preferably directed from the motor side to the control unit side. As a result, the flow direction is adapted to the flow direction which is conventional for the associated intake valve. Therefore, only minor adaptations are required. Depending on the respective structural situation, the flow direction can also be directed from the control unit side to the motor side.

[0012] In a further preferred embodiment according to the invention, the outlet valve seat has an axis along which a closing force acts when the outlet valve is received in the outlet valve seat, and an intake valve seat associated with the outlet valve seat is provided for receiving an intake valve for drawing brake fluid from the pump housing into the wheel brake cylinder, the intake valve seat having an outlet for drawing brake fluid from the intake valve to the wheel brake cylinder. A connecting line is provided from the outlet of the intake valve seat to the wheel brake cylinder, which connecting line is adapted so that the same flow direction can pass through it relative to the axis when the intake valve draws brake fluid into the wheel brake cylinder and when the outlet valve discharges brake fluid from the wheel brake cylinder. This ensures a uniform flow direction of brake fluid both when drawing brake fluid from the pump housing into the wheel brake cylinder and when discharging brake fluid from the wheel brake cylinder into the pump housing. In particular, the intake valve can pass through it in the conventional manner from the motor side to the control unit side, and the discharge valve can likewise pass through it from the motor side to the control unit side. With this type of throughflow, the brake fluid is directed with its flow force in the axial direction against the closing force acting on the closing body. The delivery valve can therefore be controlled particularly simply as described above. As is known for the intake valve, conventional lines and valves can be used to the fullest extent if the flow direction is preferably from the motor side to the control unit side. Only minor adaptations are necessary in order to obtain significant advantages, particularly in relation to the adjustability of the delivery valve. Alternatively, a corresponding flow direction from the control unit side to the motor side is possible. For this purpose, the outlet of the intake valve seat is adapted in particular to guide the brake fluid when it is delivered from the intake valve in a flow direction that is first oriented perpendicular to the flow direction when the brake fluid is drawn into the delivery valve in the direction opposite to the closing force.

[0013] According to the invention, preferably for this purpose, a connecting line is guided from the outlet of the intake valve holder into the region of the discharge valve holder directed towards the wheel brake cylinder. In this case, the outlet is in particular connected in fluid communication with the valve inlet of the intake valve accommodated in the intake valve holder. As a result, the brake fluid is guided from the inlet valve into the region of the discharge valve holder directed towards the wheel brake cylinder. From this region, the brake fluid is guided through a line or a wheel brake cylinder line for intake into the wheel brake cylinder. Through the same line and in the same region, the brake fluid is guided through the inlet into the discharge valve holder for discharge from the wheel brake cylinder and into the discharge valve accommodated in this discharge valve holder. As a result, the same axial flow direction of the brake fluid through the intake valve and the discharge valve is obtained in a particularly simple constructional manner.

[0014] Furthermore, according to the invention, preferably, a connecting line is guided from the outlet of the intake valve holder into a wheel brake cylinder line leading from the wheel brake cylinder to the inlet of the discharge valve holder. For this purpose, in particular a branch line is provided in the wheel brake cylinder line, into which a connecting line is guided. As a result, the brake fluid is guided from the outlet by the connecting line into the wheel brake cylinder line, which guides the brake fluid into the wheel brake cylinder. To discharge the brake fluid from the wheel brake cylinder, the brake fluid is returned through the wheel brake cylinder line and the inlet of the discharge valve holder into the discharge valve accommodated in this discharge valve holder. This also results in the same axial flow direction of the brake fluid through the intake valve and the discharge valve. Furthermore, this allows the connecting line to be adapted to a corresponding arrangement and geometry of the intake valve holder and the discharge valve holder. The two valve holders can be arranged with a small space-saving distance from each other.

[0015] For this purpose, according to the invention, the connecting line is preferably designed with a line section that runs obliquely to an axis along which the closing force acts. In this case, the axis is in particular the longitudinal axis of the outlet valve holder. By means of the inclined line section, the intake valve holder is connected directly and indirectly from its outlet to the area of ​​the outlet valve holder that is directed towards the wheel brake cylinder. In this case, no friction losses due to line deflections occur. Furthermore, the single inclined line section can be manufactured in a simple manner in terms of construction. The advantages of the inclined line section are also achieved in the corresponding direct connection of the intake valve holder and the wheel brake cylinder line. In this case, the inclined line section is designed to be steeper than the inclined line section that connects the outlet of the intake valve holder with the area of ​​the outlet valve holder that is directed towards the wheel brake cylinder.

[0016] Furthermore, the connecting line is preferably designed according to the invention with at least one first line section and at least one second line section, where the individual first line sections are parallel and the individual second line sections are guided at right angles in each case in relation to an axis along which the closing force acts. In this case, the axis is in particular the longitudinal axis of the outlet valve seat. This allows for a wide range of variation possibilities for the configuration of the connecting line. Further components may be provided in the pump housing between the inlet valve seat and the outlet valve seat. Bypassing these further components, the brake fluid can be guided without problems by a connecting line having a corresponding combination of at least one first line section and at least one second line section and / or at least one inclined line section.

[0017] Furthermore, the connecting line is preferably configured with at least three line sections that are formed extending in a three-dimensional space, which allows for even greater flexibility in adapting the connecting line to the structural givens in the pump housing, where the at least three line sections are preferably arranged obliquely, perpendicularly and / or parallel to the axis along which the closing force acts, as required.

[0018] The invention also relates to the use of such a pump housing in a hydraulic unit of a vehicle braking system, so that the already mentioned advantages of a cheaply controllable delivery valve are obtained in combination with improved regenerative effects in vehicle braking systems, in particular HEV systems. [Brief description of the drawings]

[0019] [Figure 1] 1 is a hydraulic circuit diagram of a vehicle brake system according to the prior art; [Diagram 2] FIG. 1 is a schematic diagram of a portion of a pump housing of an automotive hydro unit according to the prior art; [Diagram 3] FIG. 3 is a principle diagram of a first embodiment of a pump housing according to the invention of the portion shown in FIG. 2; [Figure 4] 1 is a schematic diagram showing the principle of a first embodiment of a pump housing according to the present invention; [Diagram 5] FIG. 5 shows a portion of FIG. 4 of a second embodiment of a pump housing according to the invention. [Figure 6] FIG. 5 shows a portion of FIG. 4 of a third embodiment of a pump housing according to the invention. [Figure 7] FIG. 5 shows a portion of FIG. 4 of a fourth embodiment of a pump housing according to the invention. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0020] In the following, an embodiment of the solution according to the invention is explained in detail with the aid of the attached schematic drawings.

[0021] In this case, all three-dimensional descriptions such as left, right, bottom, top, vertical and horizontal are relative to the drawing plane of the respective FIG. 1 to FIG.

[0022] The vehicle braking system 10 shown in Figure 1 comprises a brake pedal 12 with a brake booster 14 and a master cylinder 16 connected to the brake booster 14. The master cylinder 16 is connected to two structurally substantially identical brake circuits 18 and 20 which are arranged essentially in a common pump housing 22 (each of which is partially shown, see Figure 2) of a hydraulic unit 23. In the following, only one of these brake circuits, namely the brake circuit 18, is described in detail.

[0023] For the brake circuit 18, a line 24 leads from the master cylinder 16 to the high-pressure switching valve 26 and to the switching valve 28. Furthermore, a pressure sensor 30 is connected to the line 24. From the high-pressure switching valve 26, a line 32 leads to the suction side of the pump element 34 and to the check valve 36. The pump element 34 is hereby power-transmittingly connected to a drive motor 37. From the switching valve 28, a line 38 leads to the discharge side of the pump element 34 and to the first suction valve 40 and to the second suction valve 42. From the check valve 36, a line 44 leads to the first discharge valve 46 and to the second discharge valve 48. Furthermore, a pressure accumulator 50 is connected to the line 44. From the first suction valve 40, a line or wheel brake cylinder line 52 leads by means of a wheel brake cylinder connection 53 to the first wheel brake cylinder 54 and to the first discharge valve 46. A line or wheel brake cylinder line 56 leads from the second intake valve 42 by means of a wheel brake cylinder connection 57 to a second wheel brake cylinder 58 and to the second outlet valve 48. The intake valves 40 and 42 and the outlet valves 46 and 48 are each equipped with a filter element 60 to protect the associated functionally important parts of the valve from the ingress of particles. In this case, the filter element 60 is arranged in the line 52 or 56 directly on the valve on the respective side facing the wheel brake cylinder 54 or 58.

[0024] 2 partially shows the pump housing 22 of the hydraulic unit 23, which is essentially made of an aluminum block as a block-shaped housing or hydraulic block, in which openings or receptacles are formed by drilling or milling. Only the first intake valve 40 and the first outlet valve 46 belonging to the first wheel brake cylinder 54 are shown by way of example. The following description therefore also applies to the respectively associated outlet valve 48 and all other intake valves 42 of the hydraulic unit 23. In the following, the first intake valve 40 will be referred to as the intake valve 40 and the first outlet valve 46 as the outlet valve 46.

[0025] The intake valve 40 is received in a cup-shaped intake valve receiver 62 formed as an intake valve bore, and the discharge valve 46 is received in a cup-shaped discharge valve receiver 64 formed as an exhaust valve bore, where the intake valve receiver 62 has a longitudinal axis or axis 66 along which the intake valve 40 with its longitudinal extension is arranged, and the discharge valve receiver 64 has a longitudinal axis or axis 68 along which the discharge valve 46 with its longitudinal extension is arranged.

[0026] Furthermore, the pump housing 22 has a motor side 70 for arranging the drive motor 37 and a control unit side 72 facing the motor side 70, on which a control unit (Electronic Control Unit (ECU) (not shown) is arranged. Two openings are provided in the control unit side 72, which form the intake valve receptacle 62 and the discharge valve receptacle 64, whose axes 66 and 68 are oriented parallel to one another and perpendicular to the control unit side 72. Furthermore, wheel brake cylinder sides or sides 74, not shown in detail, are provided in four wheel brake cylinder openings on the right side of the pump housing 22. In these sides 74, the respective wheel brake cylinder connections 53 and 57 for the wheel brake cylinders 54 and 58 are received. Opposite the side 74 is a side 76, in which two pressure accumulator openings (not shown) are provided for receiving the pressure accumulators 50, respectively.

[0027] An inlet 78 is provided in the intake valve holder 62 below or at a cup bottom 77 of the intake valve holder 62 or toward the motor side 70, and the pipe 38 is guided into the inlet 78. The inlet 78 guides the brake fluid into the intake valve 40 through a valve inlet 80. Furthermore, an outlet 82 is arranged to the side of the intake valve holder 62 above or toward the control unit side 72, and the pipe 52 is guided from the outlet 82 to the wheel brake cylinder 54.

[0028] From the wheel brake cylinder 54, the line 52 runs into an inlet 84 of the discharge valve holder 64, which is arranged laterally above the discharge valve holder 64 or towards the control unit side 72. Correspondingly, a valve inlet 86 is arranged laterally above the discharge valve 46, through which the brake fluid is guided by the inlet 84 from the line 52 into the discharge valve 46. To discharge the brake fluid into the line 44, the discharge valve 46 is provided with a valve outlet 88, at which an outlet 90 of the discharge valve holder 64 is arranged. Both the valve outlet 88 and the outlet 90 are positioned below or at a cup bottom 91 of the discharge valve holder 64 or towards the motor side 70.

[0029] The discharge valve 46 is a solenoid valve that is closed in the absence of electric current by a mechanical spring or spring element 92. By applying an electric current, the discharge valve 46 can be opened. For this purpose, the discharge valve 46 has a valve tappet 94 that is surrounded by a sleeve 96 and is spring-preloaded by a spring element 92 against a valve seat 98. The spring element 92 exerts a closing force 100, the force vector of which acts along the axis of the discharge valve 46, which here corresponds to the longitudinal axis or axis 68 of the discharge valve receptacle 64. By this closing force 100, a closing body 102 connected to the valve tappet 94 is pressed against the valve seat 98. The valve inlet 88 or valve bore surrounded by the valve seat 98 is thus closed. To provide a flow path through the discharge valve 46, the closing body 102 and the valve tappet 94 can be lifted from this position away from the valve seat 98 by a not shown electromagnetic coil that partially surrounds the valve tappet 94. This flow path has a constant open cross section, which results in the brake pressure applied to the wheel brake cylinder 54 being reduced in an uncontrolled manner when the brake fluid is discharged from the wheel brake cylinder 54. Instead, an overshoot may occur which requires readjustment by the easily adjustable intake valve 40. When the magnetic force is interrupted, the discharge valve 46 is closed by a closing force 100 acting on a closing body 102 by the spring element 92.

[0030] When brake fluid is drawn into the wheel brake cylinder 54, it flows from the line 38 through the intake valve 40 in an intake flow direction 104, which is determined by the arrangement of the inlet 78 or the valve inlet 80 and the arrangement of the outlet 82 from the motor side 70 to the control unit side 72. From the outlet 82, the brake fluid flows horizontally or laterally through the line 52 towards the inlet 84 or towards the valve inlet 86 of the outlet valve 46. In this case, the line 52 serves as an intermediate connection between the intake valve receptacle 62 and the outlet valve receptacle 64. When the outlet valve 46 is closed, the brake fluid flows through the line 52 by way of the branch 105 to the wheel brake cylinder 54, where it applies brake pressure to the associated wheel brake.

[0031] To release or release the brake pressure in the wheel brake cylinder 54 or to discharge brake fluid from the wheel brake cylinder 54, the discharge valve 46 is opened by applying an electric current. The brake fluid then flows from the wheel brake cylinder 54 through the line 52 through the discharge valve 46 in a discharge flow direction 106. In this case, the discharge flow direction 106 is determined by the arrangement of the inlet 84 or the valve inlet 86 and the arrangement of the outlet 90 or the valve outlet 88. The brake fluid therefore flows laterally upwards through the valve inlet 86 or the inlet 84 of the discharge valve 46 and downwards through the valve outlet 88 or the outlet 90 into the line 44. The discharge flow direction 106 thus runs from the control unit side 72 to the motor side 70 in relation to the axis 68 and at the same time runs in the opposite direction to the intake flow direction 104 in relation to the axis 66 or 68. Furthermore, when brake fluid is sucked into the discharge valve 46 through the inlet 84 or the valve inlet 86, the brake fluid flows in a discharge flow direction 106 transversely perpendicular to the axis 68 and thus perpendicular to the closing force 100 acting on the closing body 102 by the spring element 92. The discharge valve 46 is therefore only switchable, not controllable without further measures.

[0032] 3 to 7 show several embodiments of a pump housing 108, which for the most part comprises components having the same function as the pump housing 22. Accordingly, these components are provided with the same reference numbers.

[0033] In contrast to the pump housing 22, in the pump housing 108, the inlet 84 of the discharge valve holder 64 is positioned below or at the bottom of the cup-shaped discharge valve holder 64 or in the direction towards the motor side 70. In this case, the inlet 84 is arranged concentrically with respect to the cross section of the discharge valve holder 64 and thus axially with respect to the axis 68. Furthermore, the inlet 84 is connected to the line 52 in which the brake fluid is guided from the wheel brake cylinder 54 to the discharge valve holder 64. Furthermore, in the discharge valve 46 accommodated in the discharge valve holder 64, the valve inlet 86 is arranged corresponding to or at the inlet 84. In this arrangement, the brake fluid flows during intake through the valve inlet 86 along the axis 68 into the discharge valve 46 in a flow direction 110 acting axially against the closing force 100. The inlet 84 is therefore adapted to be guided so as to act axially against a closing force 100 exerted by the spring element 92 on the closing body 102 when brake fluid is sucked into the outlet valve 46. In this case, the spring element 92 is designed as a coil spring, the spring characteristic curve of which is adapted for appropriately controlling the brake pressure to be relieved from the wheel brake cylinder 54 by the outlet valve 46.

[0034] For the discharge of brake fluid from the discharge valve 46, the valve outlet 88 and the associated outlet 90 of the discharge valve seat 64 are arranged to the upper right in the direction towards the control unit side 72. Correspondingly, when the brake fluid is discharged from the wheel brake cylinder 54, it flows in a flow direction 110 from the inlet 84 to the outlet 90, or in a discharge flow direction from the motor side 70 to the control unit side 72. When drawn into the discharge valve 46, the flow direction 110 is directed relative to the axis 68 against the closing force 100.

[0035] Furthermore, a connecting line 112 or a connecting hole or a connecting passage is provided, which leads in a direction from the intake valve receiver 62 toward the discharge valve receiver 64. For this purpose, the connecting line 112 extends from the outlet 82 of the intake valve receiver 62, which is arranged on the upper right side or in a direction toward the control unit side 72, to the outside of the intake valve 40. Furthermore, the connecting line 112 extends to the wheel brake cylinder 54.

[0036] When brake fluid is drawn into the wheel brake cylinders 54, it is guided in this way and flows in the intake flow direction 104 from the motor side 70 to the control unit side 72 through the intake valve 40. The brake fluid then flows through the connecting line 112 into the wheel brake cylinders 54 and from there through the line 52 by the discharge valve 46 in the discharge flow direction 110 from the motor side 70 to the control unit side 72. In this case, the intake flow direction 104 and the discharge flow direction 110 are oriented in at least the same direction relative to the axis 68. The connecting line 112 therefore allows the intake valve 40 and the discharge valve 46 to flow through in the same flow directions 104 and 110 relative to the axis 68.

[0037] To this end, the connecting conduit 112 may have various embodiments, which are illustrated in Figures 4 to 7 only diagrammatically and without the outlet valve 40 and the inlet valve 46 for clarity.

[0038] According to FIGS. 3 and 4, the connecting line 112 is configured as a line section 114 which runs obliquely to the axis 68 of the outlet valve holder 64. The line section 114 and the axis 68 form an acute angle 118 therebetween. The connecting line 112 is also guided into a region 116 of the outlet valve holder 64 which is directed towards the wheel brake cylinder 54. The region 116 is arranged below or at the cup bottom 91. From this region 116, the brake fluid leaves the outlet valve holder 64 and is guided through the line 52 into the wheel brake cylinder 54 in order to draw the brake fluid into the wheel brake cylinder 54. To discharge the brake fluid from the wheel brake cylinder 54, the brake fluid is guided from below through the same line 52 into the outlet valve holder 64 and thus into the outlet valve 46 arranged in the outlet valve holder 64. For this purpose, the connecting line 112 is designed as a simple straight beveled hole.

[0039] According to FIG. 5, the connecting line 112 is likewise formed by a line section 114, which is guided obliquely in relation to the axis 68. In this case, an acute angle 120 is formed between the connecting line 112 and the axis 68, which is smaller than the acute angle 118. The connecting line 112 is therefore arranged more steeply than in the embodiment according to FIG. 4. Furthermore, the connecting line 112 is guided directly into the line 52 at a branch 122. The connecting line 112 is therefore designed as a simple inclined hole with a direct and steep slope, so that the distance between the intake valve 40 and the discharge valve 46 can be smaller than in the embodiment according to FIG. 4. In this case, the line 52 is located below the discharge valve seat 64 or in the direction towards the motor side 70. Furthermore, the line 52 is designed here as a wheel connection hole or a wheel passage.

[0040] 6 shows a connecting line 112 which, starting from the outlet 82 of the intake valve retainer 62, has a line section 114 inclined with respect to the axis 68, a first line section 124 arranged parallel with respect to the axis 68 and a second line section 126 arranged perpendicular to the axis 68. In this case, the second line section 126 is connected in a fluid-guiding manner to the line 52 at the branch 122. In this case, in relation to FIG. 6, the first line section 124 extends vertically and the second line section 126 extends horizontally.

[0041] 7 shows the connecting line 112, which starts from the outlet 82 and has a first horizontal second line section 126, a vertical first line section 124 and a second horizontal second line section 126. The second horizontal line section 126 leads into the line 52 at a branch 122. The outlet 82 is also oriented away from the discharge valve receptacle 64 or is arranged in the intake valve receptacle 62 on the side facing the wheel brake cylinder side 74. A space is thus obtained between the intake valve 40 and the discharge valve 46, in which space further components, such as a high-pressure changeover valve, can be integrated into the pump housing 108.

[0042] 3-7, all of the pipe sections 114, 124 and 126 lie in one plane and therefore extend in two dimensions of space. In another embodiment not shown, the pipe sections 114, 124 and 126 extend in three dimensions of space between the outlet 82 and the branch 122 or region 116.

[0043] In summary, the drillings in the pump housing 108 configured as a hydraulic block, in particular with respect to the connecting line 112, the inlet 84 and the outlet 90 of the delivery valve receptacle 64, have been modified in order to allow a simplified and therefore cost-optimized design of the controllable delivery valve 46. In this case, the additional costs due to the required bores and inclined bores are significantly overcompensated by the simplified design of the controllable delivery valve 46. [Explanation of symbols]

[0044] 10 Vehicle braking system 12 Brake pedal 14 Brake booster 16 Master cylinder 18,20 Brake circuit 22 Pump housing 23 Hydraulic unit 24 Conduit 26 High pressure switching valve 28 Switching valve 30 Pressure Sensor 32 Conduit 34 Pump element 36 Check valve 37 Drive motor 38 Pipeline 40 First intake valve 42 Second intake valve 44 Conduit 46 First discharge valve 48 Second Discharge Valve 50 Accumulator 52 Pipe or wheel brake cylinder pipe 53 Wheel brake cylinder connection 54 No. 1 Wheel Brake Cylinder 56 Pipe or wheel brake cylinder pipe 57 Wheel brake cylinder connection 58 No. 2 Wheel Brake Cylinder 60 Filter Element 62 Intake valve holder 64 Discharge valve receiver 66, 68 Longitudinal axis or axis 70 Motor side 72 Control unit side 74 Wheel brake cylinder side or side 76 Side 77 Bottom of Cup 78 Inlet 80 Valve Inlet 82 Outlet 84 Inlet 86 Valve Inlet 88 Valve Outlet 90 Outlet 91 Bottom of Cup 92 Spring element 94 Valve tappet 96 Sleeve 98 Valve seat 100 Closing force 102 Closed body 104 Intake flow direction 105 Branch 106 Discharge flow direction 108 Pump housing 110 Flow direction, discharge flow direction 112 Connecting pipes, connecting holes or connecting passages 114 Pipe classification 116 areas 118 Acute angle 120 Acute angle 122 Fork in the road 124 First Pipe Section 126 Second Pipe Section

Claims

1. A pump housing (108) of a hydraulic unit (23) of a vehicle braking system (10), comprising at least one wheel brake cylinder connection (53, 57) for connecting a wheel brake cylinder (54, 58) to said pump housing (108), a discharge valve receptacle (64) leading to the respective wheel brake cylinder connection (53, 57) for receiving a discharge valve (46, 48) provided for discharging brake fluid from said wheel brake cylinder (54) into said pump housing (108), and a valve inlet (86) closed with a predetermined closing force (100) by a closing body (102), wherein said discharge valve receptacle (64) comprises an inlet (84) for drawing brake fluid from said wheel brake cylinder (54) into said discharge valve (46), the inlet (84) is adapted to guide brake fluid in a flow direction (110) directed against the closing force (100) when sucking brake fluid into the discharge valve (46) when the discharge valve (46) is received in the discharge valve receiver (64); the discharge valve receiver (64) has an axis (68), and when the discharge valve (46) is received in the discharge valve receiver (64) and the inlet (84) is axially disposed relative to the axis (68), the closing force (100) acts along the axis (68); an intake valve receiver (62) for receiving an intake valve (40) for drawing brake fluid from the pump housing (108) into the wheel brake cylinder (54), the intake valve receiver (62) having an outlet (82) for drawing brake fluid from the intake valve (40) to the wheel brake cylinder (54), a connecting line (112) leading from the outlet (82) of the intake valve receiver (62) to the wheel brake cylinder (54), the connecting line (112) being adapted to allow flow through the intake valve (40) when drawing brake fluid into the wheel brake cylinder (54) and through the discharge valve (46) when discharging brake fluid from the wheel brake cylinder (54) in the same flow direction (104, 110) relative to the axis (68); 1. A pump housing comprising: a pump housing having a connecting line (112) extending in the axial direction (68) at least at a portion thereof leading to the inlet (84) of the discharge valve receptacle (64) and guided in a region (116) of the discharge valve receptacle (64) directed towards a wheel brake cylinder line (52, 56) leading to the wheel brake cylinder connection (53, 57).

2. 2. The pump housing of claim 1, wherein the discharge valve (46) is received in the discharge valve receiver (64), the discharge valve (46) having the valve inlet (86) closed by the closing body (102) with a predetermined closing force (100), the closing force (100) being exerted by a spring element (92).

3. 3. The pump housing according to claim 1, wherein the pump housing (108) is provided with a motor side (70) for arranging a drive motor (37) and a control unit side (72) for arranging a control unit, the control unit side being located opposite the motor side (70), and the inlet (84) is adapted to direct the flow direction (110) between the motor side (70) and the control unit side (72) against the closing force (100).

4. 4. The pump housing according to claim 1, wherein the connecting line (112) is configured with a line section (114) that is guided obliquely relative to the axis (68).

5. 5. The pump housing according to claim 1, wherein the connecting line (112) comprises at least one first line section (124) and at least one second line section (126), and wherein, in relation to the axis (68), the individual first line sections (124) are guided in parallel and the individual second line sections (126) are guided at right angles.

6. 6. Use of a pump housing, comprising: a pump housing according to any one of claims 1 to 5 being used in a hydraulic unit (23) of a vehicle brake system (10).

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