JP2011057204A - Regulating valve used for vehicle brake system, and suitable vehicle brake system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve regulation quality and reduce a control pressure required for operation of a regulating valve. <P>SOLUTION: A region 9 of a pressure-released connection path 8 having a compression spring 14 is disposed between a valve seat 17 and a control chamber 19 connected to a second fluid connection path 6. The control chamber 19 is partitioned by a control piston 12 of a control piston unit 10 movable in the longitudinal direction, and the pressure formed in the control chamber 19 is set so as to work against a spring force of a compression spring 14. In addition, an effective diameter D1 of the control piston 12 is formed to be larger than or equal to an effective diameter D2 of a closed element 11.1. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention is a regulating valve used in a vehicle brake system, and is provided with a first fluid connection path, a second fluid connection path, and a pressure-released connection path leading to the atmosphere. A longitudinally movable control piston unit is loaded with a predetermined spring force by a compression spring in the region of the pressure-released connection path, and in the starting position, a first fluid connection path and a second fluid connection The fluid connection between the channels is fully open and the closing element is adapted to cooperate with the valve seat, so that the effective pressure in the second fluid connection channel is the maximum settable It is related to the type that is limited to the pressure value.

  Furthermore, the present invention is a vehicle brake system, wherein a master brake cylinder, a fluid control unit, and at least one wheel brake are provided, and the fluid control unit is provided in at least one brake circuit. The present invention relates to a type having one switching valve, one suction valve, and one return pump for adjusting the braking pressure of one wheel brake.

  Based on the known prior art, vehicle brake systems are known. This known vehicle brake system has different safety systems, such as anti-lock brake system (ABS), electronic stability program (ESP), etc., and different safety functions, such as anti-lock function, traction control (ASR). ) Etc.

  German patent application DE 102007038397 describes, for example, a vehicle brake system. This vehicle brake system has one master brake cylinder, one fluid control unit, and four wheel brakes. Each of these wheel brakes has one attached wheel brake cylinder. Each two wheel brakes are assigned to one brake circuit. In this case, each brake circuit is connected to a master brake cylinder. The fluid control unit has one return pump, one switching valve, one suction valve, and one regulating valve for adjusting the braking pressure for each brake circuit. This adjusting valve is drawn into a suction line between the return pump and the master brake cylinder. The return pumps of both brake circuits can be formed, for example, as a piston pump or a gear pump. During ESP control, a braking pressure of up to 140 bar can be generated by a switched open suction valve. If braking must be performed by the system, this braking pressure loads the corresponding return pump suction side. Even in part-active system conditions, the return pump can be loaded up to 140 bar on the suction side. Furthermore, if the pressure of the master brake cylinder is guided to the return pump via an open switching valve and then increased via the corresponding return pump to the wheel pressure required for adjustment, An inlet pressure can be generated on the suction side of the return pump. In the configuration of the return pump as the piston pump, the high pressure acting on the seal member on the eccentric body side of the return pump can lead to extremely high wear, protrusion, and leakage. When a gear pump is used as the return pump, this high pressure loads the shaft seal ring of the return pump. This leads to an increase in friction and can lead to an increase in wear of the seal member as in the piston pump. In this case, the pressure-resistant shaft seal ring is extremely expensive.

  An additional regulating valve drawn into the suction line between the corresponding return pump and the master brake cylinder serves to limit the effective pressure on the suction side of the corresponding return pump, and thereby the corresponding return A pump is connected to the master brake cylinder via each regulating valve or suction valve on the suction side. That is, the regulating valve is connected in parallel to the suction valve, and the effective pressure on the suction side of the return pump is limited to the maximum settable pressure value. Such a regulating valve has a master brake cylinder connection path, a pump connection path, a pressure release connection path leading to the atmosphere, and a longitudinally movable piston. This longitudinally movable piston is formed as a stepped piston. The piston has a first diameter relative to the released connection path and a second diameter relative to the pump connection path. In this case, the second diameter is formed larger than the first diameter. The piston is sealed with respect to the housing via a seal ring with respect to the released connection path and the pump connection path. The transition of the piston from the first diameter to the second diameter is formed as a seal cone. The seal cone corresponds to a seal seat provided in the housing. The longitudinally movable piston is loaded with a predetermined spring force by the adjusting spring on the pressure-released side, and remains in the starting position without pressure. In this starting position, the fluid connection between the master brake cylinder connection path and the pump connection path, which is present via the piston hole, is completely open. During the ABS intervention, the piston is loaded from the side of the master brake cylinder connection with a pressure that moves the piston in the direction of the released connection against the spring force of the adjusting spring. When the maximum pressure value and corresponding contact position are reached, the seal cone of the piston is in close contact with the seal seat of the housing, and the connection between the master brake cylinder connection path and the pump connection path is completely blocked by the piston. Is done. As a result, the flow from the master brake cylinder to the return pump is blocked, and the fluid control unit can perform ABS control in this state.

  During the part-active state of the brake system, the regulating valve piston is loaded from the side of the master brake cylinder connection with a pressure that moves the piston in the direction of the released connection against the spring force of the adjustment spring. Is done. In this case, the fluid connection between the master brake cylinder connection path and the pump connection path is reduced by the piston motion. When the maximum pressure value is reached, the piston is located in the corresponding contact position. In this contact position, the connection between the master brake cylinder connection path and the pump connection path is completely blocked by the piston. This prevents further pressure increase on the return pump. When the current pressure in the regulating valve decreases below the maximum pressure value, the spring force of the regulating spring moves the piston from the contact position to the starting position. As a result, the connection between the master brake cylinder connection path and the pump connection path is opened again. This ensures that the pressure in the conduit leading to the master brake cylinder can be increased without increasing the pressure on the suction side of the return pump above the set maximum pressure value. During the ESP intervention, the regulator valve piston remains in the starting position. In this case, the return pump sucks fluid in parallel through the regulating valve and the suction valve in this state. In the regulating valve described in German Offenlegungsschrift DE 102007038397, the diameter of the piston, which is moved in the closing direction against the return spring via the formed control pressure, has a seal that receives the sealing cone. It is formed smaller than the diameter of the seat. Therefore, the control pressure for operating the regulating valve must be relatively high. In this case, the friction of the sealing element can lead to an increase in the hysteresis of the closing pressure.

German Patent Application No. 102007038397

  The object of the present invention is therefore to improve a regulating valve and vehicle brake system of the type mentioned at the outset so that the quality of the regulation is improved and the control pressure required to operate the regulating valve is reduced. It is to be.

  In order to solve this problem, in the regulating valve of the present invention, the region of the pressure-released connection path provided with the compression spring is provided between the valve seat and the control chamber connected to the second fluid connection path. The control chamber is partitioned by the control piston of the longitudinally movable control piston unit, and the pressure formed in the control chamber acts against the spring force of the compression spring. The effective diameter of the control piston is made larger than or equal to the effective diameter of the closure element.

  According to an advantageous embodiment of the regulator valve of the invention, the second fluid connection is connected to the control chamber directly or via at least one compensation passage.

  According to an advantageous embodiment of the regulating valve according to the invention, at least one compensation passage is arranged inside the control piston unit.

  According to an advantageous embodiment of the regulating valve according to the invention, the control piston is coupled to the closing element via a control slider, the control slider being connected between the control piston and the closing element in the released connection path. Bridge the area located in

  According to an advantageous aspect of the regulating valve of the present invention, the control slider is guided by the guide element, and the rod seal member is disposed between the first fluid connection path and the second fluid in the region of the connection path where the pressure is released. Seals against fluid flow to and from the connection.

  According to an advantageous embodiment of the regulating valve according to the invention, a sealing member is arranged on the control piston, which seals the area of the released connection path against the control chamber.

  According to an advantageous embodiment of the regulating valve of the invention, the sealing member is formed as a piston sealing member with a clamping element or as an annular sealing member.

  According to an advantageous aspect of the regulator valve of the present invention, the pressure formed in the first fluid connection path is adapted to act on the control piston against the spring force of the compression spring in the control chamber. The piston unit is adapted to move in the direction of the valve seat with a closing element, the fluid connection between the first fluid connection path and the second fluid connection path being connected to the control piston. When the fluid connection between the first fluid connection and the second fluid connection is at a set maximum pressure value in the second fluid connection. When it is completely blocked by the contact position of the closing element and the current pressure in the second fluid connection path decreases below the maximum pressure value, the spring force of the compression spring causes the control piston to contact the contact position. Luck again in the direction of the departure position And it is adapted to.

  According to an advantageous aspect of the regulating valve of the present invention, the first fluid connection path is formed as a master brake cylinder connection path connected to a master brake cylinder provided in the vehicle brake system, and the second fluid The connection path is formed as a pump connection path connected to the return pump.

  Further, in order to solve the above-described problems, in the vehicle brake system of the present invention, the suction valve is formed as a regulating valve according to the present invention, and each of the regulating valves includes a corresponding return pump, a master brake cylinder, It was made to draw in in the suction line between.

  The regulating valve according to the present invention for use in a vehicle brake system having the features of the independent claim 1 is provided with a compression seat and a region of the pressure-relieved connecting path, as compared with the conventional one. It is arranged between the control chamber connected to the second fluid connection path, this control chamber is partitioned by the control piston of the control piston unit movable in the longitudinal direction, and the pressure formed in the control chamber is Acting against the spring force of the compression spring, with the advantage that the effective diameter of the control piston is formed larger than or equal to the effective diameter of the closure element Yes. This closure element limits the effective pressure in the second fluid connection to the maximum settable pressure value and opens the fluid connection between the first fluid connection and the second fluid connection. To work with the valve seat. With the arrangement according to the invention of the regulating valve, the quality of the regulation can be improved and the required control pressure for operating the regulating valve can be reduced. A longitudinally movable control piston unit with a closing element is loaded with a predetermined spring force by a compression spring in the region of the released connection path. In this case, in the starting position, the fluid connection between the first fluid connection path and the second fluid connection path is completely open. The regulating valve according to the invention can take over the function of the suction valve, for example in the vehicle brake system described in DE 102007038397, and the return pump is advantageously raised on the suction side. It is possible to additionally protect against the applied inlet pressure.

  The embodiment of the regulating valve according to the invention advantageously has a slight flow resistance and a robust construction. The slight flow resistance inside the regulating valve according to the invention can be clearly recognized, especially at high viscosities or low temperatures. Furthermore, the structure of the regulating valve according to the invention is extremely robust and can therefore be used even at high pressures. The mechanical structure of the regulating valve according to the invention with fewer components and a stable structure is additionally advantageous in manufacturing and can be easily assembled. The first fluid connection path is formed, for example, as a master brake cylinder connection path connected to a master brake cylinder provided in the vehicle brake system, and the second fluid connection path is connected to, for example, a return pump. It is formed as a pump connection path.

  The vehicle brake system according to the invention with the features of the independent claim 10 comprises a master brake cylinder, a fluid control unit, and at least one wheel brake, the fluid control unit being in at least one brake circuit. In order to adjust the braking pressure of at least one wheel brake provided, each has one switching valve, one suction valve, and one return pump. The suction valve of the at least one brake circuit is advantageously formed as a regulating valve as described above according to the invention, which regulating valve is in the suction line between the respective return pump and the master brake cylinder. Has been drawn into. Therefore, the regulating valve according to the invention provided in the vehicle brake system advantageously takes over the function of the suction valve and additionally protects the return pump against the increased inlet pressure on the suction side. . By limiting the effective pressure on the suction side of the return pump, wear, friction, and protrusion of the seal member provided in the return pump can be reduced. This advantageously reduces the leakage of the return pump to the outside, increasing the efficiency and significantly extending the life of the return pump. Further, in the case of a return pump formed as a gear pump, an expensive and complicated pressure-resistant shaft seal ring is avoided, and an inexpensive shaft seal ring can be assembled.

  The measures and aspects described in the dependent claims enable an advantageous improvement of the regulating valve used in the vehicle braking system described in the independent claim 1.

  It is particularly advantageous if the second fluid connection is connected to the control chamber directly or via at least one compensation passage. Thereby, since the control piston unit is advantageously pressure compensated in the high pressure region, the valve can advantageously be controlled and opened by the return pump even when the pressure in the first fluid connection is high. . The at least one compensation passage may be arranged, for example, inside the control piston unit.

  In the configuration of the regulating valve according to the present invention, the control piston is coupled to the closing element via the control slider, and the control slider is disposed between the control piston and the closing element of the connection path where the pressure is released. Bridging the territory. The control slider may be guided by a guide element, and the rod seal member seals the area of the relieved connection path against the fluid flow between the first fluid connection path and the second fluid connection path. ing. The rod seal member advantageously prevents fluid from flowing into the region of the pressure-released connection path.

  In another configuration of the regulating valve according to the present invention, a seal member is disposed on the control piston, and this seal member seals the region of the released connection path to the control chamber. In this case, the seal member is formed with as low friction as possible, thereby ensuring all functions of the regulating valve. The sealing member is formed, for example, as a piston sealing member with a clamping element or as an annular sealing member. In the configuration as a piston seal member, the tightening element and the annular seal member serve to fix the piston seal member to the control piston.

  In another configuration of the regulating valve according to the present invention, the pressure formed in the first fluid connection path acts on the control piston against the spring force of the compression spring in the control chamber, and the control piston unit is closed by the closing element. Moving in the direction of the valve seat, the fluid connection between the first fluid connection and the second fluid connection can be reduced by movement of a closing element coupled to the control piston, The fluid connection between the connection channel and the second fluid connection channel is completely interrupted by the position of the closure element against the valve seat at the set maximum pressure value in the second fluid connection channel. When the current pressure in the second fluid connection path decreases below the maximum pressure value, the spring force of the compression spring causes the control piston to move again from the abutment position toward the starting position.

  The maximum pressure in the control chamber can be defined by the diameter ratio and the spring force of the compression spring. This maximum pressure can be adjusted, for example, to a pressure value in the range from 1 to 10 bar, preferably 2 bar. In order to keep the diameter and spring force as small as possible, the sealing member is formed to have as little friction as possible.

1 is a schematic cross-sectional view of a first embodiment of a regulating valve according to the present invention. It is a schematic sectional drawing of 2nd Embodiment of the regulating valve which concerns on this invention. It is a schematic sectional drawing of 3rd Embodiment of the regulating valve which concerns on this invention.

  In the following, embodiments for carrying out the present invention will be described in detail with reference to the drawings.

  In the following, various embodiments of the regulating valves 1, 1 ′, 1 ″ according to the present invention will be described in conjunction with FIGS. 1 to 3. In the first embodiment shown in FIG. 1, the regulating valve 1 is shown in an open starting state during the suction operation of a return pump (not shown). In the second embodiment shown in FIG. 2, the regulating valve 1 'is shown in a closed state. In the third embodiment shown in FIG. 3, the regulating valve 1 ″ is also shown in a closed state.

  As is apparent from FIGS. 1 to 3, the regulating valves 1, 1 ′, 1 ″ have first fluid connection paths 4, 4 ′, 4 ″ formed as master brake cylinder connection paths, respectively. It has second fluid connection paths 6, 6 ′, 6 ″ formed as pump connection paths and pressure-released connection paths 8, 8 ′, 8 ″ leading to the atmosphere. Further, the regulating valves 1, 1 ', 1 "have housings 2, 2', 2", respectively. The housings 2, 2 ', 2 "have valve seats 17, 17', 17" with sealing surfaces 17.1, 17.1 ', 17.1 ". The valve seats 17, 17 ′, 17 ″ may be formed as press-fitted members as in the illustrated embodiment, or milled directly into the housings 2, 2 ′, 2 ″ as contours. May be.

  Furthermore, as is clear from FIG. 1, the first embodiment of the regulating valve 1 according to the present invention has a control piston unit 10 movable in the longitudinal direction. The control piston unit 10 comprises a closing element 11.1 and a control piston 12. This control piston 12 is loaded with a predetermined spring force by a compression spring 14 in the region 9 of the released connection path 8, and at the starting position shown in the figure, the first fluid connection path 4 and the second fluid connection. The fluid connection with the passage 6 is completely open. The closing element 11.1 cooperates with the valve seat 17, which limits the effective pressure in the second fluid connection 6 to the maximum settable pressure value. According to the invention, the region 9 of the released connection path 8 with the compression spring 14 is arranged between the valve seat 17 and the control chamber 19 connected to the second fluid connection path 6. ing. The control chamber 19 is partitioned by the control piston 12 of the control piston unit 10 that is movable in the longitudinal direction. Further, the control chamber 19 is partitioned by the housing 2 and the cover 18 that has been crimped. The pressure formed in the control chamber 19 acts against the spring force of the compression spring 14 and the effective diameter D1 of the control piston 12 is formed larger than the effective diameter D2 of the closing element 11.1 or the closing element. It is formed equal to an effective diameter D2 of 11.1. This advantageously makes it possible to improve the quality of the regulation or to reduce the control pressure for operating the regulating valve 1. Furthermore, the control piston 12 is provided with a seal member 13 formed as a piston seal member 13.1. This seal member 13 seals the region 9 of the released connection path 8 against the control chamber 19. The piston seal member 13.1 is fixed to the control piston 12 by means of a clamping element 13.2 and an annular seal member 13.3. Furthermore, this control piston 12 is connected via a control slider 11 to the closing element 11.1. In this case, the control slider 11 bridges the region 9 of the connection path 8 which has been released, which is arranged between the control piston 12 and the closing element 11.1.

  Furthermore, as is clear from FIG. 1, the control slider 11 is guided by a guide element 15. This guide element 15 has a seal member accommodating portion 15.1 for accommodating a rod seal member 16 formed as an annular seal member, whereby the region 9 of the released connection path 8 is In the closed state, it is sealed against the first fluid connection path 4, and in the opened state, it is sealed against the fluid flow between the first fluid connection path 4 and the second fluid connection path 6. Is done.

  Furthermore, as is clear from FIG. 1, the second fluid connection path 6 is connected to the control chamber 19 via a compensation path 11.2 arranged inside the control piston unit 10. As a result, the pressure formed in the first fluid connection path 4 acts on the control piston 12 against the spring force of the compression spring 14 in the control chamber 19, and the control piston unit 10 is valved by the closing element 11.1. It moves in the direction of the seat 17. In this case, the fluid connection between the first fluid connection 4 and the second fluid connection 6 can be reduced by the movement of the closing element 11.1 coupled to the control piston 12. In this case, the fluid connection portion between the first fluid connection path 4 and the second fluid connection path 6 is connected to the valve seat 17 in the case of the maximum pressure value set in the second fluid connection path 6. It is completely blocked by the contact position (not shown) of the closing element 11.1. When the current pressure in the second fluid connection 6 decreases below the maximum pressure value, the spring force of the compression spring 14 causes the control piston 12 to move again from the abutment position toward the starting position. The piston seal member 13.1 is desirably formed as low friction as possible in order to ensure the functions of all the regulating valves 1. The guide element 15 and the seal member accommodating portion 15.1 guide the control slider 11 and hold the rod seal member 16. This rod sealing member 16 advantageously prevents the outflow of fluid into the region 9 of the pressure-released connection path 8.

  During operation, the first diameter D1 of the control piston 12 can be loaded at a predetermined pressure from the side of the master brake cylinder connection path 4 via the compensation path 11.2. This pressure causes the control piston 12 with the control slider 11 and the closing element 11.1 having the second diameter D2 to move in the direction of the valve seat 17 against the spring force of the compression spring 14, and then The closing element 11.1 formed as a sealing cone contacts the sealing surface 17.1 of the valve seat 17. When the maximum pressure value and the corresponding contact position are reached, the closing element 11.1 formed as a sealing cone is in close contact with the valve seat 17 and between the master brake cylinder connection path 4 and the pump connection path 6. The fluid connection is completely interrupted. In this case, a fluid control unit (not shown) can perform, for example, ABS adjustment in this state. The maximum pressure value can be adjusted, for example, to a pressure value in the range from 1 to 10 bar, preferably 2 bar. Since the diameter D2 of the closing element 11.1 and the diameter d2 of the sealing surface 17.1 can be designed to be equal, it is possible to maintain a higher pressure in the master brake cylinder after the regulating valve 1 is closed. it can. In this case, high pressure does not reach the inlet of the return pump (not shown). This ensures that the pressure in the pipeline leading to the master brake cylinder can be increased without raising the pressure on the suction side of the return pump above the set maximum pressure value. For example, when the return pump sucks and the current pressure in the pump connection 6 is reduced, the spring force of the compression spring 14 causes the control piston 12 to move in the direction from the abutment position to the starting position at the closing element 11.1. . Thus, the connection between the master brake cylinder connection path 4 and the pump connection path 6 is opened again until the maximum pressure value is achieved by operating the master brake cylinder. Thus, although the return pump always has an inlet pressure, it continues to be protected against the high pressure of the master brake cylinder. In the ESP case, the regulating valve 1 continues to open and the brake fluid can be sucked in by the return pump without interruption. Since the control piston 12 is pressure compensated in the high pressure region, the regulating valve 1 can be controlled and opened by the return pump even when the pressure of the master brake cylinder is high.

  The desired maximum effective pressure in the second fluid connection path 6 can be set, for example, by changing the diameter ratio and changing the spring force of the compression spring 14 when the regulator valve 1 is manufactured. Thus, for example, in addition to the diameter D1 of the control piston 12 and the diameter D2 of the closing element 11.1, the diameter d3 of the second fluid connection path 6, the diameter d1 of the compensation path 11.2, and the sealing surface 17.1. The diameter d2 of the control valve 1 can be set in accordance with a desired usage pattern of the regulating valve 1.

  Further, as is clear from FIG. 2, the second embodiment of the regulating valve 1 ′ according to the present invention is similar to the first embodiment shown in FIG. It has a unit 10 '. This control piston unit 10 'comprises a closing element 11.1' and a control piston 12 '. The control piston 12 ′ is loaded with a predetermined spring force by a compression spring 14 ′ in the region 9 ′ of the released connection path 8 ′, and in the illustrated contact position, the first fluid connection path 4 ′. And the fluid connection between the second fluid connection 6 'is completely blocked. The closing element 11.1 'cooperates with the valve seat 17', which limits the effective pressure in the second fluid connection 6 'to the maximum settable pressure value. According to the invention, the region 9 'of the released connection path 8' with the compression spring 14 'is connected to the valve seat 17' and the second fluid connection path 6 'in the control chamber 19'. It is arranged between. Similar to the first embodiment, the control chamber 19 'is partitioned by a control piston 12' of the longitudinally movable control piston unit 10 ', a housing 2', and a crimped cover 18 '. It has been. Unlike the first embodiment, the second fluid connection path 6 ′ is directly connected to the control chamber 19 ′, and is connected between the first fluid connection path 4 ′ and the second fluid connection path 6 ′. The fluid connection is a compensation that is arranged inside the control piston unit 10 'when the pressure in the control chamber 19' or the pressure in the second fluid connection 6 'falls below a set maximum pressure value. Formed through passage 11.2 '. In this case, the pressure formed in the control chamber 19 ′ or the pressure formed in the second fluid connection path 6 ′ acts against the spring force of the compression spring 14 ′, and the effective diameter of the control piston 12 ′ is It is formed larger than the effective diameter of the closure element 11.1 ′ or equal to the effective diameter of the closure element 11.1 ′. As a result, similar to the first embodiment, it is possible to improve the quality of adjustment or reduce the control pressure for operating the adjustment valve 1 '. Furthermore, a seal member 13 'formed as an annular seal member is arranged on the control piston 12'. The sealing member 13 'seals the region 9' of the released connection path 8 'against the control chamber 19'. Furthermore, the control piston 12 'is coupled to the closing element 11.1' via a control slider 11 '. In this case, the control slider 11 ′ bridges the region 9 ′ of the connection path 8 ′ that is released between the control piston 12 ′ and the closing element 11.1 ′.

  Furthermore, as is clear from FIG. 2, the control slider 11 'is guided by a guide element 15'. This guide element 15 ′ has a seal member accommodating portion 15.1 ′ for accommodating a rod seal member 16 ′ formed as an annular seal member, and thereby the pressure of the released connection path 8 ′. In the closed state, the region 9 ′ is sealed with respect to the first fluid connection path 4 ′, and in the open state, the region 9 ′ is connected between the first fluid connection path 4 ′ and the second fluid connection path 6 ′. Sealed against fluid flow between.

  Further, as is apparent from FIG. 2, the control chamber 19 ′ or the second fluid connection 6 ′ is connected to the first fluid via the compensation passage 11.2 ′ arranged inside the control piston unit 10 ′. It can be connected to the connection path 4 ′. As a result, the pressure formed in the first fluid connection path 4 'acts on the control piston 12' against the spring force of the compression spring 14 'in the control chamber 19', thereby closing the control piston unit 10 '. The element 11.1 ′ is moved from the starting position (not shown) in the direction of the valve seat 17 ′. In this case, the fluid connection between the first fluid connection 4 'and the second fluid connection 6' is reduced by the movement of the closing element 11.1 'coupled to the control piston 12'. In this case, the fluid connection between the first fluid connection path 4 ′ and the second fluid connection path 6 ′ is a valve at the maximum pressure value set in the second fluid connection path 6 ′. It is completely blocked by the illustrated abutment position of the closing element 11.1 ′ with respect to the seat 17 ′. When the current pressure in the second fluid connection 6 'decreases below the maximum pressure value, the spring force of the compression spring 14' causes the control piston 12 'to move again from the abutment position toward the starting position. The guide element 15 'and the seal member housing 15.1' guide the control slider 11 'and hold the rod seal member 16'. This rod sealing member 16 'advantageously prevents the outflow of fluid to the region 9' of the pressure-released connection path 8 '.

  During operation, the control piston 12 'can be loaded at a predetermined pressure from the side of the master brake cylinder connection 4' via the compensation passage 11.2 '. This pressure causes the control piston 12 'with the control slider 11' and the closing element 11.1 'to move in the direction of the valve seat 17' against the spring force of the compression spring 14 ', after which the sealing cone The closing element 11.1 ′ formed as follows contacts the sealing surface 17.1 ′ of the valve seat 17 ′. When reaching a pressure value, for example in the range from 1 to 10 bar, preferably a maximum pressure value that can be adjusted to 2 bar and the corresponding contact position, the closure element 11.1 ′ formed as a sealing cone The fluid connection between the master brake cylinder connection path 4 ′ and the pump connection path 6 ′ is completely cut off, in close contact with the valve seat 17 ′. In this case, a fluid control unit (not shown) can perform, for example, ABS adjustment in this state. Since the diameter of the closing element 11.1 ′ and the diameter of the sealing surface 17.1 ′ can be designed to be equal, the higher pressure of the master brake cylinder can be maintained after the regulating valve 1 ′ is closed. Can do. In this case, high pressure does not reach the inlet of the return pump (not shown). This ensures that the pressure in the pipeline leading to the master brake cylinder can be increased without increasing the pressure on the suction side of the return pump above the set maximum pressure value. For example, when the return pump sucks and the current pressure in the pump connection 6 ′ is reduced, the spring force of the compression spring 14 ′ causes the control piston 12 ′ to move from the abutment position to the starting position with the closing element 11.1 ′. Move in the direction. As a result, the connection between the master brake cylinder connection path 4 'and the pump connection path 6' is opened again by operating the master brake cylinder until the maximum pressure value is achieved. Therefore, the return pump is always protected against the high pressure of the master brake cylinder, although the return pump always has the inlet pressure in the illustrated second embodiment. In the ESP case, the regulating valve 1 'continues to open and the brake fluid can be sucked in by the return pump without interruption.

  Similar to the first embodiment, the desired maximum effective pressure in the second fluid connection path 6 ′ is, for example, a change in the diameter ratio and the spring force of the compression spring 14 ′ when the regulating valve 1 ′ is manufactured. Can be set by changing.

  Further, as apparent from FIG. 3, the third embodiment of the regulating valve 1 ″ according to the present invention is similar to the first embodiment shown in FIG. It has a piston unit 10 ''. This control piston unit 10 "has a closing element 11.1" and a control piston 12 ". The control piston 12 ″ is loaded with a predetermined spring force by a compression spring 14 ″ in the region 9 ″ of the released connection path 8 ″, and in the illustrated contact position, the first fluid The fluid connection between the connection channel 4 ″ and the second fluid connection channel 6 ″ is completely interrupted. The closing element 11.1 "cooperates with the valve seat 17", which limits the effective pressure in the second fluid connection 6 "to the maximum settable pressure value. According to the present invention, the region 9 '' of the released connection path 8 '' with the compression spring 14 '' is connected to the valve seat 17 '' and the second fluid connection path 6 ''. Between the control room 19 ″. The control chamber 19 ″ is partitioned by the control piston 12 ″ of the longitudinally movable control piston unit 10 ″, the housing 2 ″, and the cover 18 ″ that has been crimped. The pressure formed in the control chamber 19 ″ acts against the spring force of the compression spring 14 ″, and the effective diameter of the control piston 12 ″ is greater than the effective diameter of the closing element 11.1 ″. Or is formed equal to the effective diameter of the closure element 11.1 ''. As a result, similar to the first and second embodiments, it is possible to improve the quality of adjustment or reduce the control pressure for operating the adjustment valve 1 ″. Furthermore, a seal member 13 "formed as a piston seal member 13.1" is arranged on the control piston 12 ", similar to the first embodiment. The sealing member 13 ′ seals the region 9 ″ of the released connection path 8 ″ against the control chamber 19 ″. The piston seal member 13.1 "is fixed to the control piston 12" by a clamping element 13.2 "and an annular seal member 13.3". Furthermore, this control piston 12 "is coupled to the closing element 11.1" via a control slider 11 ". In this case, the control slider 11 ″ bridges the region 9 ″ of the connection path 8 ″ that is released between the control piston 12 ″ and the closing element 11.1 ″. .

  Furthermore, as is clear from FIG. 3, the control slider 11 "is guided by a guide element 15", similar to the first embodiment. This guide element 15 '' has a seal member receiving part 15.1 '' for receiving a rod seal member 16 '' formed as an annular seal member. The 8 ″ region 9 ″ is sealed to the first fluid connection 4 ″ in the closed state, and in the open state, the first fluid connection 4 ″ and the second fluid connection 4 ″. Sealed against fluid flow to the fluid connection 6 ″.

  Further, as is apparent from FIG. 3, the second fluid connection path 6 ″ differs from the first embodiment through a compensation path 11.2 ″ arranged in the housing 2 ″. Connected to the control room 19 ''. As a result, the pressure formed in the first fluid connection path 4 ″ acts on the control piston 12 ″ against the spring force of the compression spring 14 ″ in the control chamber 19 ″, and the control piston unit 10 "" Is moved in the direction of the valve seat 17 "by means of the closing element 11.1". In this case, the fluid connection between the first fluid connection path 4 ″ and the second fluid connection path 6 ″ is caused by the movement of the closing element 11.1 ″ coupled to the control piston 12 ″. Can be reduced. In this case, the fluid connection portion between the first fluid connection path 4 ″ and the second fluid connection path 6 ″ has the maximum pressure value set in the second fluid connection path 6 ″. In addition, it is completely blocked by the illustrated abutment position of the closing element 11.1 ″ with respect to the valve seat 17 ″. When the current pressure in the second fluid connection 6 ″ decreases below the maximum pressure value, the spring force of the compression spring 14 ″ causes the control piston 12 ″ to move from the abutting position again to the starting position (not shown). )). It is desirable that the piston seal member 13.1 "is formed with as low friction as possible in order to ensure the functions of all the regulating valves 1". The guide element 15 "and the seal member housing 15.1" guide the control slider 11 "and hold the rod seal member 16". This rod seal member 16 "advantageously prevents the outflow of fluid into the region 9" of the released connection path 8 ".

  During operation, the first diameter of the control piston 12 '' is similar to that of the first embodiment by a predetermined passage from the master brake cylinder connection path 4 '' side through the compensation path 11.2 ''. Can be loaded with pressure. This pressure causes the control piston 12 ″ with control slider 11 ″ and the closing element 11.1 ″ to move in the direction of the valve seat 17 ″ against the spring force of the compression spring 14 ″, Thereafter, the closing element 11.1 ″, formed as a sealing cone, comes into contact with the sealing surface 17.1 ″ of the valve seat 17 ″. Closure element 11.1 '' formed as a sealing cone when a pressure value in the range of 1 to 10 bar, for example, a maximum pressure value which can be adjusted to 2 bar and the corresponding abutment position is reached. Closely contacts the valve seat 17 '', and the fluid connection between the master brake cylinder connection path 4 '' and the pump connection path 6 '' is completely cut off. In this case, a fluid control unit (not shown) can perform, for example, ABS adjustment in this state. Since the diameter of the closing element 11.1 ″ and the diameter of the sealing surface 17.1 ″ can be designed to be equal, the higher pressure of the master brake cylinder is applied after the regulating valve 1 ″ is closed. Can be held. In this case, high pressure does not reach the inlet of the return pump (not shown). As a result, even in the third embodiment, the pressure in the pipeline leading to the master brake cylinder can be increased without increasing the pressure on the suction side of the return pump above the set maximum pressure value. It is ensured that it can be done. For example, when the return pump draws in and the current pressure in the pump connection 6 ″ is reduced, the spring force of the compression spring 14 ″ causes the control piston 12 ″ to abut the closing element 11.1 ″. Move from to the starting position. Thereby, the connection between the master brake cylinder connection path 4 ″ and the pump connection path 6 ″ is opened again by operating the master brake cylinder until the maximum pressure value is achieved. Thus, although the return pump always has an inlet pressure, it continues to be protected against the high pressure of the master brake cylinder. In the ESP case, the regulating valve 1 '' continues to open and the brake fluid can be sucked in by the return pump without being disturbed. Since the control piston 12 ″ is pressure compensated in the high pressure region, the regulating valve 1 ″ can be controlled and opened by the return pump even when the pressure of the master brake cylinder is high.

  Similar to the first embodiment, the desired maximum effective pressure in the second fluid connection path 6 ″ is, for example, a change in the diameter ratio and the compression spring 14 ″ when the regulating valve 1 ″ is manufactured. It can be set by changing the spring force.

  Embodiments of the present invention each provide a regulating valve that allows a reduction in flow resistance, a reduction in the number of components, and simpler assembly.

1, 1 ', 1 "Regulating valve 2, 2', 2" Housing 4, 4 ', 4 "First fluid connection 6, 6, 6', 6" Second fluid connection 8, 8 ', 8''pressure-released connection path 9, 9', 9 '' area 10, 10 ', 10 "control piston unit 11, 11', 11" control slider 11.1, 11.1 ', 11.1 "Closing element 11.2, 11.2 ', 11.2" Compensation passage 12, 12', 12 "Control piston 13, 13 ', 13" Sealing member 13.1, 13.1 '' Piston seal member 13.2, 13.2 '' Tightening element 13.3, 13.3 '' Annular seal member 14, 14 ', 14''Compression spring 15, 15', 15 '' Guide element 15. 1, 15.1 ′, 15.1 ″ Seal member receiving portion 16, 16 ′, 16 ″ Rod seal member 17, 17 ′, 17 ″ Valve seat 17.1, 17.1 ′, 17 1 ″ sealing surface 18, 18 ′, 18 ″ cover 19, 19 ′, 19 ″ control chamber D1 diameter of control piston D2 diameter of closing element d1 diameter of compensation passage d2 diameter of sealing surface d3 second fluid connection Road diameter

Claims (10)

  A regulating valve used in a vehicle brake system, which includes a first fluid connection path (4, 4 ′, 4 ″), a second fluid connection path (6, 6 ′, 6 ″), and air. A longitudinally movable control with a closed element (11.1, 11.1 ′, 11.1 ″) provided with a pressure-released connection (8, 8 ′, 8 ″) leading to it The piston units (10, 10 ′, 10 ′) are connected to the compression springs (14, 14 ′, 14 ″) with a predetermined spring force, and in the starting position, the first fluid connection (4, 4 ′, 4 ″) and the second fluid connection (6, 6 ′, 6 ′). ') Is completely open, and the closing element (11.1, 11.1', 11.1 '') is connected to the valve seat (17, 17 '). 17 ″) so that the effective pressure in the second fluid connection (6, 6 ′, 6 ″) is limited to the maximum settable pressure value. In the region (9, 9 ′, 9) of the pressure-released connection (8, 8 ′, 8 ″) with compression springs (14, 14 ′, 14 ″). '') Is connected to the valve seat (17, 17 ′, 17 ″) and the second fluid connection (6, 6 ′, 6 ″) to the control chamber (19, 19 ′, 19 ″). And the control chamber (19, 19 ′, 19 ″) is connected to the control piston (12, 12 ′, 10 ′) of the longitudinally movable control piston unit (10, 10 ′, 10 ′). 12 ″) and the pressure formed in the control chamber (19, 19 ′, 19 ″) is compressed by the compression springs (14, 14 ′, 4 ″) against the spring force, and the effective diameter (D1) of the control piston (12, 12 ′, 12 ″) is the closing element (11.1, 11.1 ′). , 11.1 ″) or larger than the effective diameter (D2) of the closure element (11.1, 11.1 ′, 11.1 ″). A regulating valve for use in a vehicle brake system.   The second fluid connection (6, 6 ′, 6 ″) is connected to the control chamber (19, 19 ′, 19) directly or via at least one compensation passage (11.2, 11.2 ″). The regulating valve according to claim 1 connected to '').   3. The regulating valve according to claim 2, wherein at least one compensation passage (11.2, 11.2 ') is arranged inside the control piston unit (10, 10', 10 ').   The control piston (12, 12 ′, 12 ″) is coupled to the closure element (11.1, 11.1 ′, 11.1 ″) via the control slider (11, 11 ′, 11 ″). The control slider (11, 11 ′, 11 ″) between the control piston (12, 12 ′, 12 ″) and the closing element (11.1, 11.1 ′, 11.1 ″). 4. The bridge according to claim 1, which bridges the region (9, 9 ′, 9 ″) of the pressure-released connection path (8, 8 ′, 8 ″) arranged in between. The regulating valve described in the item.   The control slider (11, 11 ′, 11 ″) is guided by the guide element (15, 15 ′, 15 ″), and the rod seal member (16, 16 ′, 16 ″) is released. The region (9, 9 ′, 9 ″) of the connection channel (8, 8 ′, 8 ″) is divided into the first fluid connection channel (4, 4 ′, 4 ″) and the second fluid connection channel ( 6. The regulating valve according to claim 4, wherein the regulating valve is sealed against fluid flow between 6,6 'and 6' ').   Seal members (13, 13 ′, 13 ″) are arranged on the control pistons (12, 12 ′, 12 ″), and the seal members (13, 13 ′, 13 ″) are released. 6. The region (9, 9 ′, 9 ″) of the connecting channel (8, 8 ′, 8 ″) is sealed against the control room (19, 19 ′, 19 ″). The regulating valve according to any one of the preceding items.   The sealing member (13, 13 ″) is formed as a piston sealing member (13.1, 13.1 ″) with clamping elements (13.2, 13.2 ″) or an annular sealing member The regulating valve according to claim 6, formed as   The pressure formed in the first fluid connection (4, 4 ′, 4 ″) is applied to the control piston (12, 12 ′, 12 ″) in the control chamber (19, 19 ′, 19 ″). Acting against the spring force of the compression springs (14, 14 ′, 14 ″), the control piston unit (10, 10 ′, 10 ′) is connected to the closing element (11.1, 11.1). ', 11.1 ") is moved in the direction of the valve seat (17, 17', 17"), and the first fluid connection (4, 4 ', 4 ") and the first The fluid connection between the two fluid connections (6, 6 ', 6 ") is connected to a control piston (12, 12', 12") with a closure element (11.1, 11.1). ', 11.1 ") and can be reduced by the first fluid connection (4,4', 4 '') and the second fluid connection (6,6 '). 6 ″) when the fluid connection between the second fluid connection (6, 6 ′, 6 ″) is at the set maximum pressure value, the valve seat (17, 17 ′, 17 '') Is completely blocked by the contact position of the closing element (11.1, 11.1 ′, 11.1 ″) with respect to the second fluid connection (6, 6 ′, 6 ″) When the current pressure decreases below the maximum pressure value, the spring force of the compression springs (14, 14 ′, 14 ″) causes the control pistons (12, 12 ′, 12 ″) to come into contact with each other. The regulating valve according to any one of claims 1 to 7, wherein the regulating valve is moved again in the direction of the starting position.   The first fluid connection path (4, 4 ′, 4 ″) is formed as a master brake cylinder connection path connected to a master brake cylinder provided in the vehicle brake system, and the second fluid connection path ( The regulating valve according to claim 1, wherein 6, 6 ′, 6 ″) is formed as a pump connection path connected to a return pump.   A vehicle brake system, comprising a master brake cylinder, a fluid control unit, and at least one wheel brake, wherein the fluid control unit brakes at least one wheel brake provided in at least one brake circuit. In order to adjust the pressure, the suction valve (1, 1) is of a type having one switching valve, one suction valve (1, 1 ′, 1 ″) and one return pump. ', 1' ') is formed as a regulating valve according to any one of claims 1 to 9, wherein the regulating valve is a suction pipe between the corresponding return pump and the master brake cylinder, respectively. A vehicle brake system characterized by being pulled into the road.

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