Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
  • F16K31/00—Actuating devices; Operating means; Releasing devices
  • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
  • F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
  • F16K31/1221—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston one side of the piston being spring-loaded
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
  • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
  • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
  • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
  • B60T8/341—Systems characterised by their valves
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
  • B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
  • B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
  • B60T11/28—Valves specially adapted therefor
  • B60T11/34—Pressure reducing or limiting valves
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
  • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
  • B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
  • B60T13/66—Electrical control in fluid-pressure brake systems
  • B60T13/68—Electrical control in fluid-pressure brake systems by electrically-controlled valves
  • B60T13/686—Electrical control in fluid-pressure brake systems by electrically-controlled valves in hydraulic systems or parts thereof
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
  • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
  • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
  • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
  • B60T8/48—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition connecting the brake actuator to an alternative or additional source of fluid pressure, e.g. traction control systems
  • B60T8/4809—Traction control, stability control, using both the wheel brakes and other automatic braking systems
  • B60T8/4827—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems
  • B60T8/4863—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems closed systems
  • B60T8/4872—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems closed systems pump-back systems
• • G—PHYSICS
  • G05—CONTROLLING; REGULATING
  • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
  • G05D16/00—Control of fluid pressure
  • G05D16/04—Control of fluid pressure without auxiliary power
  • G05D16/10—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger
  • G05D16/103—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger the sensing element placed between the inlet and outlet
  • G05D16/106—Sleeve-like sensing elements; Sensing elements surrounded by the flow path
• • G—PHYSICS
  • G05—CONTROLLING; REGULATING
  • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
  • G05D16/00—Control of fluid pressure
  • G05D16/14—Control of fluid pressure with auxiliary non-electric power
  • G05D16/16—Control of fluid pressure with auxiliary non-electric power derived from the controlled fluid
  • G05D16/166—Control of fluid pressure with auxiliary non-electric power derived from the controlled fluid using pistons within the main valve
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
  • Y10T137/00—Fluid handling
  • Y10T137/7722—Line condition change responsive valves
  • Y10T137/7781—With separate connected fluid reactor surface
  • Y10T137/7793—With opening bias [e.g., pressure regulator]

Definitions

• the invention is based on a hydraulically actuated control valve for a vehicle brake system according to the preamble of independent claim 1 and an associated vehicle brake system with at least one such
• the published patent application DE 10 2007 038 397 A1 describes a brake system for a vehicle.
• the brake system described comprises a fluid control unit with a slide valve, which is in a suction line between a
• the slide valve described is integrated directly into a bore of a fluid block and comprises two fluid ports and a pressure-relieved connection to the atmosphere, wherein a longitudinally movable piston is acted upon by a spring disposed outside of a Fluidström- pressure spring with a spring force and in a starting position via a Inner bore completely releases the fluid connection between the two fluid ports and completely locks in an end position.
• the published patent application DE 10 2008 002 539 A1 describes a control valve for a vehicle brake system with a first fluid connection, a second fluid connection and a pressure-relieved connection to the atmosphere.
• the described control valve comprises a longitudinally movable control piston, which on the pressure-relieved side of one outside the fluid flow arranged adjusting spring is acted upon by a spring force and completely releases a fluid connection between the first fluid port and the second fluid port in an initial position.
• the control valve comprises a valve body with a sealing seat and a sealing element coupled to the control piston via a sealing seat by the sealing seat sealing element, wherein a
• Sealing portion of the sealing member cooperates with the sealing seat of the valve body to limit an effective pressure at the second fluid port to a predetermined maximum pressure value.
• an effective diameter of the control piston is made greater than or equal to an effective diameter of the sealing element.
• German Offenlegungsschrift 10 2009 027 706 A1 describes a control valve for a vehicle brake system having a first fluid connection, a second fluid connection and a pressure-relieved connection to the atmosphere.
• the control valve described comprises a longitudinally movable control piston unit with a closing element, which is acted upon in the region of the pressure-relieved connection by a spring disposed outside the fluid flow compression spring and completely releases a fluid connection between the first fluid port and the second fluid port in an initial position.
• the closure member cooperates with a valve seat to limit effective pressure at the second fluid port to a predetermined maximum pressure value.
• the region of the pressure-relieved connection with the compression spring is arranged between the valve seat and a control chamber (19) connected to the second fluid connection, which is delimited by a control piston of the longitudinally movable control piston unit.
• the pressure built up in the control chamber acts against the spring force of the compression spring, and an effective diameter of the control piston is made greater than or equal to an effective diameter of the closure member. Disclosure of the invention
• the hydraulic control valve according to the invention for a vehicle brake system with the features of independent claim 1 and the associated vehicle brake system on the other hand have the advantage that the control valve has a simple, mostly consisting of sleeves valve assembly and hydraulic pressure applied due to Druck vomunter- is moved against a spring force.
• the pressure area difference may be translated by a plunger which, alone or in combination with at least one gasket, forms an effective first diameter at a first area which, in conjunction with applied pressure, supports movement of the plunger in a first direction and at a second area forms an effective second diameter which is equal to or smaller than the first diameter and, in conjunction with an applied pressure, assists movement of the plunger in a second direction opposite to the first direction.
• Embodiments of the present invention provide a hydraulically actuated control valve for a vehicle brake system that includes a first fluid port and a second fluid port and a control chamber.
• a longitudinally movable plunger with a sealing geometry is acted upon by a compression spring with a spring force and held in a starting position, wherein a pressure built up in the control chamber acts against the spring force of the compression spring and moves the plunger with the sealing geometry from the starting position to an end position, wherein the sealing geometry cooperates with a valve seat which is arranged in a valve body in order to limit an effective pressure at the second fluid connection to a predefinable maximum pressure value.
• a fluid connection between the first fluid port and the second fluid port is completely released in a first end position of the plunger and completely interrupted in a second end position of the plunger.
• the plunger is guided in a first sleeve, and the valve body and the first and second fluid connection are arranged in a second sleeve, which is fluid-tightly connected to the first sleeve.
• the plunger in the region of the control chamber forms an effective first diameter which, in conjunction with an applied pressure, supports a movement of the plunger in a first direction
• an effective second diameter which is equal to or smaller than the first Diameter is and in conjunction with an applied pressure supports a movement of the plunger in a second direction, which is opposite to the first direction.
• Embodiments of the control valve according to the invention can be executed both as normally open and as normally closed 2/2 valves. the.
• the longitudinally movable plunger is acted upon by the compression spring with a spring force and held in an open starting position in which the fluid connection between the first fluid port and the second fluid port is completely released.
• a pressure built up in the control chamber acts against the spring force of
• a vehicle brake system comprises a master brake cylinder, a fluid control unit and at least one wheel brake, the fluid control unit for brake pressure modulation of the at least one wheel brake in at least one brake circuit each comprising a changeover valve, an intake valve and a return pump.
• the intake valve is designed as a hydraulically actuated control valve according to the invention, which in each case in a suction line between the corresponding return pump and the
• the compression spring is surrounded by the operating medium and is supported on the second sleeve. This is beneficial in avoiding spring corrosion. Furthermore, the plunger is so results in that it is arranged with respect to the valve seat or valve body on one side and does not penetrate the valve seat.
• control pressure in the control chamber can be constructed, for example, via at least one inner bore in the plunger or via a third fluid connection.
• the inner bore in the plunger advantageously allows a simple fluid guide in the fluid block, in which the control valve is installed.
• the plunger can be made without an internal bore and the effective diameter can be easily increased.
• the fluid management can be simplified within the control valve.
• the compression spring can be supported on a collar which is connected, for example, with the second sleeve or formed on the second sleeve.
• the collar can for example be designed as a collar and are arranged above an inlet opening in the second sleeve.
• the compression spring may be supported directly on the valve body, which is connected to the second sleeve. As a result, the overall height of the control valve can be reduced in an advantageous manner.
• control chamber can be sealed against the first sleeve via a first seal firmly seated on the plunger and closed by a cover connected to the first sleeve.
• first seal By firmly seated first seal the effective first sealing diameter for the closing hydraulic force can be increased depending on the embodiment of the first seal.
• the first seal can for example be designed as a grooved ring or as a continuous sealing membrane.
• the first sleeve with the lid can be made in one piece as a pot.
• the number of required parts can be reduced in an advantageous manner.
• a second seal is arranged axially fixed between a first support connected to the first support and a support connected to the second sleeve and seals radially against the plunger pulled through under the second seal.
• the second seal can be performed, for example, as a grooved ring or as a pierced sealing membrane.
• the plunger can be made in several parts. This allows the different functional diameters to be easily implemented.
• the plunger can be provided in or on introduced grooves in the plunger for the seals or the system for the compression spring by the multi-part embodiment just separation (s) and joints.
• Fig. 1 shows a schematic sectional view of a first embodiment of a hydraulically actuated control valve according to the invention for a vehicle brake system.
• FIG. 2 shows a schematic sectional illustration of a second exemplary embodiment of a hydraulically actuated control valve according to the invention for a vehicle brake system.
• FIG. 3 shows a schematic sectional view of a third exemplary embodiment of a hydraulically actuated control valve according to the invention for a vehicle brake system.
• FIGS. 4 and 5 shows a schematic sectional view of a fourth exemplary embodiment of a hydraulically actuated control valve according to the invention for a vehicle brake system.
• 5 shows a schematic sectional view of an exemplary embodiment of a one-piece first sleeve, which additionally assumes the function of a cap for the first and second exemplary embodiments of the hydraulically actuated control valve for a vehicle brake system according to the invention from FIGS. 1 and 2.
• FIGS. 6 shows a schematic sectional illustration of a further exemplary embodiment of a one-piece first sleeve, which additionally assumes the function of a cap for the first and second exemplary embodiments of the hydraulically actuated control valve for a vehicle brake system according to the invention from FIGS. 1 and 2.
• FIG. 7 shows a schematic sectional illustration of a further exemplary embodiment of a one-piece first sleeve, which additionally assumes the function of a cap for the first and second exemplary embodiments of the hydraulically actuated control valve for a vehicle brake system according to the invention from FIGS. 1 and 2.
• FIG. 8 shows a schematic plan view of the one-piece first sleeve from FIG. 7.
• FIG. 9 shows a schematic sectional illustration of an exemplary embodiment of a shortened plunger and a compression spring, which is supported on a valve body connected to a second sleeve, for the first, second, third and fourth exemplary embodiments of the hydraulically actuated control valve for a vehicle brake system according to the invention from FIG. 1 to 4.
• FIGS. 3 and 4 show a schematic sectional view of an exemplary embodiment of a multi-part tappet for the third and fourth exemplary embodiments of the hydraulically actuated control valve for a vehicle brake system according to the invention from FIGS. 3 and 4.
• the exemplary embodiments illustrated include a hydraulically actuated control valve 1 according to the invention for affybremssystem a first fluid connection 34, which is connected for example via an inlet bore 5 in a fluid block or pump housing 3, 3a with a master cylinder of the vehicle brake system, a second fluid port 36, which for example via a discharge hole 7 in the fluid block or pump housing 3, 3a with a
• a longitudinally movable plunger 10 is acted upon with a sealing geometry 12 by a compression spring 16 with a spring force and held in a starting position, wherein a pressure built-up in the control chamber 44 acts against the spring force of the compression spring 16 and moves the plunger 10 with the sealing geometry 12 from the initial position to an end position, wherein the sealing geometry 12 cooperates with a valve seat 32.1, which is arranged in a valve body 32 to an effective pressure at the second fluid port 36 to a predetermined maximum Druckw limit.
• a valve seat 32.1 which is arranged in a valve body 32 to an effective pressure at the second
• the plunger 10 is guided in a first sleeve 20, and the valve body 32 and the first and second fluid connection 34, 36 are in a second
• Sleeve 30 is arranged, which is fluid-tightly connected to the first sleeve 20.
• the plunger 10 forms an effective first diameter D1 in the region of the control chamber 44, which supports a movement of the plunger 10 in a first direction in conjunction with an applied pressure
• an effective second diameter D2 in the region of the second sleeve 30 is equal to or smaller than the first diameter D1 and, in conjunction with the applied pressure, assists movement of the plunger 10 in a second direction opposite to the first direction.
• a normally open control valve is shown in each case, so that the first end position of the plunger 10 corresponds to the illustrated open starting position and the second end position of the plunger 10 of a closed end position, not shown.
• the movement of the plunger 10 in the first direction corresponds to a closing movement and the movement of the plunger 10 in the second direction corresponds to an opening movement.
• the inventive hydraulically operated control valve for a vehicle brake system designed as a normally closed control valve, in which the first end position of the plunger corresponds to a closed starting position and the second end position of the plunger of an open end position. Furthermore, the movement of the plunger in the first direction corresponds to an opening movement and the movement of the
• valve body 32, 32a is tightly pressed into the second sleeve 30, 30a, 30b designed as a valve sleeve and carries the valve seat 32.1.
• the plunger 10, 10a carries at the lower end of the sealing geometry
• the plunger 10 at the front end, for example with e.g. are provided radially arranged grooves through which a hydraulic pressure is passed to the arranged in the control chamber 44, 44 a front side of the plunger 10.
• the hydraulic pressure is sealed by a firmly seated on the plunger 10 first seal 18, which is designed for example as a grooved ring 18a, against the first sleeve 20, 20a, 20b.
• the effective first diameter D1 is formed by an inner diameter of the first sleeve 20, 20a, 20b, wherein a diameter Di of the inner bore 14 in the plunger 10, 10a must be taken into account.
• the hydraulic pressure acting on the difference between the first diameter D1 and the diameter Di of the inner bore 14 assists in the illustrated embodiment the closing movement of the plunger 10, 10a.
• the control chamber 44, 44 a and the entire control valve 1, 1 a are closed to the outside by a cap 40, 40 a.
• the cap 40, 40a is connected to the first sleeve 20, 20a, 20b via a first connection 26, 26a.
• a further seal 24 which is designed for example as a grooved ring 24a, axially fixed between a support ring 22, 22a and the valve sleeve 30, 30a.
• a further seal 24 which is designed for example as a grooved ring 24a, axially fixed between a support ring 22, 22a and the valve sleeve 30, 30a.
• the support 31 of the second seal 24, 24a on the valve sleeve 30, 30a corresponds to the upper edge of the valve sleeve 30, 30a.
• an additional (support) ring for the second seal 24, 24a may be provided between the valve sleeve 30, 30a and the second seal 24, 24a. The radial support of the second seal 24, 24a takes place on the inside of the first sleeve 20, 20a, and the second seal 24, 24a seals against the plunger 10, 10a, which is pulled through under the second seal 24, 24a.
• the effective second diameter D2 is predetermined by an inner diameter, which bears against the plunger 10, 10a, of the second seal 24, 24a, which is designed as a grooved ring 24a.
• the diameter Di of the inner bore 14 in the plunger 10, 10a must be considered.
• the hydraulic pressure acting on the difference between the second diameter D 2 and the diameter Di of the inner bore 14 assists in the illustrated embodiment the opening movement of the plunger 10, 10 a.
• a clearance 23, 23a between the two seals 18, 24 is filled with air and can serve for leakage absorption.
• the two seals 18, 24 may be provided on the pressure side and / or on the counter-pressure side with support rings or similar additional components.
• the opening acting compression spring 16, 16a engages a shoulder on the plunger 10, 10a and is based on a ring 38, 38a, which integrally formed on the valve sleeve 30, 30a and integrally therewith is executed.
• the compression spring 16, 16 a is disposed outside the direct flow of the operating medium, but surrounded by this.
• the first sleeve 20, 20a and the valve sleeve 30, 30a sealed against each other and secured, for example by a trained as a circumferential laser weld joint 28, 28a.
• suitable types of connections and their combinations are possible, such as flanging, caulking, compression, etc.
• inlet bore 5 and outlet bore 7 in the fluid block or pump housing 3, 3a is realized by a press-in connection 39 between a shoulder of the valve sleeve 30, 30a and the fluid block or pump housing 3, 3a.
• the further seal 24, for example designed as a grooved ring 24a is axially fixed between a support ring 22, 22b and the valve sleeve 30, 30a.
• the support ring 22, 22b is executed as a single part, which is pressed into the first sleeve 20, 20b at a defined position.
• the support 31 of the second seal 24, 24a on the valve sleeve 30, 30b corresponds to the upper edge of the valve sleeve 30, 30b.
• the radial support of the second seal 24, 24a is analogous to the first embodiment on the inside of the first sleeve 20, 20b and the second seal 24, 24a seals against the under the second seal
• the pressure spring 16, 16a which acts in an opening manner acts on a shoulder on the plunger 10, 10a and is supported on a ring 38, 38b which, unlike the first embodiment, is designed as a single part, which to implement a defined spring preload in the valve sleeve 30, 30b is pressed.
• the compression spring 16, 16a is arranged outside the direct flow of the operating medium, but surrounded by it, and the first sleeve 20, 20b and the valve sleeve 30, 30b are sealed against each other, for example, by the connection 28, 28a formed as a circumferential laser weld and attached.
• connection 28, 28a formed as a circumferential laser weld and attached.
• connection 28, 28a formed as a circumferential laser weld and attached.
• valve body 32, 32a is also pressed tightly into the second sleeve 30, 30c, 30d designed as a valve sleeve in the third and fourth exemplary embodiments and carries the valve seat 32.1.
• the plunger 10, 10b of this pressure-compensated control valve 1, 1 c, 1 d comes without inner bore and is fully executed. Therefore, the control chamber 44, 44b via a third fluid connection 46, a corresponding bore 5.1 in the fluid block or pump housing 3, 3b connected to the fluid pump.
• the plunger 10, 10b carries a sealing geometry 12, which is designed for example as a spherical or conical section, and is of the
• Compressed spring 16, 16 a pressed into the open starting position. It attacks the Compression spring 16, 16a analogous to the first and second embodiment of a paragraph on the plunger 10, 10b and is supported on the housing side on a ring 38, 38c, 38d, which in the third embodiment shown in FIG. 3 is integral with the valve sleeve 30, 30c , And alternatively, in the fourth embodiment shown in FIG. 4 is designed as an extra part, which is pressed into the valve sleeve 30, 30 d matching the spring force. Analogous to the first and second embodiments, the compression spring 16, 16a is disposed outside the direct flow of the operating medium, but surrounded by this.
• a first seal 18, 18b delimiting the control chamber 44, 44b is continuous in membrane form and therefore leak-free.
• the first seal 18, 18b is fixedly connected by a suitable geometry to the end of the plunger 10, 10b, wherein the outer diameter of the first seal 18, 18a sits and seals in an annular groove, which through the first sleeve 20, 20c, 20d and the Cap 40, 40b is formed.
• this annular groove can only be in one component, i. either in the cap 40 or in the first sleeve 20, are formed.
• the cap 40, 40b closes the control valve 1, 1 c, 1 d and provides the mounting geometry 42 for the valve 1, 1 c, 1 d in the fluid block or pump housing 3, 3b available.
• the attachment of the control valve 1, 1 c, 1 d in the fluid block or pump housing 3, 3a is preferably carried out by a caulking.
• the attachment geometry may be provided by another component, such as first sleeve 20, 20c, 20d.
• the individual housing parts which comprise the first sleeve, 20, 20c, 20d, the valve sleeve 30, 30c, 20d and the cap 40, 40b, are mounted, sealed and secured in one another.
• the first sleeve 20, 20c, 20d for example, by a circumferential first laser weld 26, 26b with the cap 40, 40b and by a circumferential second laser Absch conductednaht 28, 28b with the valve sleeve 30, 30c, 30d.
• other types of connections and their combinations can be used, such as flanging, caulking, compression, etc.
• the plunger 10, 10b is against the first by a second seal 24 designed as a pierced sealing membrane 24b Sleeve 20, 20c sealed.
• the second seal 24 designed as pierced sealing membrane 24b absorbs the ram lifting movement by means of its own deformation with the least possible loss of force or low hysteresis.
• the second seal 24 designed as a pierced sealing membrane 24b lies externally in an annular groove which is formed by the valve sleeve 30, 30c and the first sleeve 20, 20c. In an alternative embodiment not shown, this annular groove can be formed only in one component, ie either in the valve sleeve 30 or in the first sleeve 20.
• the free space 23, 23b between the two seals 18, 18b and 24, 24b is filled with air and can serve for leakage absorption.
• the control space formed between the first seal 18, 18b and the cap 40, 40b is connected to the pump element pressure p (PE) by the third fluid connection 46, whereby due to the full execution of the plunger 10, 10b a first effective area of D1 2 * TT / 4, which closes with the pump element pressure p (PE).
• An inlet pressure p (Hz) rests on the opposite side of the second seal 24 designed as pierced sealing membrane 24b, so that a second effective area of D2 2 * TT / 4 results due to the full design of the plunger 10, 10b, which corresponds to the inlet pressure p (Hz) opening, wherein the second effective diameter D2 is smaller than the first effective diameter D1 and is used for the calculation of each approximately an average diameter of the membrane geometry.
• the sealing between the inlet pressure p (Hz) or the inlet bore 5 and the pump element pressure p (PE) or the bore 5.1 and / or the discharge bore 7 takes place in the lower region by a press-in connection 39 between a shoulder of the valve sleeve 30, 30c and the Fluid block or pump housing 3, 3b and in the upper region by a further press-in connection 48 between the cap 20, 20b in the fluid block or pump housing 3, 3b.
• the second seal 24 is designed to be a sliding seal similar to the first and second embodiment as a grooved ring 24a or similar with the lowest possible loss of force or low hysteresis on the plunger 10, 10b and axially fixedly disposed between a support ring 22, 22d and the valve sleeve 30, 30d.
• an effective second diameter D2 which corresponds to the inner diameter of the ram 10, 10b applied to the groove 24a.
• the support 31 of the second seal 24, 24a on the valve sleeve 30, 30d corresponds to the upper edge of the valve sleeve 30, 30d.
• the support ring 22, 22d is made in one piece with the first sleeve 20, 20d.
• the first sleeve 20, 20e, 20f, 20g has a pot-shaped bottom which assumes the function of the cap 40.
• the bottom of the sleeve 20, 20e is caulked directly to the fluid block or pump housing 3, 3a
• a shoulder 21 is formed at the bottom of the sleeve 20, 20f.
• the sleeve 20, 20f is caulked over the formed shoulder 21 with the fluid block or pump housing 3, 3a.
• star-shaped pressure outlet geometry on the end face of the plunger 10, 10a can also be realized by a plan-ending plunger 10, 10c and a first sleeve 20, 20g, which is provided with projections and grooves.
• a plurality of beads 25 are inserted into the bottom of the sleeve 20, 20g.
• three beads 25 are preferably introduced into the ground, each having an angle of approximately 120 ° to each other.
• the compression spring 16, 16b is supported in the illustrated embodiment directly on an end face of the valve body 32, 32b, which is pressed into the valve sleeve 30, 30e and the valve seat 32.1 wearing. This allows a shortened design, wherein the windings of the compression spring 16, 16b are surrounded by the operating medium, so that a mutual influence of flow and compression spring 16, 16b is likely.
• the tappet 10c in several parts.
• separation (s) and joints in or on the grooves for the first seal 18 designed as a sealing membrane 18b and / or for the second seal 24 designed as a pierced sealing membrane 24b and / or on the trained shoulder for the compression spring 16, 16a, 16b are provided.
• a first part 11 forms, for example, an upper plunger end and a part of a groove for the first seal 18 designed as a sealing membrane 18b.
• a second part 13 forms a plunger center piece and holds, for example, the first seal 18 designed as a sealing membrane 18b and forms part of the groove for the second seal 24 designed as pierced sealing membrane 24b.
• the first part 11 can be pressed into the second part 13.
• An abutment ring 17 can, for example, form the abutment for the compression spring 16, 16a, 16b and a part of the groove for receiving the second seal 24 designed as a pierced sealing membrane 24b.
• a third part 15 forms a lower plunger end and guides, for example, the compression spring 16, 16a, 16b and comprises the sealing geometry 12. For connecting the second part 13 to the third part 15, the second part 13 can be pressed into the third part 15.

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• 2011
  • 2011-11-08 DE DE201110085881 patent/DE102011085881A1/de active Pending
• 2012
  • 2012-10-04 WO PCT/EP2012/069597 patent/WO2013068181A1/de active Application Filing
  • 2012-10-04 CN CN201280054862.1A patent/CN103917422A/zh active Pending
  • 2012-10-04 JP JP2014537546A patent/JP5758054B2/ja not_active Expired - Fee Related
  • 2012-10-04 EP EP12768822.4A patent/EP2776294A1/de not_active Withdrawn
  • 2012-10-04 US US14/353,167 patent/US20140246898A1/en not_active Abandoned

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