WO1995028588A1 - Soupape de precompression pour commande hydraulique d'embrayage - Google Patents

Soupape de precompression pour commande hydraulique d'embrayage Download PDF

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Publication number
WO1995028588A1
WO1995028588A1 PCT/DE1995/000209 DE9500209W WO9528588A1 WO 1995028588 A1 WO1995028588 A1 WO 1995028588A1 DE 9500209 W DE9500209 W DE 9500209W WO 9528588 A1 WO9528588 A1 WO 9528588A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
valve according
connection
pressure valve
disc
Prior art date
Application number
PCT/DE1995/000209
Other languages
German (de)
English (en)
Inventor
Peter Giese
Hartmut Koschmieder
Reiner Mayer
Walter Parzefall
Original Assignee
Ina Wälzlager Schaeffler Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE4428074A external-priority patent/DE4428074A1/de
Application filed by Ina Wälzlager Schaeffler Kg filed Critical Ina Wälzlager Schaeffler Kg
Priority to DE19580328T priority Critical patent/DE19580328B4/de
Publication of WO1995028588A1 publication Critical patent/WO1995028588A1/fr

Links

Classifications

    • 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
    • B60T11/16—Master control, e.g. master cylinders
    • B60T11/18—Connection thereof to initiating means
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/06—Details
    • F15B7/08—Input units; Master units
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • F16D25/14—Fluid pressure control
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • 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
    • F16K15/00—Check valves
    • F16K15/18—Check valves with actuating mechanism; Combined check valves and actuated valves
    • F16K15/182—Check valves with actuating mechanism; Combined check valves and actuated valves with actuating mechanism
    • F16K15/1823—Check valves with actuating mechanism; Combined check valves and actuated valves with actuating mechanism for ball check valves
    • 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
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/18—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on either side
    • F16K17/19—Equalising valves predominantly for tanks
    • F16K17/196—Equalising valves predominantly for tanks spring-loaded
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0221—Valves for clutch control systems; Details thereof

Definitions

  • Vordruc valve of a hydraulic clutch actuation device of a motor vehicle with a first connection assigned to a master cylinder and with a second connection assigned to a slave cylinder, the valve being opened in the event of a pressure drop from the first to the second port and in the case of pressure drop from the second to the first port falling below a specified form is closed.
  • Such an actuator is known for example from DE-GM 93 12 968.
  • a closing or opening mechanism is to be developed which, with a structural simplification, enables the pre-pressure valve to be operated just as safely.
  • this object is achieved in that two closing bodies, in particular balls, are arranged between the first and the second connection by means of spring elements against their valve seats, one valve seat being arranged on the side of the first and the other valve seat on the side of the second connection, and the valve seats being formed on a component arranged between the two connections.
  • this pre-pressure valve when a clutch pedal is actuated, the ball provided on the side of the second connection is pressed out of its valve seat as a result of the pressure increase, so that hydraulic oil is pressed into the slave cylinder, the clutch disengaging. If the pressure in the master cylinder is reduced by withdrawing the clutch pedal, the other ball is pressed out of its valve seat, hydraulic oil flowing from the side of the slave cylinder to the side of the master cylinder. However, there is no pressure equalization between the two connections, since this ball is already pressed into its valve seat under the action of the spring element when the admission pressure is reached. This arrangement ensures that the clutch disengages very quickly when the clutch pedal is actuated due to the pressure on the slave cylinder side.
  • the component - which separates the two connections from one another in a liquid-tight manner - is designed as a disk and is provided with two through openings on the end face, the conical valve seats being formed on opposite end faces of the disk.
  • the valve seat itself can also be an edge, which is formed by the through opening and the end face of the disc.
  • valve seats are formed from a rubber-elastic material, in particular rubber. In this way a liquid-tight seat of the ball is guaranteed.
  • the washer is formed from a rubber-elastic material, in particular rubber, the washer being provided with a reinforcing ring, in particular made of steel.
  • the valve seats are formed directly on the disk. In this case it is ensured in a simple manner that the valve seat conforms perfectly to the contour of the ball when the ball is pressed into its valve seat.
  • the reinforcing ring can have noses protruding axially in the region of the through-openings and aligned at approximately parallel spacing from the conical valve seats. These lugs serve as support for the valve seats, so that the disk or the valve seats cannot deflect axially as a result of a pressure load and possibly cause a leaky valve seat due to this deflection.
  • the washer for correct connection is provided with a component adjoining the end face with two axial bores on the end face, the straight line connecting the center points of the bores being spaced apart from the center point of the washer, wherein in pins inserted into these holes in holes in the component.
  • the bores are through bores
  • their walls are provided with circumferential beads, the clear diameter of the circumferential beads being smaller than the diameter of the pins. This arrangement ensures that no hydraulic oil can flow through these through holes between the pins and the wall.
  • the pre-pressure valve has two axially adjacent and mutually concentric housing halves, in particular made of plastic, on the opposite end faces of which the first and the second connection is formed, the disc being arranged between mutually facing end sides of the two housing halves is.
  • These housing halves can be held together by means of a clip, which is formed in particular from steel, as suggested in claim 10.
  • the clip can be designed as a sleeve surrounding the housing halves, at the axial ends of which radially inwardly projecting ribs or rib segments are provided, which engage on the two housing halves and face away from each other holding surfaces.
  • Figure 1 shows a longitudinal section through an inventive high pressure valve
  • FIG. 2 shows a further longitudinal section through the pre-pressure valve according to the invention from FIG. 1, but under a different section;
  • FIG. 3 shows the view of a disc from FIG. 1
  • Figure 4 shows a longitudinal section of the disc of Figure 3 along the line IV-IV;
  • Figure 5 shows a longitudinal section of the disc of Figure 3 along the line V-V
  • the inlet pressure valve according to the invention shown in FIG. 1 has two axially adjacent and mutually concentric housing halves 1, 2 formed on the opposite ends of which a connection 3 and a connection 4 are formed. With these connections 3, 4, pipe or hose lines, not shown, are connected, the connection 3 being associated with a master cylinder, also not shown, and the connection 4 being associated with a slave cylinder, also not shown.
  • a disc 5 is arranged between facing end faces of the two housing halves 1, 2.
  • the plastic disc 5 is inserted in a bore 6 of the housing half 2 liquid and gas-tight.
  • the housing half 1 is inserted with its piston-shaped end 7 into a bore 8 of the housing half 2.
  • the piston-shaped end 7 has a circumferential groove 9 in which a sealing ring 10 is inserted, the sealing ring 10 being clamped between the bore 8 and a groove base 11 of the circumferential groove 9 in such a way that the valve interior is sealed in a liquid-tight manner from the surroundings.
  • the two housing halves 1, 2 are held together by a clamp sleeve 12.
  • the clamp sleeve 12 has at its axial ends inwardly projecting radial rims 13.
  • the housing half 1 has an end-side holding surface 14 and the housing half 2 has an end-side holding surface 15, which the radial rims 13 engage tightly behind.
  • the disc 5 has two radially adjacent through openings 16, 17. Tapered valve seats 18, 19 are formed on the end faces of the disk 5 facing away from one another, which connect to the through openings 16, 17.
  • a ball 20, 21 belongs to each of the two conical valve seats 18, 19 and is pressed against its valve seat 18, 19 by a helical compression spring 22, 23.
  • the one helical compression spring 22 is supported on the housing half 1 and the other helical compression spring 23 is supported on the housing half 2.
  • the housing half 1 is provided with an axially parallel piston bore 24, a piston 25 being guided axially movably in this piston bore 24.
  • the piston bore 24 and the piston 25 delimit a pressure chamber 26.
  • the pressure chamber can be ventilated or vented via a ventilation bore 27.
  • the piston is provided with circumferential, conical ring sections 28, 29, the radially outer free ends of which are pressed against the piston bore 24.
  • the piston 25 with its end facing the ball 21, presses this ball 21 out of its valve seat 19, so that hydraulic oil can flow via an axial channel 30 of the housing half 1 through the through opening 17 into an axial channel 31 of the housing half 2 and vice versa.
  • Figure 2 shows the same pressure valve as Figure 1, but with a different section.
  • Two pins 32 are inserted on the one hand into axial bores 33 of the housing half 1 and on the other hand into axial bores 34 of the disk 5. In this way, the disc 5 is fixed in position relative to the housing half 1.
  • FIG. 3 shows the disk 5 as a view. It can clearly be seen here that the connecting straight line between the centers of the axial bores 34 does not run through the center of the disk. This means that the disc 5 can only be attached to the housing half 1 in a single position.
  • Figure 4 shows that the outer surface of the axial bore 34 is provided with circumferential beads 35.
  • the inside diameter of these beads 35 is smaller than the diameter of the pins 32, not shown here. This means that no hydraulic oil can be pressed between the bead 35 and the pin 32, not shown.
  • the disc 5 is also provided with a reinforcement ring 36.
  • the reinforcement ring 36 is shaped in the region of the conical valve seats 18, 19 in such a way that it forms axially projecting cones 37 which give the rubber-elastic valve seats 18, 19 the stability required for operation.
  • the mode of operation of the pre-pressure valve according to the invention is described below.
  • the ball 21 is pushed out of its valve seat by the piston 25.
  • the entire hydraulic system is filled with hydraulic oil.
  • the hydraulic oil can pass freely from one axial channel 30 into the other axial channel 31 or vice versa, without having to overcome the spring force of one of the helical compression springs 22, 23.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Check Valves (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

Soupape de précompression pour commande hydraulique d'embrayage d'un véhicule automobile, présentant un premier raccord (3) associé à un maître-cylindre et un deuxième raccord (4) associé à un cylindre récepteur (4), ladite soupape étant ouverte en cas de chute de pression du premier (3) au deuxième raccord (4) et étant fermée lorsque la pression du deuxième (4) au premier raccord (3) tombe au-dessous d'une valeur de précompression déterminée. Conformément à l'invention, la soupape de précompression présente, entre les deux raccords (3, 4), deux corps d'obturation, notamment des billes (20, 21), s'appliquant par pression contre leurs sièges (18, 19), par l'intermédiaire d'éléments élastiques (22, 23). L'un des sièges (18) est disposé sur les côtés du premier raccord (3) et l'autre (19), sur les côtés du deuxième raccord (4). Les sièges de soupape (18, 19) sont formés sur un élément (5) disposé entre les deux raccords (3, 4).
PCT/DE1995/000209 1994-04-15 1995-02-17 Soupape de precompression pour commande hydraulique d'embrayage WO1995028588A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE19580328T DE19580328B4 (de) 1994-04-15 1995-02-17 Vordruckventil einer hydraulischen Kupplungsbetätigungseinrichtung

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DEP4412918.1 1994-04-15
DE4412918 1994-04-15
DE4428074A DE4428074A1 (de) 1994-04-15 1994-08-09 Vordruckventil einer hydraulischen Kupplungsbetätigungseinrichtung
DEP4428074.2 1994-08-09

Publications (1)

Publication Number Publication Date
WO1995028588A1 true WO1995028588A1 (fr) 1995-10-26

Family

ID=25935611

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1995/000209 WO1995028588A1 (fr) 1994-04-15 1995-02-17 Soupape de precompression pour commande hydraulique d'embrayage

Country Status (2)

Country Link
DE (1) DE19580328B4 (fr)
WO (1) WO1995028588A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2351874A (en) * 1942-05-20 1944-06-20 Parker Appliance Co Relief valve for fuel tanks
DE1755935A1 (de) * 1968-07-12 1972-01-13 Daimler Benz Ag Hydraulische Bremsanlage fuer Fahrzeuge,insbesondere fuer Kraftwagen
FR2096122A5 (fr) * 1970-06-09 1972-02-11 Blau Kg Fabrik Kraftfanr
FR2655128A1 (fr) * 1989-11-29 1991-05-31 Automotive Prod France Dispositif de filtrage de vibrations, notamment pour commande hydraulique d'embrayage de vehicules automobiles.
EP0494557A1 (fr) * 1990-12-31 1992-07-15 Forges de Belles Ondes Appareil limiteur de pression

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2032581B (en) * 1978-10-24 1983-01-06 Mac Valves Inc Combined pressure reductor and flow control valve
DE9312968U1 (de) * 1993-08-30 1993-10-14 INA Wälzlager Schaeffler KG, 91074 Herzogenaurach Vordruckventil

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2351874A (en) * 1942-05-20 1944-06-20 Parker Appliance Co Relief valve for fuel tanks
DE1755935A1 (de) * 1968-07-12 1972-01-13 Daimler Benz Ag Hydraulische Bremsanlage fuer Fahrzeuge,insbesondere fuer Kraftwagen
FR2096122A5 (fr) * 1970-06-09 1972-02-11 Blau Kg Fabrik Kraftfanr
FR2655128A1 (fr) * 1989-11-29 1991-05-31 Automotive Prod France Dispositif de filtrage de vibrations, notamment pour commande hydraulique d'embrayage de vehicules automobiles.
EP0494557A1 (fr) * 1990-12-31 1992-07-15 Forges de Belles Ondes Appareil limiteur de pression

Also Published As

Publication number Publication date
DE19580328B4 (de) 2006-11-02
DE19580328D2 (de) 1997-07-24

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