EP1532031A1 - Maitre-cylindre - Google Patents

Maitre-cylindre

Info

Publication number
EP1532031A1
EP1532031A1 EP03766364A EP03766364A EP1532031A1 EP 1532031 A1 EP1532031 A1 EP 1532031A1 EP 03766364 A EP03766364 A EP 03766364A EP 03766364 A EP03766364 A EP 03766364A EP 1532031 A1 EP1532031 A1 EP 1532031A1
Authority
EP
European Patent Office
Prior art keywords
pressure medium
closing body
master cylinder
valve
pressure
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP03766364A
Other languages
German (de)
English (en)
Inventor
Holger Von Hayn
Jürgen Schonlau
Manfred Rüffer
Wolfgang Ritter
Milan Klimes
Torsten Queisser
Ralf Jakobi
Michael Vogt
Dieter Merkel
Bernhard Hammes
Hans-Jörg Feigel
Jose Gonzalez
Stephan Krebs
Oliver Kugland
Thomas Sellinger
Guido Schell
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Continental Teves AG and Co OHG
Original Assignee
Continental Teves AG and Co OHG
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 DE2002134541 external-priority patent/DE10234541A1/de
Application filed by Continental Teves AG and Co OHG filed Critical Continental Teves AG and Co OHG
Publication of EP1532031A1 publication Critical patent/EP1532031A1/fr
Withdrawn legal-status Critical Current

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
    • B60T11/228—Pressure-maintaining arrangements, e.g. for replenishing the master cylinder chamber with fluid from a reservoir
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/005—Filling or draining of fluid systems
    • 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
    • B60T11/232—Recuperation 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
    • B60T11/30—Bleed valves for hydraulic brake systems
    • 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
    • B60T17/00—Component parts, details, or accessories of power brake systems not covered by groups B60T8/00, B60T13/00 or B60T15/00, or presenting other characteristic features
    • B60T17/18—Safety devices; Monitoring
    • B60T17/22—Devices for monitoring or checking brake systems; Signal devices

Definitions

  • the invention relates to a master cylinder, in particular for a hydraulic brake system, with at least one pressure chamber formed in a housing of the master cylinder and at least one container bore for receiving a pressure medium container, a valve having a closing body being provided which, as a result of an applied pressure difference between the pressure chamber and the pressure medium container is movable into an open position or a closed position, the valve in the open position permitting a pressure medium flow from the pressure medium container into the pressure chamber and in the closed position throttling or preventing a pressure medium flow from the pressure chamber into the pressure medium container that is opposite to the pressure medium flow.
  • the problem with master cylinders is that the free travel to be overcome when the master cylinder is actuated is relatively large, ie the driver of a vehicle must depress the brake pedal relatively far before there is an increase in pressure in the brake system and thus the desired braking.
  • the reason for this relatively long free travel which results from an actuation is primarily that, starting from a rest position in which the pressure pistons are when actuation begins, pressure pistons in the master cylinder have to be displaced relatively far in the actuation direction before the pressure medium connection between the pressure medium container and the pressure chambers present in the master cylinder is interrupted. Before this pressure medium connection is not interrupted, the can Pressure chambers of the master cylinder no significant pressure can be built up.
  • the vehicle manufacturer initially fills the brake system with pressure medium by means of a vacuum. This means that the system evacuates before filling with pressure medium, i.e. all air is removed from the brake system. After the evacuation, the brake system is filled with pressure medium under pressure. The evacuation eliminates the need to vent the brake system at a later date.
  • a filling head is attached to the pressure medium container for evacuation and vacuum filling.
  • evacuation it is necessary to keep the valve closing body in the open position so that the air can escape unhindered from the brake system through the container.
  • a master cylinder with a valve arrangement for shortening the free travel having a closing body arranged in a container bore, the valve seat of which is formed by a container connecting piece and which due to an applied pressure difference between the pressure chamber and the pressure medium container into an open position or a closed position is movable. In the closed position there is a throttled pressure medium connection between the pressure chamber and the pressure medium container.
  • a disadvantage of this valve arrangement is that the closing body is arranged directly on the pressure medium container, as a result of which large tolerances can occur, which have a negative effect on the shortening of the free travel.
  • the closing body is not in the open position due to the pressure difference that arises when the brake system is evacuated, but is moved into the closed position and thus prevents the air from escaping from the brake system.
  • the object is achieved in that means are provided which hold the closing body, which has a closing pressure difference as a result of an evacuation for the purpose of vacuuming the braking system, in the open position and, when the brake is actuated, enable the closing body to move into the closed position.
  • the valve enables a very short free travel, since the pressure build-up in the pressure chamber occurs from the start when the pressure piston moves.On the other hand, the escape of air is not impeded when the brake system is evacuated, so that the air is not throttled can flow out of the brake system.
  • the valve for contacting the closing body in the closed position has a first contact element arranged in the container bore, the closing body between the contact element and a bottom of the Container bore is movably arranged, and the contact element on a bottom side facing the closing body has a circumferential sealing bead which is arranged in such a way that a radially outer region of an upper side of the closing body in the closed position bears sealingly on the sealing bead.
  • the arrangement of the first contact element in the container bore takes place, for example, by caulking. Other fastening options are conceivable, such as screwing in, pressing on using a screw ring, or fastening using a snap ring.
  • the closing body of the valve is not arranged on a pin of the pressure medium container, as a result of which small tolerances can be maintained.
  • the closing body is designed as a disc which, in order to ensure the flow of pressure medium from the pressure medium container into the pressure chamber, has webs formed in the direction of the bottom of the container bore, the webs resting on the floor in the open position.
  • a further possibility for ensuring the pressure medium flow from the pressure medium container into the pressure chamber is that the disc has webs on its periphery, which in the open position allow the disc to rest on a circumferential shoulder of the container bore.
  • the valve opens in the closed position from a certain pressure difference and enables the unrestricted flow of pressure medium from the pressure chamber into the pressure medium container.
  • this makes it possible to reduce excess pressure medium volume or residual pressure in certain operating states
  • This is particularly important at low temperatures where the flow resistance is quite high without it.
  • the structure according to the invention thus gives a braking system with a very small free travel, which is also suitable for regulating the braking system in which the driver does not actuate the brake pedal.
  • the contact element on its underside has elevations which serve the closing body in the closed position from the pressure difference opening the valve as lever points, the closing body deflecting and the radially outer region of the upper side of the closing body lifting off the sealing bead and the unthrottled pressure medium flow from the pressure chamber into the pressure medium container.
  • the closing body can be designed as a disk, which is dimensioned in such a way that bending is possible without damage. It is thereby achieved that an excess pressure medium volume or a residual pressure can be reduced without a complicated structure of the valve.
  • the valve has a second contact element provided with channels, which adjoins the first contact element in the container bore in the direction of the bottom, the second contact element serving to support the closing body in the open position.
  • the channels ensure that pressure medium flow into the pressure chamber is not prevented.
  • the two contact elements form an assembly unit.
  • an adhesive holds the closing body in the open position when the brake system is evacuated, the adhesive detaching when the vacuum is applied to the pressure medium, as a result of which no additional components are necessary.
  • a clamping element holds the closing body in the open position, which releases when pressure is applied to the vacuum.
  • a sleeve-shaped tensioning element is provided in the first contact element, which, when the brake system is evacuated, protrudes so far out of the first contact element in the direction of the closing body that it keeps the closing body in the open position, with a result of the first-time brake actuation Valve-closing pressure difference moves the closing body into the closed position, the closing body pushing the clamping element back into the first contact element, so that the closing body can be moved into the closed position when the brake is actuated.
  • the clamping ring is pushed even further into the first contact element by the deflection of the closing body, it not being able to detach from the contact element.
  • the clamping ring enables very simple assembly, since it is inserted into a bore of the first contact element from the side facing the container can be .
  • the closing body has on its circumference
  • Locking elements which hold the closing body in the open position by means of a mechanical lock when the brake system is evacuated, the mechanical lock being releasable during the vacuuming by filling in the pressure medium.
  • the closing body is again conceivable here.
  • the closing body is again conceivable here.
  • Pins Have locking elements in the form of pins, which are arranged on its circumference or its underside.
  • the pins are arranged in grooves for evacuation of the brake system, with a spring ensuring this open position. If the brake system is then filled with pressure medium, the pins are released from the grooves by the pressure difference applied to the closing body and a closing position of the closing body when the brake is actuated is possible again.
  • the circumference of the closing body can be provided with shovel-like elements which turn the closing body out of the mechanical lock due to the pressure medium filling.
  • Pins can also be used for mechanical locking, which are arranged, for example, on the connecting piece of the pressure medium container and hold the closing body in the open position during the evacuation process.
  • an external magnetic field holds the closing body in the open position.
  • the material of the closing body and the contact elements is selected such that when the brake system is evacuated as a result of the Applied magnetic field, which is generated for example by means of a yoke and a coil outside the master cylinder, the closing body is repelled by the first contact element and is thus held in the open position, so that an unimpeded air flow from the pressure chamber into the pressure medium container and thus a ventilation of the brake system is possible.
  • the generation of the magnetic field is possible in different ways. For example, generation using permanent magnets is conceivable.
  • a weight is fastened to the closing body when the brake system is evacuated, which holds the closing body in the open position and whose material is selected such that the weight in the pressure medium is almost neutralized when the brake is actuated.
  • the valve is preferably provided with a throttled pressure medium connection which, in the closed position of the closing body, enables throttled pressure medium flow from the pressure chamber into the pressure medium container. As a result, a back pressure reduction on the valve can take place without actuation of the closing body.
  • the throttled pressure medium connection can be designed, for example, as a parallel path or as an orifice arranged on the first contact element.
  • the valve is inserted in a connection area between the master cylinder and the pressure medium container.
  • the reason for this is that several paths lead from the pressure chamber to the pressure medium container, such as the sniffer hole and the trailing bore. If necessary, the connection runs via a central valve in the piston and the follow-up bore.
  • the valve is effective regardless of the way in which the pressure medium flows. It is particularly expedient to arrange the valve in a connecting piece of the pressure medium container. The invention is therefore also well suited as a leakage protection for the container.
  • the valve preferably has a valve housing, in which a valve seat is arranged to be longitudinally displaceable, a second channel being connectable through the valve seat. From a certain pressure difference, the second channel enables, for example, a rapid reduction in the residual pressure in the pressure chamber.
  • the valve seat can serve to receive the throttled pressure medium connection or at least limit the throttled path in part, for example by inserting a groove in the edge or a bore along the center line of the valve seat, which results in a particularly simple construction of the valve.
  • valve comprises a valve body, a sealing element with a sealing lip and a leaf spring, the sealing lip counteracting the flow of pressure medium from the pressure medium container into the pressure chamber and the leaf spring starting from a certain pressure difference Pressure fluid flow enables.
  • the sealing element instead of the leaf spring, can have a second sealing lip, the first sealing lip permitting the pressure medium flow from the pressure medium container into the pressure chamber and the second sealing lip allowing the oppositely directed pressure medium flow from a certain pressure difference.
  • the valve body is preferably provided with a permeable membrane, which enables the throttled flow of pressure medium from the pressure chamber into the pressure medium container.
  • Fig. 1 shows a first embodiment of an inventive
  • Fig. 2 shows an enlarged section X of the first
  • FIG. 1 shows a detail of a second exemplary embodiment of a master cylinder according to the invention
  • 4 shows a detail of a third exemplary embodiment of a master cylinder according to the invention
  • 5 to 7 a fourth embodiment of a master cylinder according to the invention in different
  • FIG. 20 shows a seventh embodiment of an inventive
  • Fig. 21 shows an eighth embodiment of an inventive
  • Fig. 22 shows a ninth embodiment of an inventive
  • Fig. 23 shows a tenth embodiment of an inventive
  • FIG. 25 in a broken-away representation a top view of the exemplary embodiment according to FIG. 24.
  • FIG. 1 shows a first embodiment of a master cylinder 1 for a hydraulic brake system with two pressure chambers 3, not shown, formed in a housing 2 of the master cylinder 1 and two container bores 4 for receiving a
  • a valve 6 is provided in the container bore 4, which enables a shortening of the free travel and a vacuum supply to the brake system.
  • FIG. 2 shows an enlarged section X of the master cylinder 1 shown in FIG. 1.
  • the pressure medium container 5 is arranged in the container bores 4 of the master cylinder 1 by means of connecting pieces 28 and sealing elements 29.
  • the valve 6 comprises an annular first contact element 8 arranged in the container bore 4 and a closing body 7 which is designed as a thin disc and is arranged between the contact element 8 and a bottom 9 of the container bore 4.
  • the valve 6 can be moved into an open position or a closed position due to an applied pressure difference between the pressure chamber 3 and the pressure medium container 5.
  • a pressure medium flow S1 from the pressure medium container 5 via the pressure medium channel 30 into the pressure chamber 3 is possible.
  • a pressure medium flow S2 directed opposite the pressure medium flow S1 is throttled or prevented by the pressure chamber 3 into the pressure medium container 5.
  • the disk 7 does not rest on the bottom 9 of the container bore 4 in the open position shown in FIG. 2 and thus cannot close the pressure medium channel 30, the disk 7 has integrally formed webs 12 on its outer circumference in the direction of the bottom 9, through which the pressure medium can flow.
  • the valve 6 blocks the pressure medium flow S2 before the closing path is crossed and the pressure medium is displaced into the brake system.
  • the first contact element 8 can be fastened in the container bore 4 as shown in FIG. 2 by caulking. However, more are also conceivable
  • Fig. 3 shows a section of a second embodiment of a master cylinder 1.
  • the closing body 7 of the valve 6 is also designed as a disc and is provided with webs 31 formed on its circumference, which in the open position for supporting the disc 7 on a circumferential Paragraph 32 of the container bore 4 serve.
  • the webs 31 are distributed on the circumference of the disk in such a way that the pressure medium flow S1 into the pressure chamber 3 is ensured by an intermediate space between two webs 31.
  • FIG. 4 A third exemplary embodiment of a master cylinder 1 with a valve 6 is shown in FIG. 4.
  • a second contact element 14 is provided, which on the shoulder 32 of the Container bore 4 rests.
  • the first contact element 8 bears against the second contact element 14, both contact elements 8, 14 being held securely in this position by fastening the first contact element 8 in the container bore 4.
  • the closing body 7, which is designed as a disk, is located between the two contact elements 8, 14, which serve the latter as a contact in the closed position and the open position.
  • the second contact element 14 has contact surfaces 35 for the disc 7 and is formed with channels 13 which, when the disc 7 is placed on the contact element 14 in the open position, enable the first pressure medium flow S1 from the pressure medium container 5 into the pressure chamber 3 and through which the disc 7 does not rest with its entire circumference on the second contact element 14.
  • the first contact element 8 is provided with the sealing bead 10, against which the disc 7 lies in a sealing manner in the closed position.
  • 5 to 7 show sections of a fourth exemplary embodiment of a master cylinder 1 in three different operating states, this exemplary embodiment relating to that The third exemplary embodiment shown in FIG. 4 differs only in the fastening of the first contact element 8 in the container bore 4.
  • 5 shows the valve 6 in the open position, in which pressure medium is sucked in from the pressure medium container 5 into the pressure chamber 3 by the piston return movement (first pressure medium flow S1).
  • the disc 7 is moved the resulting pressure difference in the direction of the second contact element 14 and rests thereon on the support surfaces 35, the channels 13 therein allowing the pressure medium flow S1.
  • FIG. 6 shows the valve when the master cylinder 1 is actuated.
  • the piston movement displaces pressure medium from the pressure chamber 3 and the disk 7 is moved upwards into the closed position, so that the top 11 of the disk 7 rests on the sealing bead 10 and one Pressure medium flow S2 in the direction of the pressure medium container 5 is prevented.
  • the elevations 15, which are arranged in a circle inside the sealing bead 10, are no higher than the sealing bead 10, as a result of which the sealing contact of the disk 7 with the first contact element 8 is ensured.
  • the valve 6 In order to reduce a residual pressure in the pressure chamber 3, for example, the valve 6 must open in the closed position from a certain pressure difference and allow an unrestricted flow of pressure medium S2 from the pressure chamber 3 into the pressure medium container 5.
  • the elevations 15, which serve as lever points H from a certain pressure difference of the disk 7, the disk 7, as shown in FIG. 7, bending in the middle in the direction of the pressure medium container 5 rests at the lever points H and is thus lifted off the sealing bead 10.
  • the vehicle manufacturer initially fills the brake system with pressure medium by means of a vacuum.
  • the system is evacuated before filling with pressure medium, ie all the air is removed from the brake system. After the evacuation, the brake system is filled with pressure medium under pressure. The evacuation eliminates the need to vent the brake system at a later date.
  • the pressure medium container 5 is used for evacuation and
  • Vacuum application a filling head attached. During the evacuation, it is necessary to close the closing body 7 of the valve 6 in the
  • Brake system can escape through the container.
  • the valve 6 thus fulfills the following four functions:
  • FIG. 8 and 9 show the third exemplary embodiment according to FIG. 4 when the brake system is evacuated.
  • the disc 7 must be held in the open position on the second contact element 14 during this process in order to enable and ensure an air flow L from the pressure chamber 3 into the pressure medium container 5 through the channels 13 of the second contact element 14.
  • the disk 7 is glued to the support surfaces 35 of the second contact element 14 for this purpose.
  • the adhesive K dissolves on contact with the pressure medium when the brake system is filled, so that the disk 7 can again be moved between the two contact elements 8, 14 and the valve 6 fulfills the required functions when the brake is actuated.
  • FIG. 9 shows a further possible solution for holding the pane 7 in its open position for evacuation.
  • a clamping element 16 is clamped between the disc 7 and the first contact element 8 and thus holds the disc 7 in the lower position. If the brake system is filled with pressure medium, the clamping element 16 is released and the disk 7 is movable again.
  • the clamping element 16 is designed and positioned in the valve 6 such that the air flow L is not hindered during the evacuation.
  • a fifth embodiment of a master cylinder 1 is shown.
  • a sleeve-shaped clamping element 17 is inserted into a bore 36 of the first contact element 8 during assembly.
  • the tensioning element 17 becomes so deeply depressed that the disc 7 is pressed against the second contact element 14 in the open position.
  • the clamping element 17 is dimensioned such that the disc 7 does not come out of this position during the evacuation.
  • the air flow L takes place through the pressure medium channel 30 via the channels 13 of the second contact element 14 and the through bores 34 of the first contact element 8 into the pressure medium container 5.
  • Fig. 11 shows the valve 6 after a first brake application.
  • the disc 7 is moved into the closed position by a pressure difference that arises from a first brake application, in which the disc 7 bears against the first contact element 8.
  • the tensioning element 17 is also displaced in this direction and the valve 6 is fully functional.
  • FIG. 12 shows the valve 6 when the residual pressure is reduced, the disk 7 bending in the closed position as described in FIG. 7, lifting off the sealing bead 10 and thus allowing the residual pressure to be reduced.
  • the clamping element 17 is pushed back further by the bending of the disc 7 into the first contact element 8, it not being released from the contact element 8.
  • FIG. 13 shows the first contact element 8 with the tensioning element 17 mounted in the bore 36.
  • the circumferential sealing bead 10 is arranged on the underside 50 of the contact element 8 outside the circularly arranged elevations 15, which serve the disc 7 as lever points H when the residual pressure is reduced.
  • the through bores 34 are arranged with the elevations 15 in such a way that the pressure medium flow S2 into the pressure medium container 5 through the contact of the disc 7 the lever points H is not hindered.
  • FIGS. 14 to 19 show a sixth embodiment of a master cylinder 1 with the valve 6 for shortening the free travel and vacuuming.
  • a mechanical lock holds the disk 7 in the open position, the disk 7 being unlocked by the filling pressure during the vacuum application.
  • locking elements 18 designed as pins are attached to the periphery of the disc 7 on the disc 7, which are either integrally formed during the manufacture of the disc 7 (FIG. 14) or subsequently by suitable methods such as, for example can be attached by welding (Fig. 15). 16 that the locking elements 18 can also be molded onto an underside of the disk 7. 17 shows the valve 6 during the evacuation.
  • the pins 18 engage in grooves 37 which are arranged obliquely in the second contact element 14, the grooves 37 being closed at an upper end and open at a lower end in the tangential direction.
  • the grooves 37 are, as can be seen from FIGS. 18 and 19, made in projections 38 which protrude radially inward from an inner wall 39 of the second contact element 14.
  • the projections 38 can be molded on during the manufacture of the contact element 14, but also subsequently. 19 shows projections 38, which are designed as pins and are fastened to the inner wall 39 of the contact element 14.
  • the disc 7 By means of a spring 40 acting on the disc 7 from below, the disc 7 is held in the open position in the sketched position (FIG. 17) and cannot be released from the master cylinder 1 to the pressure medium container 5 by the air flow L even during evacuation. If the disc 7 is now acted upon by the pressure of the pressure medium counteracting the spring 40 when filling the brake system, the disc 7 moves out of the grooves 37 against the pressure of the spring 40 with a minimal rotation. The disc 7 can now freely move upwards into the firing position when the brake is actuated and shut off the pressure medium flow S2 from the pressure chamber 3 by contacting the first contact element 8.
  • the valve 6 has a first contact element 8, a closing body 7 and a second contact element 14.
  • the material of the closing body 7 and of the first contact element 8 is selected such that the closing body 7 is held in the open position by means of a magnetic field M during the evacuation.
  • the magnetic field M is applied to the master cylinder 1 from the outside by means of a yoke 41 and a coil 42 during the evacuation of the brake system.
  • the first contact element 8 and the closing body 7 consist of ferromagnetic materials and are magnetized in the same direction by the magnetic field M. As a result, they repel each other and the closing body 7 is pressed into the open position on the second contact element 14, which consists of a non-ferromagnetic material.
  • a suitable choice of materials can prevent the magnetized components from sticking.
  • the entire structure for generating the magnetic field M can also be integrated in the filling system of the vehicle manufacturer.
  • the following embodiments, not shown, are conceivable:
  • the density of the material is selected such that the weight in pressure medium is almost neutralized.
  • a weight acts on the closing body 7 from above via a pin and presses it onto the support element 14.
  • the weight should not act in pressure medium (float).
  • a locking pin enables locking, which is actuated by the filling pressure, pressed into a bore and thereby releases the closing body 7.
  • valve 21 shows a valve 6 of an eighth exemplary embodiment of a master cylinder 1, which can be used in the container bore 4 of the master cylinder 2, but also in the connecting piece 28 of the pressure medium container 5.
  • a displaceable valve seat 21 is arranged in a valve housing 20 of the valve 6 under pretension of a spring 43.
  • the valve seat 21 is provided with through openings 44, which can be closed by a closing body 7 even at a small pressure difference (closed position) and prevent a pressure medium flow S2 from the pressure chamber 3 into the pressure medium container 5.
  • the closing body 7 opens (open position) and allows pressure medium to flow in the suction direction (pressure medium flow S1), so that pressure medium into the pump when the brake system intervenes independently of the driver can reach.
  • An additional pressure medium connection 19 is provided as a throttle bore in the valve seat 21 and is chosen so closely that only a throttled pressure medium flow D can flow from the pressure chamber 3 to the pressure medium container 5 when pressure builds up in the pressure chamber 3.
  • valve seat 21 is raised to such an extent that pressure medium can flow via an inlet 45 and a groove channel 46 in the valve housing 20 in order, for example, to be able to quickly remove the pressure from the wheel brakes (ABS ).
  • the throttled pressure medium connection 19 is placed on an outer lateral surface of the valve seat 21 by inserting a suitable groove there.
  • the closing body 7 allows a first pressure medium flow S1 from the pressure medium container 5 into the pressure chamber 3 (open position) and closes the second pressure medium flow S2 from the pressure chamber 3 into the pressure medium container 5 (closed position).
  • a plunger 47 is lifted from the valve seat 21 against the force of a spring 48 that prestresses the plunger 47, and thus enables a pressure medium flow S2 via an access 51.
  • a second sealing lip 23 shows a tenth embodiment of a master cylinder 1 with a valve 6, which is arranged in the connecting piece 28 of the pressure medium container 5.
  • the throttle function is formed by a permeable membrane 49, which is arranged in a valve body 27 and has a large flow resistance.
  • the closing body 7 is formed by a sealing element 24 with a first sealing lip 22, which the pressure medium flow S2 from the pressure chamber 3 into the pressure medium container 5 through passages 26 in the The valve body 27 is blocked and the pressure medium flow S 1 into the pressure chamber 3 is permitted.
  • a second sealing lip 23 can also block a pressure medium flow S1 and allow a pressure medium flow S2, as is shown for example in FIG. 24 in an eleventh embodiment.
  • the passages 26 of the valve body 27 are closed by a first sealing lip 22 and a leaf spring 25.
  • the first sealing lip 22 and leaf spring 25 are now designed and arranged such that some of the passages 26 are freely accessible from above and another part of the passages 26 from below, while the other end of these passages are each accessible through the leaf spring 25 or the sealing lip 22 is closed.
  • the spring constant, or the pressure required for opening, is very much larger in the direction of the pressure medium container 5 than in the direction of the pressure chamber 3.
  • FIGS. 24 and 25 This principle can be seen in FIGS. 24 and 25. It can be seen that the lower sealing lip 22 is much thinner and longer than the upper sealing lip 23. The upper sealing lip 23 is thus much stiffer than the lower sealing lip 22, as a result of which the associated passages 26 are opened at different pressures.
  • valve 25 shows a top view of the permeable membrane 49, which is arranged in the valve body 27.
  • FIGS. 21 to 25 The exemplary embodiments according to FIGS. 21 to 25 can thus be briefly described as follows.
  • valve 6 which is preferably arranged between the pressure medium container 5 and the master cylinder 1.
  • the valve 6 must enable the master cylinder 1 to be sucked in, generate a certain pressure when it starts quickly and, on the other hand, connect the master cylinder 1 to the pressure medium container 5, so that no residual pressure remains in the brake system.
  • Embodiment according to FIG. 21 The closing body 7 enables suction, the valve seat 21, which is biased by a spring 43, opens the way to one or more channels 46 from a certain pressure.
  • a throttled pressure medium connection (throttle bore) 19 enables pressure equalization of the brake system in the unactuated state.
  • the plunger 47 is provided here, which enables a pressure medium flow S2 into the pressure medium container 5 from a certain pressure.
  • Embodiments according to FIGS. 23, 24 The valve body 27 with a built-in permeable membrane 49 offers a space-saving design with a simple mode of action. By means of a corresponding stiffening and the interaction with the
  • Pressure medium container contour enable the sealing lips 22, 23 or the sealing lip 22 and the leaf spring 25 to perform the required functions.
  • valve 6 is fixed in the pressure medium container in a sealing manner.
  • the permeable membrane 49 ensures the residual pressure reduction in the Brake system with the advantage that it is less sensitive to dirt and less dependent on consistency than a throttle bore.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Transmission Of Braking Force In Braking Systems (AREA)

Abstract

L'invention concerne un maître-cylindre (1), notamment pour système de freinage hydraulique, comportant au moins une chambre de pression (3) formée dans un boîtier (2) du maître-cylindre (1) et au moins un alésage (4) prévu pour loger un réservoir de fluide hydraulique (5). Il est prévu une soupape (6) munie d'un corps de fermeture (7, 24), qui peut être déplacée dans une position d'ouverture ou de fermeture, en cas de pression différentielle entre la chambre de pression (3) et le réservoir de fluide hydraulique (5). Ladite soupape (6) permet, en position ouverte, un écoulement du fluide hydraulique S1 du réservoir de fluide hydraulique (5) à la chambre de pression (3) et en position fermée, un écoulement de fluide hydraulique S2 en sens inverse à celui de l'écoulement de fluide hydraulique S1, de la chambre de pression (3) au réservoir de fluide hydraulique (5). Afin de permettre, outre une réduction de la course à vide du maître-cylindre, un remplissage sous vide du système de freinage, il est prévu des éléments qui maintiennent en position ouverte le corps de fermeture (7, 24) soumis à une pression différentielle induisant une fermeture, suite au vide effectué pour permettre un remplissage sous vide, et permettent un déplacement du corps de fermeture (7, 24) en position fermée, en cas d'actionnement des freins.
EP03766364A 2002-07-30 2003-07-30 Maitre-cylindre Withdrawn EP1532031A1 (fr)

Applications Claiming Priority (7)

Application Number Priority Date Filing Date Title
DE10234541 2002-07-30
DE2002134541 DE10234541A1 (de) 2002-07-30 2002-07-30 Hauptzylinder-Behälter-Einheit
DE10321380 2003-05-12
DE10321380 2003-05-12
DE10321381 2003-05-12
DE10321381 2003-05-12
PCT/EP2003/008424 WO2004012974A1 (fr) 2002-07-30 2003-07-30 Maitre-cylindre

Publications (1)

Publication Number Publication Date
EP1532031A1 true EP1532031A1 (fr) 2005-05-25

Family

ID=31498921

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03766364A Withdrawn EP1532031A1 (fr) 2002-07-30 2003-07-30 Maitre-cylindre

Country Status (6)

Country Link
US (1) US7152406B2 (fr)
EP (1) EP1532031A1 (fr)
JP (1) JP2005534562A (fr)
KR (1) KR20050031465A (fr)
CN (1) CN100343100C (fr)
WO (1) WO2004012974A1 (fr)

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Publication number Priority date Publication date Assignee Title
JP5000411B2 (ja) * 2006-08-31 2012-08-15 日立オートモティブシステムズ株式会社 マスタシリンダおよびその製造方法
JP5507532B2 (ja) 2011-11-25 2014-05-28 日信工業株式会社 マスタシリンダ装置
FR2984264B1 (fr) * 2011-12-15 2014-06-27 Bosch Gmbh Robert Maitre cylindre avec systeme de limitation de flux
DE102012007380A1 (de) * 2012-04-12 2013-10-17 Lucas Automotive Gmbh Hauptbremszylinderanordnung für eine Kraftfahrzeug-Bremsanlage sowie integrales Dicht-Drossel-Element hierfür
DE102014213709A1 (de) * 2014-07-15 2016-01-21 Continental Teves Ag & Co. Ohg Bremsflüssigkeitsbehälter
DE102015205938A1 (de) 2015-04-01 2016-10-06 Continental Teves Ag & Co. Ohg Bremsgerät mit einem Arbeitsflüssigkeitsbehälter
GB201617506D0 (en) 2016-10-14 2016-11-30 Mennie Trevor M Brake control system
DE102016222148A1 (de) * 2016-11-11 2018-05-17 Continental Teves Ag & Co. Ohg Fluidbehälter mit einem strömungsoptimierten Anschlussstutzen
CN110203186A (zh) * 2019-05-28 2019-09-06 万向钱潮股份有限公司 一种带常闭阀的制动主缸

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DE1039858B (de) * 1953-05-11 1958-09-25 Schaefer Industriegesellschaft Rueckschlagventil fuer Hauptzylinder, insbesondere in hydraulischen Betaetigungsanlagen fuer Kraftfahrzeug-bremsen
US2809495A (en) * 1953-08-31 1957-10-15 Kelsey Hayes Co Master cylinder for hydraulic brake systems
US4773224A (en) * 1985-10-18 1988-09-27 Toyota Jidosha Kabushiki Kaisha Portless type master cylinder device with non return valve and restricted passage in parallel between pressure chamber and fluid reservoir
DE9016775U1 (de) * 1990-12-12 1992-04-09 Robert Bosch Gmbh, 7000 Stuttgart Rückschlagventil
US5557935A (en) 1995-05-23 1996-09-24 Kelsey-Hayes Company Apply-rate-independent fast-fill master cylinder
CN2275978Y (zh) * 1996-08-29 1998-03-11 东风汽车公司 阀门式活塞液压制动主缸
DE19639560A1 (de) 1996-09-26 1998-04-02 Bosch Gmbh Robert Hydraulische Fahrzeugbremsanlage
JP3984751B2 (ja) * 1998-09-07 2007-10-03 ボッシュ株式会社 マスタシリンダ
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US6405534B1 (en) * 1999-11-24 2002-06-18 Continental Teves, Inc. Evacuation and fill valve assembly and method for using the same
US6637201B2 (en) * 2001-11-07 2003-10-28 Bosch Braking Systems Co., Ltd. Master cylinder
GB0218167D0 (en) * 2002-08-06 2002-09-11 Meritor Heavy Vehicle Braking In line vacuum bleeding device

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See references of WO2004012974A1 *

Also Published As

Publication number Publication date
US20050269180A1 (en) 2005-12-08
CN1671585A (zh) 2005-09-21
US7152406B2 (en) 2006-12-26
JP2005534562A (ja) 2005-11-17
WO2004012974A1 (fr) 2004-02-12
KR20050031465A (ko) 2005-04-06
CN100343100C (zh) 2007-10-17

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