DE4016749A1 - Antilocking brake control valve for motor vehicle - has wheel cylinder valve mechanically linked and operated by single solenoid - Google Patents

Abstract

The wheel cylinders are linked to the master brake cylinder by normally open inlet valves and separated from the venting line by normally closed venting valves (5). A simple design has the two valves of each wheel brake linked by a mechanical linkage incorporating a spring element (15). A single solenoid (10) operates the two valves. The solenoid is normally unpowered and holds the vent valve closed and the inlet valve open. The spring element is selected to provide the optrimum algorythm for the two valves. A servo pump (3) provides the drive force for the brake modulation. The system is suitable for ABS or anti-wheelspin. ADVANTAGE - Only one solenoid required. Compact and simple design.

Description

The invention relates to a brake pressure control device, especially for motor vehicles, with an anti-lock control system (ABS) and / or a traction control system tem (ASR) with a fluid, especially hydrau mix, pressure fluid works, consisting of a main cylinders, one or more wheel cylinders for wheel brakes, a pressure modulator for changing the hydraulic Pressure in the wheel cylinders of the wheel brakes during a Brake pressure control mode, at least one motor-driven Pump for generating a fluid, in particular hydraulic pressure, an electronic regulator.

Generic, the subject of the invention is one Type of braking systems, such as in the German Offenlegungsschrift 37 31 603 is described. However, the application of the invention is not to this Limited type.

Such brake systems are with an anti-lock rule system and / or traction control system equipped. They have one or two auxiliary pumps. This auxiliary pump pen convey pressure medium during the anti-lock control mode into a pressure modulator. The pressure modulator comprises several re hydraulic valves. In particular, in the print module lator inlet and outlet valves provided that certain Wheel cylinders are assigned. The driver stage of the elek tronic controller controls these intake and exhaust valves corresponding to that in the controller  installed control algorithm. With the outlet valve open til and closed inlet valve will reduce pressure phase generated in the wheel cylinder. With the inlet closed valve and the exhaust valve is closed Constant pressure phase. With the inlet valve open and the exhaust valve is closed, pressure is restored construction phase reached.

Hydraulic circuits are also described been in which the intake valve has a throttling effect having. See also German patent application P 39 19 842.1.

In this patent application, an anti-lock, hydraulic brake system for a vehicle with a main cylinder, a pressure fluid collector, at least one Wheel brake connected to the main brake via a brake line cylinder and via a return line to the pressure with collector is connected, an electromagnetic actuated exhaust valve that enters the return line is introduced, and in its rest position the return line blocks and in its switch position the return line releases a throttle valve that enters the brake line is inserted and has two switch positions, with an unthrottled in the first switching position and a throttled connector in the second switch position between the wheel brake and the master brake cylinder exists, a pump that comes from the pressure fluid collector Sucks in pressure medium and via a pressure line in the Master cylinder promotes the sensor to detect the Angular speed of the wheel to be braked  and an electronic evaluation unit that the sensor evaluates signal and switching signals for the pump drive and generates the exhaust valve.

In the aforementioned German patent application is featured suggest that the throttle valve by means of a control line device is connected to the outlet of the pump, so that the pressure at the pump outlet the throttle valve from the first in the second switch position.

The aforementioned German patent application P 39 19 842.1 applies according to § 2, paragraph 2, patent law, as state of the art.

The US patent also belongs to the prior art font 40 90 739.

There is a braking system with anti-lock control described that is suitable for use in motorcycles or small motor vehicles. The system includes one Electromagnetically actuated anti-lock control valve that can take different positions: a normal position, a depressurization position and a blocking position tion between two pistons. The valve is replaced by a Spring applied, in the direction of the normal position. In this position the valve directs the brake pressure to the wheel cylinder. In anti-lock control mode the valve is moved to the pressure reduction position. The Valve is prevented from the pressure release position return to normal position as long as pressure is exercised by the master cylinder. The valve stays in the blocking position when the pressure medium supply is blocked.  

A bypass is provided over the control valve bridges. There is a narrow flow cross section in the bypass intended. This ensures that the second and the subsequent build up of pressure only a limited amount of brake fluid is made available.

Further details are in the aforementioned US patent refer to.

The invention is based on the following objects:

The manufacturing costs are basically to be reduced will. This is to be achieved in particular by saving Magnetic coils, electrical cables and connector pins respectively.

The one for installing the anti-lock control device necessary installation space should be reduced.

The applicability of the anti-lock rule according to the invention device should be more universal than this at the stand the technology is common. So an application for so-called called "open" and "closed" braking systems with anti blocking control may be possible. Open brake systems are those that are within the cycle of pressure by means of a pressure medium open to the atmosphere container is located. Closed systems are systems that have no open container for the pressure medium.  

The inventions are supposed to be prerequisites for this be created that the brake pressure control device integrated in the existing steel valve block of the control system can be.

With the object of the invention it should be possible to achieve the effect of a flow limiting valve. This means that when a nominal current is reached, this remains essentially the same despite fluctuations in Pressure levels, or despite fluctuations in Difference in pressure before and after the valve.

By nominal current is meant here that not more than one defined pressure medium volume per unit of time in Anti Locking control mode is supplied to the wheel cylinder, and independent of the level of pressure on the pumps pressure side, or on the master cylinder pressure page.

It is also one of the objects of the invention that in addition to avoiding undesirably high wheel cylinder pressures in control mode a quick pressure reduction in control mode occurs when pressure reduction is pre-selected by the control algorithm is written. The control quality should fundamentally be improved will.

The invention is also based on the object electromagnetically actuated in the prior art Actuated normally open valves, which act as intake valves act, save.  

With the invention, conditions for this should continue be created that the scheme regardless of Changes in viscosity and thus changes in Temperature of the pressure medium is. With the invention constant pressure gradients during control can be achieved.

It also belongs to the task, noise reduce or prevent during control mode.

In addition to reducing the effort for electrical Cables should also be reduced in size. It is also intended to be made possible by the invention the effort for the driver stage of the electroni reduce controller. In the valve unit for the Regulation is intended to be a simpler channel through the invention leadership compared to those of the prior art to be possible.

The tasks set according to the invention solved that the outlet assigned to a wheel cylinder valve in operative connection with that assigned to the wheel cylinder Neten inlet valve stands and trained and arranged net is that it is the inlet valve in its closed position Til opens the inlet valve and in its open position closes.

It can be provided that the closing body of the Exhaust valve and the closing body of the intake valve are connected to each other via a bondage device, which is designed and arranged so that the closure Exhaust valve body  the closing body of the inlet in its closed position valve opens or allows its opening, and that the closing body of the exhaust valve in its Open position of the closing body of the intake valve closes, or permits its closure.

It is also proposed that the exhaust valve be on Electromagnetically actuated in a manner known per se The normally closed valve (SG valve) is the one at Currentlessness of the actuating magnet its rest position, the closed position, occupies and at the same time the on opening valve opens or allows its opening, that when current is applied to the actuating magnet SG valve switch position, the open position and at the same time closes the inlet valve, resp wise its closure allows.

The restraining device can be a tension element and / or a Include pressure element.

A most preferred embodiment is that Tension element and pressure element by a pin (pressure and traction pin) that the closing body the exhaust valve and the intake valve with one each Push and pull pin is provided.

In particular, it can be provided that the bondage direction includes an aggregate, the relative movements the closing body of the inlet valve and the exhaust valve tils allows each other.  

In a further embodiment of the invention, it is proposed conditions that the push and pull pins of the closing body, which in particular have a spherical shape, by an aggregate are interconnected (connection unit), the Relative movements of the pins and thus the closing body to each other.

It has been found to be particularly useful that the connection unit from a with the pin of Closing body of the outlet valve connected housing, in particular sleeve (coupling housing), in which a compression spring (coupling spring) is housed, the a spreading force on the pins of the closing body and thus exercising on the closing body itself.

The desired control effects are described in one version Example achieved in that within the brake pressure control device with the master cylinder and Pump related room is provided (main cylinder pump chamber) that within the brake pressure rule device in connection with the wheel cylinder the space is provided (wheel cylinder space) that inside the brake pressure control device with the suction side the pump-related space is provided (Pump suction side space) that one between the main cylinder the pump chamber and the wheel cylinder chamber provided opening is closable by the inlet valve that a between vorese the wheel cylinder space and the pump suction side space opening can be closed by the outlet valve,  that between the master cylinder pump chamber and the Radzylin derraum a throttle device for the flow of the Pressure medium is provided.

In this context, it is also proposed that that the throttle device in a bypass line, the bridged the inlet valve and master cylinder pump chamber connects to the wheel cylinder space, is arranged and is preferably designed as an aperture.

Particular cost advantages are achieved in that the throttle device as preferably notch-shaped trained recess with a small flow cross-section is formed in the valve seat of the inlet valve, or that the throttle device as preferably notch-shaped trained recess with a small flow cross-section is formed in the closing body of the inlet valve.

In another embodiment suggested that two be on a line with each other connected wheel cylinder spaces are provided that the first wheel cylinder room and the master cylinder pump room are separable through the inlet valve that the second Wheel cylinder space and the pump suction side space through that Exhaust valve are separable.

A further development of this concept is that the first wheel cylinder space and the pump suction side space are separated by a seal and that the pin of the closing body of the exhaust valve in the seal between the first wheel cylinder space and the pump suction side space is sealingly led.  

For constructive execution of the operative connection between Inlet and outlet valve is proposed that the Connection unit between the pins of the inlet valve tils and exhaust valve from a housing, preferably consists of a coupling sleeve, which with the pin of the Exhaust valve is connected and a stop for one has frontal collar of the pin of the inlet valve, that a compression spring (coupling spring) is arranged in the housing is that on the bottom of the case and on the forehead term collar of the pin of the inlet valve acts and thus resiliently the closing body of the inlet valve and Exhaust valve closing body to a certain Holds distance that varies around the stroke of the collar in the housing is cash.

In addition, it can be provided that the closing body of the intake valve towards its valve seat is arranged biased by a spring.

In another category of embodiments it is proposed that flow in front of the wheel cylinder a valve unit is provided, which as a current limit tion valve element is formed and in particular at undesirably high pump and / or master cylinder pressure a constant essentially from the pump and / or Master cylinder pressure independent flow rate (nominal current), same amount of pressure medium per unit of time, caused in the wheel cylinder.

In particular, it can be provided that in the area a current limiting valve element of the wheel cylinder space is provided,  the one essentially from the pump and / or main cy Linderdruck independent nominal flow of pressure medium generated.

In a further embodiment of this idea is pre suggest that the flow limiting valve element Control that is movably arranged in the wheel cylinder space which includes the inlet valve and an orifice having the master cylinder pump chamber with the Connect wheel cylinder space that the control through the pressure difference between the master cylinder pump chamber and Wheel cylinder space is moved so that one on the control arranged control edge the mouth cross section of the Line to the wheel cylinder runs over so far that in the area a sniff of the mouth cross section and the control edge felling process is achieved.

In addition, it can be provided that the inlet valve Control element, preferably a control sleeve, is provided that a valve space in a Separates master cylinder pump chamber and a wheel cylinder chamber, by the pressure difference between master cylinder pumps space and wheel cylinder space is movable, which is an aperture with a narrowed flow cross section, which the master cylinder pump room with the wheel cylinder room connects that at higher pressure in the master cylinder pumps clear the control against the pressure of a tax spring in the direction of the mouth cross section of the line is arranged movably to the wheel cylinder that the control element has a control edge that crosses the muzzle can at least partially run over,  that the flow cross-section of the orifice, the position the control edge with regard to the mouth cross-section, the spring characteristic of the control spring, the size and Shape of the mouth cross section are designed so that through a shuffling process that is caused by the movements the control edge in the area of the mouth cross-section causes a current limiting effect for the Radzy linder is achieved that at a certain pressure like the build-up gradient in the wheel cylinder in the anti-lock control mo dus leads.

In a further embodiment of this embodiment it is proposed that a first wheel cylinder space for the inclusion of the control and a second Radzylin the space which is arranged upstream of the exhaust valve net is provided.

The valve body of the outlet valve can be used to save costs tils a recess, especially in the form of a notch have, which when the valve body is seated on the Valve seat forms a throttle flow cross section.

On the other hand, it can be provided that the valve seat the outlet valve has a recess, in particular in the form has a notch when the valve body is seated a throttle flow cross-section on the valve seat forms.

In another preferred embodiment provided that a control element without an inlet valve, preferably a control sleeve is provided,  the one valve chamber into a master cylinder pump chamber and separates a wheel cylinder space, which by the Druckdif reference between master cylinder pump chamber and wheel cylinder that is an orifice with a flow Cross section is provided, which the master cylinder pump Penraum connects with the wheel cylinder space that at higher Pressure in the master cylinder pump chamber counter the control against the pressure of a control spring towards the coin cable cross-section of the line to the wheel cylinder movable is arranged that the control element in the normal braking mode due to the higher pressure in the master cylinder pump chamber against the force of the control spring is shifted and pressure promotes medium in the wheel cylinder.

In a further embodiment of this embodiment it is proposed that a control element without inlet valves til, preferably a control sleeve, is provided that a valve chamber into a master cylinder pump chamber and separates a wheel cylinder space by the pressure difference between master cylinder pump chamber and wheel cylinder chamber that is an orifice with a flow cross Cut is provided, which the master cylinder pumps connects space with the wheel cylinder space that at higher Pressure in the master cylinder pump chamber counter the control against the pressure of a control spring towards the Mouth cross section of the line movable to the wheel cylinder is arranged that the control element has a control edge has at least partially the mouth cross-section can run over that the flow cross-section of the orifice, the position of the control edge  in terms of the muzzle cross section, the feather character teristics of the control spring, the size and shape of the muzzle cross-section are designed so that by a Sniffing process by the movements of the control edge is caused in the area of the mouth cross-section, achieved a current limiting effect for the wheel cylinder that leads to a certain pressure recovery gradient leads in the wheel cylinder in anti-lock control mode.

It can also be provided that the connection gregat between the pins of the inlet and outlet valves tils from a housing, in particular a coupling sleeve, exists, which is connected to the pin of the intake valve is and a stop for a frontal collar of the Pin of the exhaust valve has that in the housing Compression spring, in particular coupling spring, is arranged, on the bottom of the case and on the front The collar of the pin of the exhaust valve acts and is thus resilient the closing body of the exhaust valve and the closing body of the intake valve at a certain distance that around the stroke of the collar in the housing is variable that a physical separation between the pin of the closing body of the inlet valve and the closing body of the inlet valve tils exists.

The invention can further by an embodiment be realized, which is designed so that in terms of flow to the pressure side of the pump and / or of the master cylinder and a valve in front of the wheel cylinder chamber Unit is provided as a flow control valve element is formed  and especially in the case of undesirably high pumps and / or Master cylinder pressure is essentially constant Pump and / or master cylinder pressure independent through flow current (nominal current), equal amount of pressure medium per unit of time in the wheel cylinder.

It has proven to be particularly useful represents that the flow limiting valve element is a control element that is movably arranged in the wheel cylinder space is included, which has an aperture that the main connects the cylinder pump chamber to the wheel cylinder chamber, that the control element by the pressure difference between Master cylinder pump chamber and wheel cylinder chamber moved in this way is that a control edge arranged on the control element the mouth cross-section of the supply line from the pump, or the master cylinder, so far overrun, that in the area of the muzzle cross section and the tax edge a sniffing process is achieved.

In addition, it is proposed that the intake valve and having a control edge, preferably as a control sleeve is provided, the one valve space in a master cylinder pump room and a Radzylin separates the space by the pressure difference between Master cylinder pump chamber and wheel cylinder chamber movable is an orifice with a flow cross-section which has the master cylinder pump chamber with the Wheel cylinder room connects that at higher pressure in the main cylinder pump chamber the control edge of the control element against the pressure of a control spring in the direction of the mouth cross-section of the supply line from the pressure side the pump and / or  Master cylinder is movably arranged that the control edge at least partially run over the mouth cross-section can that the flow cross-section of the orifice, the Posi tion of the control edge with regard to the muzzle cross cut, the spring characteristic of the control spring, the Size and shape of the mouth cross-section formed in this way are that through a sniffing process by the Movements of the control edge in the area of the muzzle cross cut is caused, a current limiting effect is achieved for the wheel cylinder that to a certain Pressure restoration gradient in the wheel cylinder in the anti blocking control mode leads.

A particularly inexpensive version consists in that the movable control element as a sleeve with a outer ring groove is formed that one through the ring edge created as a control edge together with the Mouth cross section of the supply line to the pump and / or Master cylinder carries out the sniffing process.

The following advantages are achieved by the invention:

The tasks are solved.

The manufacturing costs are fundamentally reduced. The effort for the electrical components and lines gene, especially the effort for solenoids, connectors Pin and for the driver level within the electronics controller is considerably reduced. The installation space for the control components is compared to the status of technology smaller. The brake pressure control device can in the existing steel valve block of the control system to get integrated.  

The control quality is increased. The invention succeeds it to achieve the effect of a flow limiting valve. Rapid pressure reduction in control mode is achieved.

Further details of the invention, the task and the advantages achieved are the following description of embodiments of the invention.

These embodiments are illustrated in FIG Figures explained.

Figs. 1, 2, 4, 5 and 7 each show a Ausführungsbei game of the invention.

Fig. 3 shows a detail to the embodiments of FIGS. 1 and 2.

Fig. 6 shows a variant of the embodiments according to FIGS. 4 and 5.

In the following description of the execution games of the invention is based on a prior art assumed that he is in the form of the above Represents fonts.

The descriptions and figures of these writings can to explain the starting point for the following described embodiments of the invention be drawn.  

In Figs. 1 and 2, two exemplary embodiments of a combination of an inlet and an Auslaßven TILs are shown. The outlet valve is designed as a normally closed valve, the inlet valve is actuated by the outlet valve. The following description of the exemplary embodiments according to FIGS. 1 and 2 can serve to supplement the descriptions of the exemplary embodiments according to FIGS. 4 to 7 which follow below.

In Figs. 1 and 2 of the main cylinder carries the reference numeral 1, the wheel cylinder is indicated by 2. The pump has the reference number 3 . The solenoid for the exhaust valve is designated 4 . The closing body of the exhaust valve is spherical and bears the reference number 5 . The closing body of the inlet valve is also spherical and bears the reference number 6 . With 7 a low-pressure accumulator is called net.

In Figs. 1 and 2, the closing body of the outlet valve is actuated by a tie rod 8 5. When the solenoid 4 is supplied with current, the tie rod 8 pulls the closing body upward and opens the cross section 9 of the outlet valve.

The outlet valve is designated in its entirety with 10 . The valve seat of the exhaust valve is mounted in an intermediate plate 90 . The entirety of the inlet valve bears the reference number 11 .

Between the closing body 5 of the exhaust valve and the closing body 6 of the intake valve there is a coupling via the pins 12 , 13 , the housing 14 . In the housing, a compression spring 15 is arranged, which holds the front collar 16 of the pin 13 of the closing body 6 of the inlet valve against the lower stop 17 of the housing. The compression spring 15 is supported on the bottom 39 of the hous ses.

18 with 1 and 2 is a bypass line in the FIG., Which bridges the inlet valve and which has a shutter 19.

As stated at the outset, the closing body of the inlet valve is actuated indirectly by the closing body of the outlet valve via the components 12 , 14 , 13 .

The mode of operation of the object of the exemplary embodiment according to FIG. 1 is described below:

In the normal braking mode, pressure medium is conveyed by actuating the master cylinder 1 via the line 20 into the main cylinder chamber 21 . In this situation, the inlet valve 11 is open. Pressure medium flows into the wheel cylinder chamber 22 and from there via the line 23 into the wheel cylinder 2 .

In the anti-lock control mode, the pump 3 is started by starting the electric drive motor based on an output signal from the controller.

In addition, current is applied to the magnet coil 4 by a further output signal from the controller. The closing body 5 of the exhaust valve is raised via the armature 8 and thus the cross section 9 of the exhaust valve is opened.

At the same time, the cross-section 24 of the inlet valve is closed by the closing body 6 via the connection described between the closing body of the exhaust valve and the closing body of the inlet valve. The closing body 6 of the inlet valve is under the pressure of the spring 25 .

The direct connection between the master cylinder and the wheel cylinder is thus interrupted. The pump 3 promotes pressure medium through line 58 in the master cylinder pump room.

Pressure medium can only throttled flow back through the aperture 19 in the wheel cylinder 22nd It flows in this situation, over the cross section of the exhaust valve 9 more pressure medium from the wheel cylinder 22 into the pump 27 as saugseitenraum can flow 19 pressure fluid into the wheel cylinder chamber 22 via the aperture.

The pump suction side space is connected via line 28 to the suction side of pump 3 . A branch line 29 connects the suction line to a low-pressure accumulator 7 .

In the embodiment of FIG. 2, the pump suction side space 34 is arranged between an intermediate plate 91 having the valve seat of the outlet valve and an intermediate plate 94 . The intermediate plate 94 has a seal that guides the pin 12 .

In the exemplary embodiment according to FIG. 2, there are two wheel cylinder spaces, namely a first wheel cylinder space 30 and a second wheel cylinder space 31 . The first Radzy linderraum can be connected to the Hauptzy linderraum 21 via the inlet valve 11 . The second wheel cylinder chamber 31 , which is connected to the first wheel cylinder chamber via the line 32 , is located upstream of the outlet valve with respect to the direction of flow.

In the exemplary embodiment according to FIG. 2, the wheel cylinder pressure thus loads the closing body 5 of the exhaust valve in the normal braking mode. As a result, the closing body 5 is pressed onto the valve seat, which leads to a higher seal. The valve seat is mounted in an intermediate plate 91 .

The following is a description of the normal braking mode of the exemplary embodiment from FIG. 2.

When the master cylinder 1 is actuated, which is provided with the pressure medium container 26 , brake fluid is conveyed into the master cylinder space via the line 20 . From there, the brake fluid enters the first Radzy cylinder chamber 30 and via line 23 into the wheel cylinder. At the same time, pressure medium flows via line 32 into second wheel cylinder space 31 .

In the anti-lock control mode, see description of FIG. 1, the pump 3 is started and the solenoid 4 is supplied with current. As described, the closing body 5 is raised and opens the cross section of the exhaust valve. The closing body 6 of the inlet valve closes, see Fig. 1, the inlet valve.

The pump 3 thus delivers against the aperture 19 . Therefore, only a small amount of pressure medium flows through the orifice 19 into the first wheel cylinder space 30 . A larger amount of pressure medium flows from the second wheel cylinder space 31 via the open exhaust valve, the pump suction side space 34 , via the line 28 to the suction side of the pump 3 .

This leads to a pressure reduction in the wheel cylinder.

In Fig. 3, the valve seat 36 of the intake valve is shown in an enlarged view. It has a notch 37 . This notch acts as a throttle opening or diaphragm when the closing body 6 of the inlet valve rests on the valve seat. With 38 the opening of the inlet valve is designated.

In a corresponding manner, one, for example designed as a notch, throttle opening in the valve seat of the inlet valve may be provided.

Through the throttle openings in the closing body or in Valve seat can be a separate bypass line with cover, which bypasses the inlet valve can be saved.  

In the exemplary embodiment according to FIG. 4, a coupling is provided between the closing body 5 of the exhaust valve 10 and the closing body 6 of the intake valve 11 , as was described with reference to FIG. 1.

In Fig. 4, 35 pressure medium is conveyed in the normal braking mode by the master cylinder of 1 via line 33 into the master cylinder pump chamber. The inlet valve 11 is open, pressure medium therefore enters the first wheel cylinder chamber 40 and from there via the mouth cross-section 41 of the line 42 to the wheel cylinder 2 . The second wheel cylinder space 44 is filled with pressure medium through the line 43 .

In the anti-lock control mode, the pump 3 is started in FIG. 4. See also the description of Fig. 1. In addition, the inlet valve, which is designated in its entirety with 11 , see also the description of Fig. 1. The closing body 6 sits on the valve seat.

The pump delivers via line 59 in the Hauptzylin derpumpenraum 35 and thus against the lower end wall of the control sleeve 48 and against the aperture 49th The control sleeve 48 thereby moves upwards. The aperture 49 allows only a small volume flow.

At the same time, the outlet valve 10 is opened, that is to say the closing body 5 is lifted off the valve seat in the intermediate plate 92 . The flow cross section 9 is released.

Pressure medium can now get from the wheel cylinder 2 via the line 43 through the second wheel cylinder space 44 into the pump suction side space 45 . The pump suction side space is separated from the first wheel cylinder space by an intermediate plate 76 with a seal. The pump suction side space is connected via line 46 to the suction side of the pump 3 . This line 46 has an aperture 47 . It is also connected to the low pressure accumulator 7 .

The flow cross section, the orifice 49 arranged in the bottom of the control sleeve 48 , the axial length of the control sleeve, that is the position of the control edge 50 of the control sleeve, the characteristic of the control spring 51 , the size and shape of the mouth cross section 41 of the mouth of the line 42 to the wheel cylinder are dimensioned or arranged so that the control edge 50 partially runs over the mouth cross section 41 of the line to the wheel cylinder. There is a sniffing process that takes place in the area of the control edge and the muzzle cross section. There is the effect of a Strombe limit valve. This means that when a nominal current (pressure medium volume per unit of time) is reached, an essentially constant pressure medium flow to the Radzy cylinder does not matter how high the pump and / or master cylinder pressure is.

With 52 a stop is designated, which positions the control sleeve in its rest position.

In the embodiment according to FIG. 5, a simplification compared to the previously described exemplary embodiments has been carried out.

In the embodiment according to FIG. 5, the usual inlet valve with closing body and valve seat is missing. The main cylinder pump chamber 53 is separated from the first wheel cylinder chamber 54 by the control sleeve 55 , which is biased by a control spring 95 . A connection between the master cylinder pump chamber and the wheel cylinder chamber exists only through the aperture 56 in the bottom of the control sleeve 55 .

In the normal braking mode, the master cylinder 1 conveys pressure medium into the master cylinder pump chamber 53 via the line 57 . The pressure in the master cylinder pump chamber pushes the control sleeve upwards.

In this way, pressure medium from the first Radzylin derraum, which is closed by the plate 60 , is pressed via the line 61 into the wheel cylinder 2 .

In the anti-lock control mode, the pump 3 is started up and delivers pressure medium via the line 67 into the master cylinder pump chamber 53 . The outlet valve is opened.

Via line 62 , pressure medium comes from the wheel cylinder into the second wheel cylinder chamber 63 and from there via the opened outlet valve 10 into the pump suction chamber 64 . Pressure medium is conveyed from the pump suction chamber via line 65 to the suction side of the pump. Here, too, the line 65 has an aperture 66 . The line 65 is connected to the low pressure accumulator 7 .

In the anti-lock control mode, the control sleeve 55 moves by the pump pressure in the master cylinder pump chamber 53 further upward, so that the control edge 68 of the control sleeve 55 performs a sniffing process together with the mouth cross section of the line 61 to the wheel cylinder, similar to that described in connection with FIG. 4 .

Also in the embodiment of Fig. 5 have the spring characteristic of the control spring, the axial extension of the control sleeve, that is the position of the control edge, the size and shape of the mouth cross section of the supply line 61 to the wheel cylinder, and the flow cross-section of the aperture 56 in the bottom of the control sleeve be coordinated so that it comes to the desired Schnüffelvor gear in the area of the mouth cross section 69 of the line to the wheel cylinder.

In this embodiment, too, the effect becomes a Flow limiting valve as described above, achieved by the sniffing process.

FIG. 6 shows an alternative to the bondage according to FIG. 1. There is a physical separation between the closing body 6 of the inlet valve 11 and the pin 70 .

The pin 70 is provided at its upper end with a sleeve 71 which has a stop 72 . The pin 73 , which is connected to the closing body 5 of the exhaust valve 10 , projects into the sleeve. The pin 73 is guided in the intermediate plate 93 through a seal. At its lower end, this pin carries a collar 74 which , when the outlet valve 10 is opened , that is to say when the valve body 5 is raised , pulls the pin 70 upward via the stop and the sleeve. A compression spring 96 is arranged between the bottom of the housing 71 and the collar 74 .

The closing body 6 of the inlet valve 11 is under the pressure of the spring 75 which, when the outlet valve is open, that is to say when the pin 70 is pulled up, presses the closing body 6 of the inlet valve against the valve seat of the inlet valve.

It is therefore an effectually reverse conception compared to the coupling of FIGS. 1 to 5. In FIGS. 1 to 5, see for example FIG. 4, the closing body of the inlet valve is firmly connected to a pin.

In the exemplary embodiment according to FIG. 7, a coupling is provided between the closing body 5 of the exhaust valve 10 and the closing body 6 of the intake valve 11 , as was described with reference to FIG. 1.

The special feature of the exemplary embodiment according to FIG. 7 is that an intermediate plate with a seal, as denoted by 76 in FIG. 4, is missing in FIG. 7.

In the normal braking mode, master cylinder 1 delivers pressure medium into master cylinder pump chamber 77 via line 89 .

Pressure medium enters the wheel cylinder chamber 78 via the opened inlet valve 11 . From there, the pressure medium is conveyed via line 79 to the wheel cylinder 2 .

In the anti-lock control mode, the pump 3 is started up. It conveys pressure medium into the master cylinder pump chamber 77 via the line 80 .

In the control mode, the inlet valve 11 is closed and the outlet valve 10 is opened as described. Pressure medium can be conveyed from the wheel cylinder 2 via the line 79 to the wheel cylinder chamber 78 , via the flow cross-section 9 of the outlet valve, the pump suction side chamber 81 , the line 82 to the suction side of the pump.

At the same time, a pressure is built up by the pump in the master cylinder pump chamber 77 which is higher than the pressure in the wheel cylinder chamber 78 . Due to the resulting pressure difference, the sleeve 83 , which is provided with an extension 84 and a control edge 85 , moves upward. The control edge 85 is formed by an annular groove 97 in the extension 84 . As a result of the movement of the sleeve 83 upward, the control edge 85 of the extension comes into the region of the mouth cross section 86 of the feed line to the pump 3 and the master cylinder 1 .

In this situation there is a sniffing process. The position of the control edge 85 , the shape, size and position of the orifice cross-section 86 , the characteristic of the spring 87 , the flow cross-section of the orifice 88 , which is located in the bottom of the sleeve, are coordinated with one another in such a way that the current-limiting effect described above occurs .

List of items

1 master cylinder
2 wheel cylinders
3 pump
4 solenoid
5 exhaust valve closing body
6 inlet valve closing body
7 low pressure accumulators
8 tie rods
9 cross section, opening
10 exhaust valve
11 inlet valve
12 pin
13 pin
14 housing
15 compression spring
16 fret
17 stop
18 bypass line
19 aperture
20 line
21 master cylinder pump chamber
22 wheel cylinder compartment
23 line
24 cross section, opening
25 spring
26 pressure medium container
27 Pump suction side room
28 line
29 line
30 first wheel cylinder room
31 second wheel cylinder space
32 line
33 line
34 Pump suction side space
35 master cylinder pump chamber
36 valve seat
37 notch
38 opening
39 floor
40 first wheel cylinder room
41 Mouth cross section
42 line
43 line
44 second wheel cylinder space
45 pump suction side space
46 line
47 aperture
48 control sleeve, control element
49 aperture
50 control edge
51 control spring
52 stop
53 master cylinder pump chamber
54 first wheel cylinder compartment
55 control sleeve, control element
56 aperture
57 line
58 line
59 line
60 plate
61 line
62 management
63 second wheel cylinder compartment
64 pump suction side space
65 line
66 aperture
67 line
68 control edge
69 Muzzle cross section
70 pen
71 sleeve
72 stop
73 pen
74 fret
75 spring
76 intermediate plate
77 master cylinder pump chamber
78 wheel cylinder space
79 line
80 line
81 Pump suction side room
82 line
83 sleeve, control
84 continuation
85 control edge
86 muzzle cross-section
87 spring
88 aperture
89 management
90 intermediate plate
91 intermediate plate
92 intermediate plate
93 intermediate plate
94 intermediate plate
95 control spring
96 compression spring
97 ring groove

Claims (32)

1. Brake pressure control device, in particular for motor vehicles, with an anti-lock control system (ABS) and / or a traction control system (ASR), which works with a fluid, in particular hydraulic, pressure medium, consisting of a master cylinder, one or more wheel cylinders for wheel brakes, a pressure modulator for the change in the hydraulic pressure in the wheel cylinders of the wheel brakes during a brake pressure control mode, at least one motor-driven pump for generating a fluid, in particular hydraulic pressure, an electronic controller, characterized in that the outlet valve ( 10 ) associated with a wheel cylinder is in operative connection with the the wheel cylinder assigned inlet valve ( 11 ) and is designed and arranged so that it opens the inlet valve in its closed position and closes the inlet valve in its open position. 2. Brake pressure control device according to claim 1, characterized in that the closing body ( 5 ) of the Auslaßven valve and the closing body ( 6 ) of the inlet valve are connected to one another via a captive device which is designed and arranged such that the closing body of the exhaust valve in its closed position Closing body of the inlet valve opens or allows its opening, and that the closing body of the Auslaßven valve closes the closing body of the inlet valve in its open position, or permits its closing. 3. Brake pressure control device according to claim 1 and 2, characterized in that the outlet valve ( 10 ) is a known electromagnetically actuated normally closed valve (SG valve) which assumes its rest position, the closed position when the actuating magnet is de-energized and at the same time the inlet valve ( 11 ) opens or permits its opening, which, when current is applied to the actuating magnet, assumes the SG valve switching position, the open position, and at the same time closes the inlet valve or permits its closing. 4. Brake pressure control device according to one or more of the preceding claims, characterized in that the captive device comprises a tension element. 5. Brake pressure control device according to one or more of the preceding claims, characterized in that the restraining device comprises a pressure element.   6. Brake pressure control device according to one or more of the preceding claims, characterized in that the closing body ( 5 ) of the exhaust valve and the closing body ( 6 ) of the intake valve are each provided with a push and pull pin ( 12 , 13 ). 7. Brake pressure control device according to one or more of the preceding claims, characterized in that the captive device comprises an assembly that Relative movements of the closing body of the inlet valve and the exhaust valve to each other. 8. Brake pressure control device according to one or more of the preceding claims, characterized in that the pressure and tension pins of the closing body, which in particular have a spherical shape, are connected to one another by an assembly (connecting assembly), the relative movements of the pins ( 12 , 13 ) and so that the closing body ( 5 , 6 ) allows each other. 9. Brake pressure control device according to one or more of the preceding claims, characterized in that the connecting unit consists of a housing ( 14 ), in particular a sleeve (coupling housing) connected to the pin ( 12 ) of the closing body ( 5 ) of the exhaust valve, in which a compression spring ( 15 ) (coupling spring) is housed, which exerts a spreading force on the pins ( 12 , 13 ) of the closing body and thus on the closing body ( 5 , 6 ) itself. 10. Brake pressure control device according to one or more of the preceding claims, characterized in that within the brake pressure control device with the master cylinder ( 1 ) and the pump ( 3 ) in communication space is provided (master cylinder pump chamber) ( 21 ) that within the brake pressure control device the wheel cylinder ( 2 ) communicating space is provided (wheel cylinder space) ( 22 ) that within the brake pressure control device is a space in communication with the suction side of the pump (pump suction side space) ( 27 ) that a between the main cylinder pump space ( 21 ) and the wheel cylinder chamber ( 22 ) provided opening ( 24 ) can be closed by the inlet valve ( 11 ), that an opening ( 9 ) provided between the wheel cylinder chamber ( 22 ) and the pump suction side chamber ( 27 ) can be closed by the outlet valve ( 10 ), that between the master cylinder pump chamber ( 21 ) and the Radzy cylinder chamber ( 22 ) a throttle device ( 19 ) is provided for the flow of the pressure medium. 11. Brake pressure control device according to one or more of the preceding claims, characterized in that the throttle device ( 19 ) in a bypass line ( 18 ) which bridges the inlet valve ( 11 ) and Hauptzy cylinder pump chamber ( 21 ) with the wheel cylinder chamber ( 22 ) is arranged and is preferably designed as an aperture. 12. Brake pressure control device according to one or more of the preceding claims, characterized in that the throttle device is designed as a preferably notch-shaped recess ( 37 ) with a small flow cross-section in the valve seat ( 36 ) of the inlet valve ( 11 ). 13. Brake pressure control device according to one or more of the preceding claims, characterized in that the throttle device as preferably notch-shaped trained recess with a small flow cross-section is formed in the closing body of the inlet valve. 14. Brake pressure control device according to one or more of the preceding claims, characterized in that two Radzy cylinder spaces ( 30 , 31 ) connected to one another are provided in such a way that the first wheel cylinder space ( 30 ) and the master cylinder pump space ( 35 ) through the inlet valve ( 11 ) are separable that the second wheel cylinder space ( 31 ) and the Pumpensaugsei tenraum ( 34 ) can be separated by the outlet valve ( 10 ). 15. Brake pressure control device according to one or more of the preceding claims, characterized in that the first wheel cylinder space ( 30 ) and the pump suction side space ( 34 ) are separated by an intermediate plate ( 94 ) with a seal. 16. Brake pressure control device according to one or more of the preceding claims, characterized in that the pin ( 12 ) of the closing body ( 5 ) of the Auslaßven valve ( 10 ) in the seal of the intermediate plate ( 94 ) is guided. 17. Brake pressure control device according to one or more of the preceding claims, characterized in that the connecting unit between the pins ( 12 , 13 ) of the inlet valve ( 11 ) and outlet valve ( 10 ) consists of a housing ( 14 ), preferably of a coupling sleeve, which with the pin ( 12 ) of the exhaust valve is the verbun and has a stop ( 17 ) for a front collar ( 16 ) of the pin ( 13 ) of the inlet valve that a compression spring ( 15 ) (coupling spring) is arranged in the housing ( 14 ), which acts on the bottom ( 39 ) of the housing ( 14 ) and on the front collar ( 16 ) of the pin ( 13 ) of the inlet valve and thus resiliently the closing body ( 6 ) of the inlet valve and the closing body ( 5 ) of the outlet valve at a certain distance holds, which is variable by the stroke of the collar ( 16 ) in the housing ( 14 ). 18. Brake pressure control device according to one or more of the preceding claims, characterized in that the closing body ( 6 ) of the inlet valve ( 11 ) is arranged biased towards its valve seat by a spring ( 25 ). 19. Brake pressure control device, in particular for power vehicles with an anti-lock braking system (ABS) and / or a traction control system (ASR), the with a fluidic, especially hydraulic, pressure medium works, consisting of a master cylinder, a or several wheel cylinders for wheel brakes, a pressure mo dulator for changing the hydraulic pressure in the wheel cylinders of the wheel brakes during  a brake pressure control mode, at least one motor transmission benen pump for generating a fluidic, in particular hydraulic pressure, an electronic regulator, esp especially according to one or more of the preceding Claims, characterized in that flow a valve assembly is provided in front of the wheel cylinder, which is designed as a current limiting valve element and especially in the case of undesirably high pumps and / or Master cylinder pressure is essentially constant Pump and / or master cylinder pressure independent through flow current (nominal current), equal amount of pressure medium per unit of time in the wheel cylinder. 20. Brake pressure control device according to one or more of the preceding claims, characterized in that in the area of the wheel cylinder space ( 40 ) a current limiting valve element is provided which has a nominal flow of the pressure medium for the wheel cylinder ( 2 and 3) which is independent of the pump and / or master cylinder pressure ) generated. 21. Brake pressure control device according to one or more of the preceding claims, characterized in that the flow limiting valve element comprises a control element which is arranged movably in the wheel cylinder chamber ( 40 ), which has the inlet valve ( 11 ) and an orifice ( 49 ) which the master cylinder pump chamber ( that the control element (48) is 35) connected to the wheel cylinder chamber (40) is moved by the pressure difference between Hauptzylinderpum penraum (35) and said wheel cylinder (40), that arranged on the control element (48) control edge (50) of the mouth cross-section (41 ) runs over the line ( 42 ) to the wheel cylinder ( 2 ) so far that a sniffing process is achieved in the region of the mouth cross section ( 41 ) and the control edge ( 50 ). 22. Brake pressure control device according to one or more of the preceding claims, characterized in that a control element having the inlet valve ( 11 ), preferably a control sleeve ( 48 ), is provided which separates a valve chamber into a master cylinder pump chamber ( 35 ) and a wheel cylinder chamber ( 40 ) , which is movable by the pressure difference between the master cylinder pump chamber ( 35 ) and the wheel cylinder chamber ( 40 ), which has an orifice ( 49 ) with a narrow flow cross section, which connects the master cylinder pump chamber ( 35 ) with the Radzy cylinder chamber ( 40 ), that at higher pressure in Main cylinder pump chamber ( 35 ) the control element ( 48 ) against the pressure of a control spring ( 51 ) in the direction of the mouth cross section ( 41 ) of the line ( 42 ) to the wheel cylinder ( 2 ) is arranged such that the control element ( 48 ) has a control edge ( 50 ), which can at least partially run over the mouth cross section ( 41 ) that the current gsquerschnitt the aperture ( 49 ), the position of the control edge ( 50 ) with respect to the muzzle cross-section ( 41 ), the spring characteristic of the control spring ( 51 ), the size and shape of the muzzle cross-section ( 41 ) are designed so that by a Schüffelvorgang, which is caused by the movements of the control edge ( 50 ) in the region of the orifice cross section ( 41 ), a current limiting effect for the wheel cylinder ( 2 ) is achieved, which leads to a certain pressure recovery gradient in the wheel cylinder in the anti-lock control mode. 23. Brake pressure control device according to one or more of the preceding claims, characterized in that a first wheel cylinder chamber ( 40 ) for receiving the control element and a second wheel cylinder chamber ( 44 ), which is arranged upstream of the outlet valve, are provided. 24. Brake pressure control device according to one or more of the preceding claims, characterized in that the valve body of the exhaust valve has a recess, in particular in the form of a notch, which when opening the valve body sit on the valve seat a throttle flow cross section forms. 25. Brake pressure control device according to one or more of the preceding claims, characterized in that the valve seat of the exhaust valve has a recess, in particular in the form of a notch, which when Seat the valve body on the valve seat Throttle flow cross section forms. 26. Brake pressure control device according to one or more of the preceding claims, characterized in that a control element ( 55 ) without an inlet valve, preferably a control sleeve, is provided which separates a valve chamber into a master cylinder pump chamber ( 53 ) and a Radzylin derraum ( 54 ) which is determined by the pressure difference between the master cylinder pump chamber (53) and said wheel cylinder (54) is movably mounted, which is provided with a flow cross-section provided in the control element (55) comprises a diaphragm (56) which connects the master cylinder pump chamber (53) with the Radzylin derraum (54) that in Higher pressure in the Hauptzy cylinder pump chamber ( 53 ) the control element ( 55 ) against the pressure of a control spring ( 95 ) in the direction of the mouth cross section ( 69 ) of the line ( 61 ) to the wheel cylinder ( 2 ) is movably arranged that the control element ( 55 ) due to the higher pressure in the main cylinder chamber ( 53 ) against the force of the control spring ( 95 ) is moved and pressure medium in the wheel cylinder ( 2 ) promotes. 27. Brake pressure control device according to one or more of the preceding claims, characterized in that a control element without an inlet valve, preferably a control sleeve ( 55 ), is provided which separates a valve chamber into a master cylinder pump chamber ( 53 ) and a wheel cylinder chamber ( 54 ) by the pressure difference between the master cylinder pump chamber and said wheel cylinder is movably provided in the control sleeve, a diaphragm (56) having a flow cross section which connects the master cylinder pump chamber (53) with the wheel cylinder chamber (54), in that the pump chamber at a higher pressure in the master cylinder (53) the control ( 55 ) against the pressure of a control spring ( 95 ) in the direction of the muzzle cross section ( 69 ) of the line ( 61 ) to the wheel cylinder ( 2 ) is movably arranged that the control element ( 55 ) has a control edge ( 68 ) which Mouth cross section ( 69 ) can at least partially run over that the flow cross section d he aperture ( 56 ), the position of the control edge ( 68 ) with respect to the muzzle cross-section ( 69 ), the spring characteristic of the control spring ( 95 ), the size and shape of the muzzle cross-section ( 69 ) are designed so that by a Schüffelvorgang, the caused by the movements of the control edge ( 68 ) in the region of the mouth cross-section ( 69 ), a current limiting effect for the wheel cylinder ( 2 ) is achieved, which leads to a certain pressure restoration gradient in the wheel cylinder in anti-lock control mode. 28. Brake pressure control device according to one or more of the preceding claims, characterized in that the connecting unit between the pins of the inlet and outlet valve consists of a housing, in particular a coupling sleeve ( 71 ), which with the pin ( 70 ) of the inlet valve ( 11 ) is connected and a stop ( 72 ) for a front collar ( 74 ) of the pin ( 73 ) of the exhaust valve ( 10 ) that in the housing ( 71 ) a compression spring ( 96 ), in particular coupling spring, is arranged, which on the Bottom of the housing ( 71 ) and on the front collar ( 74 ) of the pin ( 73 ) of the exhaust valve ( 10 ) acts and thus resiliently holds the closing body ( 5 ) of the exhaust valve and the closing body ( 6 ) of the intake valve at a certain distance, which around the stroke of the collar ( 74 ) in the housing ( 71 ) is variable that a physical separation between the pin ( 70 ) of the closing body ( 6 ) of the inlet valve ( 11 ) and the Schl pouring body ( 6 ) of the inlet valve. 29. Brake pressure control device, in particular for power vehicles with an anti-lock braking system (ABS) and / or a traction control system (ASR), the with a fluidic, especially hydraulic, pressure medium works, consisting of a master cylinder, a or several wheel cylinders for wheel brakes, one pressure modulator for changing the hydraulic pressure in the wheel cylinders of the wheel brakes during a brake pressure control mode, at least one motor-driven pump to generate a fluidic, especially hydraulic pressure, an electronic regulator, in particular according to one or more of the preceding claims, characterized in that flow according to the pressure side of the pump and / or the master cylinder and in front of the Wheel cylinder space a valve unit is provided, which is designed as a current limiting valve element and especially when the pump and / or main are undesirably high cylinder pressure a constant essentially from the pump and / or master cylinder pressure independent flow rate (Nominal current), equal amount of pressure medium per time unit in the wheel cylinder. 30. Brake pressure control device according to one or more of the preceding claims, characterized in that the flow limiting valve element comprises a control element ( 83 ) which is movably arranged in the wheel cylinder chamber ( 78 ), which has an aperture ( 88 ) which with the master cylinder pump chamber ( 77 ) the wheel cylinder chamber (78) connects that the control element (83) is moved by the pressure difference between the master cylinder pump chamber (77) and said wheel cylinder (78), that arranged on the control element (83) control edge (85) of the mouth cross-section (86) of the feed line ( 80 ) by the pump ( 3 ), or the master cylinder ( 1 ), overrun so far that a sniffing operation is achieved in the area of the muzzle cross section ( 86 ) and the control edge ( 85 ). 31. Brake pressure control device according to one or more of the preceding claims, characterized in that a control element ( 83 ), preferably a control sleeve, having an inlet valve ( 11 ) and a control edge ( 85 ) is provided, which has a valve chamber in a master cylinder pump chamber ( 77 ) and a wheel cylinder chamber (78) separates the cylinder pump chamber by the pressure difference between the main (77) and said wheel cylinder (78) is movable, comprising a diaphragm (88) having a flow cross section which connects the master cylinder pump chamber (77) with the wheel cylinder chamber (78) that at higher pressure in the master cylinder pump chamber ( 77 ) the control edge ( 85 ) of the control element ( 83 ) against the pressure of a control spring ( 87 ) in the direction of the mouth cross-section ( 86 ) of the feed line ( 80 , 89 ) from the pressure side of the pump ( 3 ) and / or master cylinder ( 1 ) is movably arranged so that the control edge ( 85 ) the mouth cross section ( 86 ) to can at least partially run over that the flow cross section of the orifice ( 88 ), the position of the control edge ( 85 ) with respect to the orifice cross section ( 86 ), the spring characteristic of the control spring ( 87 ), the size and shape of the orifice cross section ( 86 ) so are designed so that a sniffing process, which is caused by the movements of the control edge ( 85 ) in the region of the mouth cross-section ( 86 ), a current limiting effect for the wheel cylinder is achieved, which leads to a certain pressure restoration gradient in the wheel cylinder ( 2 ) in anti-lock control mode. 32. Brake pressure control device according to one or more of the preceding claims, characterized in that the movable control element ( 83 ) is designed as a sleeve with an outer annular groove ( 97 ) that an edge ( 85 ) formed by the annular groove as a control edge together with the muzzle cross-section ( 86 ) the supply line of pump ( 3 ) and / or master cylinder carries out the sniffing process.