DE20122549U1 - Brake valve for trailers has first no-return valve rendered ineffective when supply connection has no pressure - Google Patents

Abstract

The valve unit has a valve (8) with two hoses (30, 31), a supply connection, a brake pre-setting connection, a container connection and a brake pressure connection. When the supply connection is pressurized, the pressure at the brake pressure connection depends dependent on the pressure at the brake pre-setting connection. The first no-return valve is rendered ineffective when the supply connection has no pressure.

Description

The The invention relates to a trailer brake valve according to the generic term of claim 1

Such a trailer brake valve is out of DE 28 10 850 A1 known.

In the known trailer brake valve for a two-line pressure medium brake system via the clutch hose "brake" fed pneumatic brake signal air flow amplified via a relay valve contained in the trailer brake valve [there control pressure chamber ( 6 ), Relay piston ( 5 ), Relay piston extension ( 28 ), Exhaust valve ( 26 . 28 ), Inlet valve ( 26 . 27 ), Brake pressure chamber ( 8th )] as brake pressure at the brake cylinder connections [there ( 9 ) 10 )] for the brake cylinders.

As a further function, the breakaway protection for the coupling hose "supply" is implemented; is the connection for the supply air [there automatic brake connection ( 20 )] depressurized, then the emergency brake piston [there ( 22 )] on its upper side depressurized and the voltage applied to its underside reservoir pressure pushes him up, so that first the exhaust valve [there ( 26 . 28 )] and in the further upward movement the inlet valve [there ( 26 . 27 )] is opened, so that the at the reservoir connection [there ( 33 )] pressure is also transmitted to the brake chamber and rests against the brake cylinder connections.

In the trailer brake valve is further the function of an advance of the transmitted to the brake cylinder Brake pressure opposite integrated with the pneumatic brake signal.

at the realization of a trailer brake valve according to the known document must be taken to ensure that the design-related Hysteresis of the relay valve enough becomes small in order to be able to tolerate her. For this, a certain Minimum size for the relay piston chosen become the influence of the friction forces, z. B. the friction force influence to reduce the piston seal. Since the size of such a valve the Costs, at least strongly determined, they can with this design principle not be reduced as much as you would like.

From the DE 30 31 105 A1 a load-dependent regulated two-line trailer brake system is known, which consists of an emergency brake valve constructed as a seat valve [there ( 3 )] and a load-dependent controlled brake force controller [there ( 5 )], wherein this is formed as a combination of a load-dependent acting control part with an air volume enhancing relay valve. The emergency brake valve corresponds in its operation of the tear function in a conventional trailer brake valve, so that the function of both valves can be understood as the function of a trailer brake valve with load-controlled braking force control mutatis mutandis. This is especially true, as well as a trailer brake valve z. B. after the former font by the combination of these valves can be replaced [in both cases, the brake cylinder are directly connected to the trailer brake valve or with the combination of two valves]. This document shows as well as the latter example typifies that together with trailer brake valves, other functions may be linked, as such, not the actual basic function of a trailer brake valve, namely substantially simplifies that of the anti-tore.

From the DE 32 07 793 C2 is known, in addition, in a 2-line wagon train brake system, a pressure sensor [there ( 18 )], which is connected via a branch 17 )] with the trailer brake line [there ( 15 )] for the trailer brake valve [there ( 10 )] connected is. Using the electrical pressure sensor signal, an electronic switching device [there ( 20 )] together with other sensor signals generates a control signal which is present in a pressure control valve [there ( 14 )] generates a brake pressure for the trailer brake cylinders. Due to the rapid switching of the electrical system, the brake pressure thus generated is leading the time in front of the front trailer brake valve pneumatically generated th brake pressure.

From DE-A1-198 18 982 a parking and maneuvering valve for trailer vehicles with spring-loaded parking brake is known, is initially omitted for cost reasons on a trailer brake valve and omitted by the waiver air quantity gain of the trailer brake valve optionally by an ABS relay valve [there ( 25 )] is realized. Unlike when using a combination of a trailer brake valve with a double release valve called combined release valve [the interaction is there in connection with 1 explained], in which a part of the combination release valve is provided for releasing the service brake braked in connection with the automatic braking of the trailer brake valve and the other part of the combination release valve serves to release the parking brake with parked trailer, are all release functions for the brakes of the trailer in this one parking and maneuvering valve. Namely, instead of operating two separate operating buttons for a combination release valve, the modes of parking and maneuvering valve are "parking", "driving" and "maneuvering" by only one control slide provided with an operation knob [there ( 7 )], which switches three to control the respective operating mode can take positions. Another difference of the parking and maneuvering valve to the combination trailer brake valve / combination release valve is that when parking as well as while driving in a supply line demolition [or dissolved supply clutch] not the service brake but the parking brake is effective. In particular, in the Vorratsleitungs demolition this is disadvantageous because of the absence of a service brake pressure no conventional ABS braking can use more and the trailer can be easily unstable by a full braking without ABS. In the parking and maneuvering valve, the changeover valve acting as overload protection [prevention of brake force addition from spring accumulator and service brake] is not present as a separate component as in the combination trailer brake valve / combination release valve [there 1 , (C)], but itself integrated into the parking and maneuvering valve [there ( 37 )]. This installation location of the overload shuttle valve does not allow the use of the parking and maneuvering valve in trailers with electronic brake pressure control; in such a trailer, the electric EBS-CAN bus signal is used in EHS operation for braking, which is still strongly influenced by the brake pressure modulator, so that the brake pressure modulator controlled by the brake pressure sometimes deviates greatly from the pneumatic brake pressure, which on the Brake line is connected to the parking and maneuvering valve. Finally, the valve actuation by means of a spool valve contradicts the current state of standardization considerations for double release valves, whose operation and functions will in future be governed by a DIN standard.

From the WABCO data sheet "Wabcodruck 820 001 051 3 / 05.95" a double release valve 963 001 051 0 is known. Since a double release valve according to this principle also in 1 is shown with its details, in the following explanations next to reference numerals in the local data sheet and corresponding reference numerals in 1 specified.

The double release valve [there ( 1 ) under "Scheme with ALB trailer brake valve"] consists of a service brake release valve [in 1 ( 33 )], a parking valve [in 1 ( 20 )] and a check valve associated with the parking valve.

The service brake release valve is pneumatic on the input side [there ( 1-1 )] with the supply coupling head [in 1 ( 48 )]. connected and on the output side pneumatically at the supply pressure connection [there ( 1 ) of the local ALB trailer brake valve ( 2 ), in 1 ( 1 ) of the trailer brake valve ( 8th )].

In his driving position [pulled position of the local black actuating button] has the service brake release valve no influence on the pressure in the service brake chambers of the spring brake cylinder; in its release position [not pulled position of the black operating knob] causes the Service brake release valve the release of the Service brakes.

The service brake release valve is used to move a decoupled trailer by overriding the automatic brake [triggered by the supply line breakaway in the trailer brake valve]; This happens because in the release position tank pressure is deflected and fed to the supply connection in the trailer brake valve [in 1 from the release connection ( 5 ) via the pressure channel ( 24 ) to the supply connection ( 1 )]; By this pressure deflection is simulated in the trailer brake valve that is applied to the coupling head for the supply pressure hose pressure.

The parking valve is pneumatic on the input side [there ( 1-2 )] connected to the reservoir, wherein the connection via a check valve [in 1 ( 19 )], and on the output side [there ( 22 )] the parking valve is pneumatically actuated via the brake overload shuttle valve [there ( 3 ), in 1 ( 52 )] to the dissolution chambers [there ( 12 )] of the spring brake cylinder [in 1 ( 38 . 39 . 40 . 41 )].

The Parking valve vented in its parking position [pulled position of the local red actuating button] the dissolving chambers the spring brake cylinder, so that the parking brakes are effective; in its driving position [not pulled position of the red actuating button] solve that Park valve the parking brakes by ventilating the spring-loaded release chambers.

The mentioned above, in the direction of the dissolving chambers the spring brake cylinder opening check valve Hold the high original Reservoir pressure in the dissolving chambers the spring brake cylinder, even if the tank pressure breaks down for a short time. Such burglaries can be due to leakage or intense ABS braking occurs.

These known legally required function of the check valve Also works for a parked trailer, by uncoupling in the automatic cal brake function and in which the parking valve remains in the driving position.

If such a parked trailer vehicle then loses container pressure and the spring-loaded release chambers secured by the non-return valve still remain pressurized, the service brakes begin to release and the trailer can start to move when the parking brakes are released z. B. is parked at a location with a slightly inclined roadway.

at only slight road gradient, it may happen that the operator it overlooks the parking valve by pulling the red control knob in the parking position to which the followers on the automatic braking first slowed down. Forgetting, when parked trailer vehicle to operate the parking valve, So in the operation of known trailer brake valves with a Double release valve a security hole represents.

at a trailer with electronic brake control is the regulation of the brake pressure in the brake cylinders of a vehicle axle of the designated Brake control electronics made, which also z. B. in the case of an ABS control intervention with different friction conditions on both sides of the vehicle on the brake pressure in the brake cylinders the left side of the vehicle different from the brake pressure in the brake cylinders on the right side of the vehicle. Likewise, the brake pressure from the Bremsregelelek electronics z. B. varies depending on the load. For one such load-dependent Braking, the loading z. B. via a pressure measurement in an air bag determined and communicated to the brake control electronics, which then the Brake pressure in the brake cylinders of the trailer modified accordingly. For the Generation of the brake pressure is provided a brake pressure modulator, which consists of electrically controllable valves, usually driven in clocking mode of operation of the brake control electronics be used as pilot valves to generate a control pressure in serve the control chamber of a relay valve, which is the control pressure air volume amplified as brake pressure over its output to one or more brake cylinders; in this connection can be implemented one or more such constructed brake control channels.

One Trailer brake valve for the Use in a trailer with electronic brake control therefore needs neither over the Function of the air quantity boost still over Special functions such. B. the mentioned function of a lead or that of a load-dependent Modification of the brake pressure to dispose. For such a trailer brake valve it is completely sufficient if the basic functions, namely the provision of the transmitted from the towing vehicle Brake specification pressure, the breakaway safety as well as the possibility the connection of a double-release valve explained above are realized.

Of the The invention is therefore based on the object for a trailer brake valve after the former Well th font to specify a valve construction, the corresponding the reduced requirements of the use of the trailer brake valve in a trailer with electronic brake control to reduce manufacturing costs is simplified, and in the case of parked trailer increased safety is given against unintentional rolling on.

These The object is achieved by the invention specified in claim 1 solved. Further developments and advantageous embodiments of the invention are in the subclaims specified.

The Invention has the advantage that for increased security against unintentional rolling on the part of the trailer no additional components or piping is required.

Additionally has the invention has the advantage that the error rate by significantly simplified compared to the prior art Structure is considerably reduced.

relay valves are through the vent the relay valve pressure chamber is not free of air consumption. With the Elimination of an air-boosting according to the relay valve principle working valve device after The invention provides the advantage that no more air consumption and the noise associated with air consumption also not takes place.

By the elimination of a relay valve eliminates the relay piston hysteresis, Firstly, to the advantage of improved accuracy and secondly to leads to the advantage that no delayed Response of the controlled pressure against the applied pressure more is available. The set pressure had therefore at St. d. T. first of the pneumatic brake signal exceeded so that the pneumatic brake signal is controlled by air flow can be.

With Eliminating an overfeed is the benefit of improved accuracy connected; Furthermore deleted by eliminating the override function the error-prone and possibly even abusive Setting the lead.

A Development of the invention has the advantage that by eliminating the relay valve with its time delay "output input" from i. Gen. more than 30 ms a time advantage for the electrical signal of the pressure sensor is connected, because this pressure sensor from the trailer brake valve measured brake pressure measures.

Strongly generalized is optimized in the invention, the pneumatic path, because this Ge gensatz is provided for the normally effective electrical brake signal transmission only for emergency braking, in which can be dispensed with a load-dependent brake pressure influencing. With the optimized pneumatic path has the advantage that on the one hand air consuming facilities eliminated and on the other time delays caused by such facilities no longer occur.

A Another embodiment of the invention has the advantage that the switching the trailer brake valve in the demolition position only from the supply connection of the Valve [this is pneumatically connected to the red coupling head] applied pressure depends. The transition from one to the other switching position is also abrupt, so that Switch also friction-independent done and creeping transitions avoided become. Thus, in the supply line demolition, the emergency brake "immediately", and it must be compared to conventional solutions first no characteristic curve will be traversed. The valve is designed as a pressure balanced Positive overlap valve performed; compared to conventional solutions This training also has the advantage that breathing spaces and the associated Risk of icing can be avoided.

From The latter development, there are various embodiments, the according to the respective preferred approach certain advantages Offer.

The Invention will be described below with reference to an embodiment, which in the Drawings is shown, closer explained.

It shows:

1 The trailer brake valve in the block diagram of a trailer EBS brake system;

2 the trailer brake valve designed as a slide valve with coupled supply-pressure hose;

3 the trailer brake valve designed as a slide valve with decoupled supply pressure hose.

4 a trailer brake valve designed as a slide valve with an integrated pilot valve, in which the valve actuation takes place independently of the container pressure, in the basic position;

5 the trailer brake valve 4 in the demolition position;

6 a detail of the pilot valve in the basic ( 6a ) and demolition position ( 6b );

7 a trailer brake valve according to the principle of 4 in which the pilot valve is designed as a separate 3/2-way valve, in the basic position;

8th the trailer brake valve 7 in the demolition position;

9 a trailer brake valve according to the principle of 6 in which the pilot valve is designed as a combination of two 2/2-way valves, in the basic position;

10 the trailer brake valve 9 in the demolition position.

Based on 1 the functional scope of the trailer brake valve for a trailer EBS brake system will be explained; In this case, it will be explained on the basis of the realization, in which way already mentioned functions that can be omitted, are taken over by the trailer EBS brake pressure control.

The block diagram after 1 is based on the configuration of a base variant for trailer EBS systems, which consists of a semi-trailer ( 34 ) with two axles, this is a 2S / 2M system [two ABS sensors for two wheels and two modulator channels for the left and right wheel brakes]; the ABS brake pressure control is thus carried out page by page.

The trailer with the trailer brake valve according to the invention is pneumatically with the towing vehicle via two pressure hoses, via firstly a supply pressure hose ( 30 ) for the transmission of the supply pressure [on the towing vehicle mounted red pressure hose, which via the "red coupling head" ( 48 ) of the trailer] and secondly a brake pressure hose ( 31 ) for transmitting the brake pressure [yellow cable attached to the towing vehicle, which is connected via the "yellow coupling head" ( 49 ) of the trailer is coupled]. On the side of the towing vehicle, both the red pressure hose and the yellow pressure hose are pneumatically connected to a trailer control valve [AST valve].

On the trailer side, the supply pressure hose ( 30 ) pneumatically via the above-described service brake release valve ( 33 ) with the supply connection ( 1 ), and the brake pressure hose ( 31 ) via a pneumatic line to the brake specification port ( 4 ) of trailer braking tiles ( 8th ) connected. The trailer brake valve ( 8th ) further has a container connection ( 3 ), at which the supply pressure vessel ( 9 ) is connected to the trailer, and via a brake pressure connection ( 2 ), at which the pneumatic brake pressure to the pneumatic input ( 28 ) of the pneumatic brake pressure modulator ( 29 ) is output; This brake pressure represents the redundant pressure for the trailer with its electronic brake pressure control.

In the trailer with the electronic brake pressure control is in all conceivable cases in which a braking to take place at the brake pressure port ( 2 ) a corresponding redundancy pressure controlled. In normal braking operations this is because the trailer must of course be coupled with any type of suitably approved towing vehicles, both in the event that the towing vehicle has electronic brake control, and in the event that the towing vehicle is equipped with a conventional pneumatic braking system equipped. In a towing vehicle with electronic brake control a braking operation is initiated by actuation of the control system belonging to Bremswertge bers, while this is done in a conventional towing vehicle by pressing the corresponding motor vehicle brake valve.

In the case of the towing vehicle [this is the towing vehicle] with electronic brake control, in which, of course, the brake pressure set by the electronic trailer brake control by the motor vehicle via the electrical interface ( 32 ) [ISO 7638 / CAN] to the trailer transmitted electrical brake request signal is determined, the redundancy pressure in the trailer in case of failure is used for braking, namely, when the motor vehicle electronics has failed. When using a conventionally braked motor car, the "redundancy pressure" in the trailer is used to brake the trailer at all, since such a motor vehicle, the electronic brake pressure control in the trailer can not respond. The conversion of the pneumatic braking signal into an electronic signal is carried out by the pressure sensor ( 47 ) in the trailer.

In addition to these normal braking operations, the trailer brake valve ( 8th ) a full brake pressure to the modulator ( 29 ), which allows a purely pneumatic braking without the intervention of the electronics. In demolition of one of the two pneumatic lines between towing vehicle and trailer or uncoupled red coupling head emergency braking by means of the tank pressure is triggered in a known manner by the interaction between the trailer control valve in the towing vehicle and trailer brake valve by, as explained below, in this case in the trailer brake valve ( 8th ) the Behälteran circuit ( 3 ) pneumatically with the brake pressure connection ( 2 ) is connected.

In summary, it can be said that in all cases in which trailer braking is required, be it normal braking or emergency braking, the trailer brake valve ( 8th ) at the brake pressure connection ( 2 ) a pressure, either the redundant pressure or the tank pressure, is output which corresponds to the pneumatic brake pressure modulator ( 29 ) is supplied.

The brake pressure modulator ( 29 ) further has a pressure supply connection ( 35 ), which by a pneumatic line with the reservoir pressure vessel ( 9 ) connected is. The brake pressure modulator ( 29 ) is connected via electrical connections through the electronics unit ( 42 ) controlled.

The pneumatic brake pressure modulator ( 29 ) is z. B. as a two-channel pressure control module after the DE 42 27 084 A1 [there 2 ] built up; this font will be referred to as S1 below.

In a realization according to S1, a common 3/2 solenoid valve [there (for both channels 12 )] as a changeover valve for further duct-specific ventilation and venting solenoid valves [there ( 9 ' ) and ( 7 ) respectively. ( 9 ) and ( 8th )], which in the case of EBS brake pressure control with a clocking operating mode control pilot brake pressures per channel, which in turn are fed to control inputs [there ( 5 ) respectively. ( 6 )] of per channel relay valves [there ( 3 ) respectively. ( 4 )] are placed. The relay valve working ports [there ( 20 ) and ( 22 ) respectively. ( 21 ) and ( 23 )] are, as in 1 shown with the cylinder service brake lines ( 36 ) arranged in the direction of travel on the left side of the vehicle spring brake cylinder ( 38 ) and ( 39 ), or with the cylinder service brake lines ( 37 ) arranged in the direction of travel on the right side of the vehicle spring brake cylinder ( 40 ) and ( 41 ) connected.

The pneumatic input ( 28 ) is connected to the control pressure port [there ( 13 )] and the pressure supply connection ( 35 ) is connected to the reservoir pressure port [there ( 17 )] of the pressure control module connected to the S1. In its spring-actuated basic position, ie in its de-energized state, of the 3/2-solenoid valve [there ( 12 )] of the S1 at the pneumatic input ( 28 ) to 1 incoming pressure to the control inputs of the relay valves (there ( 3 ) 4 )] the S1 and controlled by air volume at the said relay valve working ports issued. This mode of operation corresponds to the case of redundancy, in which a pneumatic redundant pressure is fed in an air-volume-enhanced manner to the brake cylinder, without the electronics unit ( 42 ) involved in any way.

In the current-charged state, ie controlled by the electronic unit ( 42 ) to 1 , is supplied by the 3/2 solenoid valve [there ( 12 )] of the S1 at the pressure supply connection ( 35 ) to 1 applied supply pressure to the above-mentioned channel-specific ventilation and vent solenoid valves of S1, which represents the illustrated case of electronic EBS brake pressure control. As part of the EBS brake pressure control also pressure control functions are performed, which in conventional brake systems z. T. executed as a function of a trailer brake valve.

In this way, as part of the EBS brake pressure control, a charge-dependent brake force distribution between the vehicle axles is made. For this purpose - it is assumed that an air-suspended semi-trailer with bellows on the left and right side of the vehicle - the bellows on the right side usually provided with a pressure sensor whose Druckmeßwert the electronic unit ( 42 ) is available. The electronics unit ( 42 ) modifies the controlled brake pressures as a function of the load using this pressure measurement representing the load of the vehicle.

The electronics unit ( 42 ) also uses the pressure measurement value of the pressure sensor for the EBS brake pressure control ( 47 ), which at the brake pressure connection ( 2 ) output brake pressure of the trailer brake valve ( 8th ). This pressure reading is provided for the case of a conventional towing vehicle in which the electronics unit ( 42 ) uses the electrical pressure reading as the electrical braking request signal for the EBS brake pressure control.

For completeness, it should be added that the ABS brake control is also performed by the EBS brake pressure control devices; For this purpose, on the left and right wheels, which are controlled by the spring brake cylinders [( 38 ) and ( 39 ) respectively. ( 40 ) and ( 41 )] are braked, appropriate ABS sensors for detecting the respective wheel speeds provided.

If all the functions of the EBS brake pressure control are summarized, then for the trailer brake valve ( 8th ) only pneumatic functions are to be realized, which are defined by two switching states: First, this is the valve home position, which is present when the supply port is pressurized, and on the other hand, this is the valve-breakaway position, which at unpressurized supply port ( 1 ) given is.

• G1) – Der Versorgungsanschluß (1) ist pneumatisch über das zweite Rückschlagventil (6) mit dem Behälteranschluß (3) verbunden;
• G2) – der Bremsdruckanschluß (2) ist pneumatisch mit dem Bremsvorgabeanschluß (4) verbunden.

In the valve basic position, the trailer control valve ( 8th ) produced the following compounds:

• G1) - The supply connection ( 1 ) is pneumatically via the second check valve ( 6 ) with the container connection ( 3 ) connected;
• G2) - the brake pressure connection ( 2 ) is pneumatic with the brake specification port ( 4 ) connected.

• A1) – Der Versorgungsanschluß (1) ist durch das zweite Rückschlagventil (6) pneumatisch abgeschlosssen;
• A2) – der Bremsdruckanschluß (2) ist pneumatisch mit dem Behälteranschluß (3) verbunden.

In its valve breakaway position, the trailer brake valve ( 8th ) produced the following compounds:

• A1) - The supply connection ( 1 ) is through the second check valve ( 6 ) pneumatically completed;
• A2) - the brake pressure connection ( 2 ) is pneumatically connected to the container connection ( 3 ) connected.

In addition to these functions for the EBS brake pressure control, the trailer brake valve contains connection options for the function modules of the double release valve, ie the connection of the service brake release valve ( 33 ) and the parking valve ( 20 ).

In 1 is the trailer brake valve ( 8th ) in its valve basic position, which is evident from the fact that the red coupling head ( 48 ) is drawn in the coupled state.

For connecting the service brake release valve ( 33 ) is the above-mentioned release connection ( 5 ) provided by a in the trailer control valve ( 8th ) existing direct pneumatic connection with the container connection ( 3 ) connected is.

If now that in 1 in its drive position [operating knob "pulled"] drawn service brake release valve is set in its release position, so to solve the service brakes, as already explained above, the container pressure on the pressure channel ( 24 ) into the supply connection ( 1 ) fed.

The connection of the parking valve ( 20 ) to the trailer brake valve ( 8th ) does not take place as in the St. d. T. on the reservoir, but via a separate parking terminal ( 21 ); inside the trailer brake valve ( 8th ) is the park connection ( 21 ) via the already mentioned above, in the direction of the park connection ( 21 ) opening, first check valve ( 19 ) with the container connection ( 3 ) [this check valve is, as explained above, housed in the St.dT parking valve of the double release valve]].

At the in 1 in its driving position [actuating button "not pulled"] shown parking valve ( 20 ) at the park exit ( 21 ) adjacent Be container pressure over the pressure channel ( 23 ) through the parking valve connection ( 51 ) into the dissolution line ( 53 ) and from there via the brake overload shuttle valve ( 52 ) and the spring-loaded release lines ( 50 ) in the release chambers for the spring brake cylinder ( 38 . 39 . 40 . 41 ) fed; thus the parking brakes of this spring brake cylinder are released.

In the parking position of the parking valve ( 20 ) [Actuating button "pulled"], the release chambers of the spring brake cylinder over the effective in this valve position pressure channel ( 22 ) vented, which causes the parking brakes of the spring brake cylinders are effective again.

According to the invention in the trailer brake valve ( 8th ) at the park connection ( 21 ) parallel to the first check valve ( 19 ) a bypass channel ( 46 ), which in the valve basic position of the trailer brake valve ( 8th ) is irrelevant, because it is effective over the paths that are active in this switching state ( 54 ) is completed.

In the valve breakaway position, however, the paths of the valve breakaway position ( 55 ) and in this Stel development of the container pressure is on the bypass channel ( 46 ) directly at the park connection ( 21 ) at; In this valve position, the container pressure is also at the brake pressure port ( 2 ) at.

In the valve breakaway position - the parking valve ( 20 ) is in his in 1 shown driving position - so both the service brake chambers and the release chambers of the spring brake cylinder ( 38 . 39 . 40 . 41 ) is subjected to the tank pressure; the parking brakes are released and the service brakes are effective.

In the context of a leakage-related pressure reduction in the reservoir ( 9 ) decreases the effect of service brakes; but at the same time also decreases the release of the parking brake, so that the effect of the parking brake increases. Depending on the design, the effect of the operating or the effect of the parking brakes prevails at a given by the device design [spring force / pressure surface] pressure level: Thus, at any pressure level a residual braking effect for the trailer is present, either from the operating or comes from the parking brakes.

Under Use of the device according to the invention becomes a trailer, the on a roadway with only moderate road gradient is set up, not independently roll in; the security against one automatic rolling away of the trailer is thus significantly improved.

at a parked trailer is a safe state achieved when the parking valve by pulling of the actuating button has been placed in the parking position and thus the parking brakes permanently are effective. Unfortunately, sometimes the button is forgotten to pull, since the parked vehicle by the automatic emergency braking yes first when slowed down seems safe. The invention increases safety especially by the fact that as well in case of incorrect operation, the parking valve is not in park state put, the trailer always sufficiently slowed down and thus practically do not roll away can.

For reduced requirements or other types of equipment [eg. B. without spring brake cylinder] may optionally be dispensed with the use of the illustrated release or parking valve function. In such an embodiment, the red coupling head ( 48 ) directly to the supply connection ( 1 ) and the dissolution line ( 53 ) directly to the park connection ( 21 ) connected. Due to the absence of the parking valve the parked vehicle can then no longer be secured by the parking brakes, and the release of the automatic emergency braking takes place with the reconnection of the supply line pressure hose to the towing vehicle. However, it is important that even in such a simplified system the described measures against automatic rolling away are effective. It should be added that it is of course also possible to use a service brake release valve or a parking valve as a single valve.

It there is also the possibility the trailer brake valve according to the invention with a service brake release valve and / or to combine a parking valve in a housing structurally.

It should be added that the brake overload shuttle valve ( 52 ) serves to protect the brakes from acting on them too much clamping force, when the parking brake and the service brake are effective at the same time.

If the parking brake should be effective, in the release line ( 53 ) Pressure, and at the same time on the cylinder service brake lines ( 37 ) apply a service brake pressure, so reduces this service brake pressure on the overload shuttle valve ( 52 ) the release pressure in the spring-loaded release lines ( 50 ) such that the braking force exerted by the parking brakes is reduced by the force of the service brakes.

In 2 and 3 are the service brake release valve ( 33 ) and the parking valve ( 20 ) shown only schematically in their respective driving position, the pneumatic feeders "input / output" are each drawn as dashed lines.

In the lower part of the representations of 2 and 3 the switching states of the valve are shown as pneumatic diagrams of a piston-operated 3/2-way valve; the upper area shows these switching states in the realization of the trailer brake valve ( 8th ) as a slide valve.

The trailer brake valve ( 8th ) is in 2 in the valve home position and in 3 shown in the valve breakaway position.

at 2 is to mark the valve home position the red coupling head ( 48 ) drawn in coupled state. In the pneumatic diagram is located according to the valve home position of the piston ( 7 ), which is designed as an actuating piston for the valve, in its unactuated state and it is the valid for this state paths ( 54 ), so that in the trailer brake valve ( 8th ) the above-described compounds G2) and G1) [in the case that at the terminal ( 1 ) the supply pressure is applied, the below-explained second check valve ( 6 ) operated in the forward direction] are produced.

at 3 is to clarify the state of "demolition" of the red coupling head ( 48 ) drawn in uncoupled state [the yellow coupling head ( 49 ) is both in 2 as well as in 3 drawn in a coupled state]. In the pneumatic diagram is the actuating piston ( 7 ) in its actuated state and it is the valid paths for this state ( 55 ), so that in the trailer brake valve ( 8th ) the above-described compounds (A1) [the second check valve ( 6 ) is located at open supply connection ( 1 ) in the blocking state] and (A2) are produced.

In the structural design of the trailer brake valve ( 8th ) as a slide valve corresponding to the respective upper areas of 2 respectively. 3 is the one with an O-ring seal ( 16 ) provided actuating piston ( 7 ) with the valve slide ( 10 ) firmly and pressure-tight connected.

In the middle of the actuating piston valve slide assembly ( 7 . 10 ) there is a pressure channel ( 12 ) in the form of a blind hole.

The actuating piston ( 7 ) has a first ( 17 ) and a second ( 18 ) Effective area. The first effective area ( 17 ) is due to the cross-sectional area of the actuating piston ( 7 ) and the second effective area ( 18 ) is due to the structural union of actuating piston ( 7 ) and valve slide ( 10 ) designed as an annular surface, wherein the inner ring diameter by the outer diameter of the valve gate seal ( 14 ).

The first effective area ( 17 ) is formed larger than the second ring-active surface ( 18 ).

The second check valve ( 6 ) is in the direction of action shown in the actuating piston ( 7 ), whereby both active surfaces ( 18 ) and ( 17 ) are interconnected by this check valve such that the passage direction of the check valve ( 6 ) from the second ( 18 ) to the first ( 17 ) Effective surface runs. Since the second effective area ( 18 ) from the supply connection ( 1 ) applied pressure and the first effective area ( 17 ) from that at the container connection ( 3 ) is applied, the second check valve is ( 6 ) is always switched in the forward direction, when the at the supply terminal ( 1 ) applied pressure is greater than that at the container connection ( 3 ) applied pressure.

In the basic position 2 is the actuating piston valve slide assembly ( 7 . 10 ) by the action of the return spring ( 11 ) at the first stop ( 26 ) of the valve housing. In this switching position, the above-described compounds G1) and G2) are made. Here, G2 represents a direct connection, ie in the pneumatic path no mechanical intermediate links are inserted [the connection G2 corresponds to the DE 28 10 850 A1 in that the at the local control terminal ( 7 ) applied pressure first on the local relay piston ( 6 ) acts as a mechanical intermediate].

The above-described bypass channel ( 46 ) is realized as a pressure channel within the valve housing and is in the valve home position without effect, since the park connection ( 21 ) via both the direct channel ( 56 ) as well as via the bypass channel ( 46 ) is connected to the same pressure chamber, which via the in the direction of the park connection ( 21 ), in the end wall of the valve slide ( 10 ), first check valve ( 19 ) and the blind hole pressure channel ( 12 ) with the container connection ( 3 ) connected is.

In the demolition position after 3 acts on the container connection ( 3 ) applied pressure over the first effective area ( 17 ) on the actuating piston ( 7 ), whereby the valve piston valve slide assembly ( 7 . 10 ) to the second stop ( 27 ) is pushed.

The second check valve ( 6 ) is in the reverse direction, which causes the above-mentioned compound A1). In the valve slide ( 10 ) is a pressure channel ( 13 ) provided in the form of a bore. The above-described compound A2) is due to the direct pneumatic connection from the container port ( 3 ) via the blind hole pressure channel ( 12 ) and the pressure channel ( 13 ) to the brake pressure connection ( 2 ) produced.

In the valve breakaway position the park connection ( 21 ) via two parallel pneumatic connections with the container connection ( 3 ): The first connection is via the direct channel ( 56 ), the second check valve ( 19 ) and the blind hole pressure channel ( 12 ) to the container connection ( 3 ) and the second pneumatic path leads directly bypassing the check valve via the bypass channel ( 46 ), designed as a bore pressure channel ( 45 ) and the blind hole pressure channel ( 12 ) to the container connection ( 3 ); with unpressurized supply connection ( 1 ), the effect of the first check valve ( 19 ) canceled.

In addition to its arrangement within the actuating piston ( 7 ), the second check valve ( 6 ) are also executed by the as O-ring ( 16 ) seal is formed as a grooved ring in a suitable installation direction or by a check valve is provided at another location, which connects the two pressure chambers, which has a force on the active surfaces ( 17 ) and ( 18 ) exercise.

The same applies mutatis mutandis to the first check valve ( 19 ) and the O-ring ( 44 ).

For sealing the valve slide with respect to the supply connection ( 1 ) is on the valve spool ( 10 ) a suitable slide valve seal ( 14 ) as the first slide seal and for sealing against the brake pressure connection ( 2 ) [This seal is important in the case of valve home position] is on the valve spool ( 10 ) a slide valve seal ( 15 ) provided as a second slide seal. For sealing the bore pressure channel ( 45 ), both with respect to the pressure chamber for the direct connection ( 56 ) as well as with respect to the brake pressure connection ( 4 ), are a third ( 43 ) and fourth ( 44 ) Gate valve seal provided. Generalized, these slide seals serve to seal the effective in the various valve switching positions pneumatic pressure chambers for the pneumatic paths in the valve.

To simplify manufacturing, the actuating piston ( 7 ) also in one piece with the valve slide ( 10 ), so that the actuating piston valve spool unit ( 7 . 10 ) z. B. completely as a turned part or as a plastic injection molded part can be produced.

Alternatively to the embodiment shown, in which the slide valve seals ( 14 . 15 . 43 . 44 ) in the valve slide ( 10 ) and the sealing surfaces are arranged on the inner wall of the valve housing, it is also possible, as is known from the valve technology, the slide valve seals ( 14 . 15 . 43 . 44 ) in the valve housing, above and below the bore for the brake pressure connection ( 2 ) or the inlet opening for the bypass channel ( 46 ), and the sealing surfaces on the valve spool ( 10 ) train.

As explained above, in the breakaway position of the trailer brake valve ( 8th ) to 3 the automatic emergency braking is effective and the trailer can not be moved as long as in the reservoir tank ( 9 ) is still a sufficient pressure exists; to release the emergency brake, as explained, the service brake release valve ( 33 ) to 1 in its release position [operation button "not pulled"].

In this release, the pressure prevailing in the reservoir pressure pressure now acts on both active surfaces ( 17 ) and ( 18 ) to 3 one. The return spring ( 11 ) is dimensioned such that it determines the force by the area fraction around which the second active surface ( 18 ) with respect to the first effective area ( 17 ) is canceled, and overcompensated so that the actuating piston valve slide assembly ( 7 . 10 ) from the return spring ( 11 ) to the first stop ( 26 ) is pushed. This is the in 2 shown valve position and the brake pressure connection ( 2 ) is connected to the brake specification port ( 4 ) connected. However, since the yellow coupling head ( 49 ) is not connected, the at the brake pressure connection ( 2 ) connected pressure chambers, ie the service brake chambers of the spring brake cylinder, vented, so that the brake is released.

It should be noted that it is possible, using the valve characteristics set forth herein, to design the spool valve valve-trained valve areas [( 2 ) 10 ) 13 ) 14 ) 15 ); respectively. ( 21 ) 10 ) 45 ) 43 ) 44 )] of the trailer brake valve ( 8th ) also in seat valve design.

Even though the trailer brake valve according to the invention primarily for trailer braking systems designed with electronic braking force control, can be, provided that there the legal requirements regarding the braking time behavior is met are, the device in unchanged form also used in conventional systems. The explained security against an automatic Rolling is then also effective in these systems. Next are the reduced manufacturing and installation costs also advantageous.

In the illustrations after 4 and 5 the trailer brake valve according to the invention is shown in one embodiment as a slide valve, in which the slide operation exclusively from the at the supply terminal ( 1 ) depending pressure, ie at which the container connection ( 3 ) applied pressure no force on the valve spool ( 10 ) exercises. For this the trailer brake valve ( 8th ) constructed as a pressure-relieved valve, wherein the valve spool ( 10 ) from any other connection except the supply connection ( 1 ), which acts on this force-generating effect on a below-explained effective area, a compressive force is generated.

Since the in 2 and 3 connected to the connections of the trailer brake valve, in 1 detailed and in 2 . 3 shown in simplified form, components are explained in detail above, the presentation is limited to 4 and 5 on the explanation of the valve operation with reference to the valve connections. For the sake of clarity, it should be added that the trailer brake valve ( 8th ) to 4 and 5 in the same way as the trailer brake valve 2 and 3 in a trailer EBS brake system 1 operate.

For the sake of clarity, in 4 and 5 Pneumatic diagrams, as in the lower parts of 2 and 3 are shown omitted since the too 4 and 5 belonging pneumatic diagrams are basically similar to this; there is only the difference that, as explained, the valve spool ( 10 ) to 4 and 5 not from the pressure difference between the supply connection ( 1 ) and the container connection ( 3 ), but only by the pressure at the supply terminal ( 1 ) is switched.

In 4 and 5 So are the supply connection ( 1 ), the brake specification port ( 4 ), the container connection ( 3 ) and the brake pressure connection ( 2 ), wherein the release connection ( 5 ) pneumatically with the container connection ( 3 ) connected is. In addition, a vent ( 57 ) to the atmosphere. The valve spool ( 10 ) is formed as mentioned as a valve spool piston, ie it combines the functions of the above-described valve spool ( 10 ) and the actuating piston ( 7 ).

The valve spool ( 10 ) is connected to the return spring ( 11 ) and has two positions; one in 4 illustrated basic position, in which the valve slide ( 10 ) at the first stop ( 26 ), and an in

5 shown tear-off, in which the valve slide ( 10 ) at the second stop ( 27 ) comes to the plant.

By one on the valve slide ( 10 ) acting on the mentioned active surface pressure force is at pressurized supply connection [ 4 ] taken the basic position while the breakaway [ 5 ] by the action of the return spring ( 11 ) is taken when the supply connection ( 1 ) is depressurized.

The above-described second check valve ( 6 ) is in 4 . 5 realized as a grooved ring. By this check function and in the valve home position to 4 drawn position of the valve spool ( 10 ) are the above-described compounds (G1) [pneumatic connection supply terminal ( 1 ) with container connection ( 3 )] and (G2) [pneumatic connection brake pressure connection ( 2 ) with brake specification connection ( 4 )] realized. In the valve breakaway position to 5 are at the position shown the valve spool ( 10 ) the above-described compounds (A1) [pneumatic termination supply connection ( 1 )] and (A2) [pneumatic connection Bremsdruckan circuit ( 2 ) with container connection ( 3 )] realized.

In the basic position ( 4 ] the separately formed park connection ( 21 ) from the reservoir pressure vessel ( 9 ) at the container connection ( 3 ) via the first check valve ( 19 ), which is also designed as a grooved ring, ventilated. By contrast, by the concave housing constriction at the parking terminal ( 21 ), which in the demolition position [ 5 ] is effective, in this position, a direct pneumatic connection between the container port ( 3 ) and the park connection ( 21 ) produced.

In the valve slide ( 10 ) is a pilot valve ( 60 ), which consists of a valve switching element ( 62 ), one on the valve switching element ( 62 ) acting spring ( 61 ), a first valve seat ( 63 ) and a second valve seat ( 64 ) consists.

According to its two valve seats, the pilot valve ( 60 ) two positions, a starting position and a switching position on. The initial position of the pilot valve ( 60 ) is in 5 shown: In the tear-off position there is no pressure at the supply connection ( 1 ), and by the action of the spring ( 61 ) the valve switching element ( 62 ) at the first valve seat ( 63 ), whereby the on the valve spool ( 10 ) acting pressure chamber opposite the supply terminal ( 1 ) is sealed. Is displayed on a parked trailer [demolition position 5 ] the supply pressure hose ( 30 ), the pressure at the supply connection ( 1 ), and according to the applied pressure and the effective diameter ( 65 ) at the first valve seat ( 63 ) is a pressure force on the valve switching element ( 62 ) exercised. This effective diameter ( 65 ) determined by the properties of the spring ( 61 ) [Spring length and spring constant] a pressure threshold above which the valve switching element ( 62 ) from the first valve seat ( 63 ) takes off.

The valve switching element ( 62 ) is in his cone form such that after lifting from the first valve seat ( 63 ) the pressure at the supply connection ( 1 ) acts now on a larger area, whereby the pilot valve ( 60 ) by the pressing force the force of the spring ( 61 ) overcomes, and according to the in 4 shown switching position of the pilot valve ( 60 ) the valve switching element ( 62 ) against the second valve seat ( 64 ) and close it.

With the transition to the switching position of the pilot valve ( 60 ) is the on the valve spool ( 10 ) abruptly increased pressure, and the valve spool, starting from its position in 5 when he hits the second stop ( 27 ) is applied, against the force of the return spring ( 11 ), to the first stop ( 26 ) pushed; This has the trailer brake valve ( 8th ) taken his basic position.

Compared to the effective diameter ( 65 ) in the initial position of the pilot valve ( 60 ) to 6b is in the switching position of the pilot valve ( 60 ) to 6a the effective diameter ( 66 ) elevated; This introduces a switching hysteresis.

Due to the switching hysteresis causes the trailer brake valve not at z. B. a brief drop below the pressure threshold explained again in the tear position 5 passes. To switch from the switch position [ 4 ] to the demolition [ 5 ], the pressure at the supply connection ( 1 ) have fallen such that the valve switching member ( 62 ) by the force of the spring ( 61 ) back to the first valve seat ( 63 ) is pressed. Only then will the valve slide ( 10 ) by the force of the return spring ( 11 ) again at the second stop corresponding to the breakaway position ( 27 ) pushed back.

going one from a usual one Target pressure in the supply pressure hose of 8 bar, then the pressure threshold z. B. expediently set to 3.5 bar. The explained Switching hysteresis can z. B. be designed so that the tear-off position the trailer brake valve recaptured when falling below a pressure of 2.5 bar becomes.

The first valve seat ( 63 ) acts as a ventilation seat and the second valve seat ( 64 ) as a vent seat; when bleeding the trailer brake valve ( 8th ), ie at the transition of the valve spool ( 10 ) with the second valve seat open ( 64 ) [ 5 ] from the first stop ( 26 ) to the second stop ( 27 ), there is the advantage that the venting takes place directly to the atmosphere and there are no breathing spaces, as is the case with conventional trailer brake valves. Breathing rooms have the disadvantage that moisture can penetrate into the device, which may lead to icing. Compared to conventional trailer brake valves there is also the advantage that the valve switching is effective immediately and not a characteristic curve must first be passed.

In the embodiments according to 7 and 8th [the check valves ( 6 ' ) and ( 19 ' ) are not implemented at first] is the pilot valve ( 60 ) no longer in the valve spool ( 10 ), but as a separate 3/2-way valve ( 70 ). The valve switching element ( 62 ) is designed as a conventional seat valve switching element, which in the tear-off position [ 8th ] at the first valve seat ( 63 ) and in the basic position [ 7 ] on the second valve seat ( 64 ) is present. The function is similar to the embodiments according to 4 and 5 with the one exception that after the connection of the supply pressure hose ( 30 ) the ventilation of the storage pressure container ( 9 ) via the container connection ( 3 ), which via the formed as a grooved ring second check valve ( 6 ) takes place, takes place only when the 3/2-way valve ( 70 ) from its starting position [ 8th ] in its switching position [ 7 ], since the pressure of the supply connection ( 1 ) then on the second U-ring check valve ( 6 ) is also present.

One too 7 . 8th modified embodiment is when the check valves ( 6 ) and ( 19 ) not as groove rings in the valve slide ( 10 ), but as a separate, arranged in the housing check valves ( 6 ' ) and ( 19 ' ) are executed. The groove rings ( 6 ) and ( 19 ) are then replaced by corresponding O-rings. Here it is not related to 7 . 8th explained limitation that the ventilation of the reservoir pressure tank ( 9 ) only after the transition of the 3/2-way valve ( 70 ) takes place in its switching position.

The representations after 9 and 10 show the embodiment according to 7 . 8th in which instead of a 3/2-way valve ( 70 ) two 2/2-way valves, a first 2/2-way valve ( 68 ) as a vent valve and a second 2/2-way valve ( 69 ) are provided as a vent valve. In the basic position 9 is the first 2/2-way valve ( 68 ), the corresponding valve switching member is from the first valve seat ( 63 ), so that a ventilation through the supply connection ( 1 ) he follows; however, the second 2/2-way valve ( 69 ) closed, the second valve seat ( 64 ) is closed, so that according to the above-described basic position function of the valve slide ( 10 ) by duck force to the first stop ( 26 ) is pushed.

In the demolition position after 10 is the second 2/2-way valve ( 69 ) open; the opened second valve seat ( 64 ) allows venting of the valve slide ( 10 ) acting pressure chamber, so that via the return spring ( 11 ) the demolition position at the second stop ( 27 ) is taken. In this position, the first 2/2-way valve ( 68 ) [first valve seat ( 63 )], so that the pressure chamber ( 67 ), as explained above, from the supply connection ( 1 ) is separated.

It follows a list of further embodiments the invention:

Embodiment 1

• a) Es ist ein Versorgungsanschluss zur Verbindung mit einem den Vorratsdruck zwischen dem Zugfahrzeug und dem Anhänger übertragenden Druckschlauch vorgesehen;
• b) es ist ein Bremsvorgabeanschluss zur Verbindung mit einem den Bremsdruck vom Zugfahrzeug zum Anhänger übertragenden Druckschlauch vorgesehen;
• c) es ist ein Behälteranschluss zur Verbindung mit einem Vorrats-Druckbehälter des Anhängers vorgesehen;
• d) es ist ein Bremsdruckanschluss zur Ausgabe des Bremsdruckes vorgesehen;
• e) bei druckbeaufschlagtem Versorgungsanschluss ist der am Bremsdruckanschluss anliegende Druck vom am Bremsvorgabeanschluss anliegenden Druck abhängig;
• f) bei drucklosem Versorgungsanschluss ist der Bremsdruckanschluss pneumatisch mit dem Behälteranschluss verbunden;
• g) es sind außerhalb der Ventileinrichtung angeordnete Federspeicherbremszylinder vorgesehen, deren Betriebsbremskammern, gegebenenfalls unter Verwendung weiterer Pneumatik-Schaltelemente, mit dem Bremsdruckanschluss verbindbar sind, und deren Lösekammern, gegebenenfalls unter Verwendung weiterer Pneumatik-Schaltelemente, über ein erstes Rückschlagventil mit dem im Vorrats-Druckbehälter herrschenden Druck befüllbar sind; gekennzeichnet durch das folgende Merkmal:
• h) Bei drucklosem Versorgungsanschluss ist die Wirkung des ersten Rückschlagventils aufgehoben.

Valve device for a trailer coupled to a towing vehicle for connection to the trailer braking device, having the following features:

• a) It is provided a supply connection for connection to a pressure between the towing vehicle and the trailer transmitting pressure hose;
• b) there is provided a brake specification port for connection to a brake hose pressure from the tractor to the trailer transmitting pressure hose;
• c) there is provided a container port for connection to a reservoir pressure vessel of the trailer;
• d) there is provided a brake pressure port for outputting the brake pressure;
• e) when there is a pressurized supply connection, the pressure applied to the brake pressure connection depends on the pressure applied to the brake specification port;
• f) when the supply port is depressurised, the brake pressure port is pneumatically connected to the reservoir port;
• g) there are provided outside the valve device arranged spring brake cylinder whose service brake chambers, optionally using other pneumatic switching elements, are connectable to the brake pressure port, and their release chambers, optionally using other pneumatic switching elements, via a first check valve with the supply pressure vessel prevailing pressure can be filled; characterized by the following feature:
• h) When the supply port is depressurised, the effect of the first check valve is removed.

Embodiment 2

Trailer brake valve with features of the embodiment 1, characterized in that the Cancellation of the action of the check valve one parallel to the first check valve arranged bypass channel is provided.

Embodiment 3

Trailer brake valve with features of the embodiment 2, characterized in that in Valve for connection to the dissolving chambers of the Spring brake cylinder, optionally using further Pneumatic switching elements, a separate connection is provided.

Embodiment 4

• a) Das erste Rückschlagventil ist im Anhängerbremsventil angeordnet;
• b) der Bypasskanal ist im Anhängerbremsventil angeordnet.

Trailer brake valve with features of embodiment 3, characterized by the following features:

• a) The first check valve is arranged in the trailer brake valve;
• b) the bypass channel is arranged in the trailer brake valve.

Embodiment 5

Trailer brake valve with features of the embodiment 1, characterized in that at pressurized supply connection of the brake pressure connection pneumatically connected directly to the brake specification port.

Embodiment 6

• a) Es ist ein Ventilschieber vorgesehen;
• b) zur Betätigung des Ventilschiebers ist ein Kolben mit einer ersten und mit einer zweiten Wirkfläche vorgesehen.

Trailer brake valve with at least one of the features of the embodiments 1 to 5, characterized by the following features:

• a) There is provided a valve spool;
• b) for actuating the valve slide, a piston is provided with a first and a second effective area.

Embodiment 7

• a) Das Ventil ist als Schieberventil ausgeführt;
• b) zur gegenseitigen Abdichtung der in den verschiedenen Ventil-Schaltstellungen wirksamen pneumatischen Druckräume für die pneumatischen Wege im Ventil ist mehr als eine Schieberventildichtung vorgesehen.

Trailer brake valve with features of embodiment 6, characterized by the following features:

• a) The valve is designed as a slide valve;
• b) for the mutual sealing of the effective in the various valve switching positions pneumatic pressure chambers for the pneumatic paths in the valve more than a spool valve seal is provided.

Embodiment 8

Trailer brake valve with at least one of the features of the embodiments 6 or 7, characterized characterized in that first check valve is arranged in the end wall of the valve spool.

Embodiment 9

Trailer brake valve with at least one the features of the embodiments 6 or 7, characterized in that the bypass channel is arranged as a pressure channel in the valve housing.

Embodiment 10

Trailer brake valve according to one of the embodiments 6 to 9, characterized in that the first effective area is greater than the second effective area is trained.

Embodiment 11

• a) Der Kolben ist als Betätigungskolben ausgebildet;
• b) der Betätigungskolben und der Ventilschieber sind baulich vereinigt.

Trailer brake valve with features of embodiment 10, characterized by the following features:

• a) The piston is designed as an actuating piston;
• b) the actuating piston and the valve slide are structurally combined.

Embodiment 12

• a) Die erste Wirkfläche ist durch die Querschnittsfläche des Betätigungskolbens gebildet;
• b) die zweite Wirkfläche ist durch eine sich aus der baulichen Vereinigung von Betätigungskolben und Ventilschieber ergebenden Ringfläche gebildet;

Trailer brake valve according to at least one of the preceding embodiments, characterized by the following features:

• a) the first effective area is formed by the cross-sectional area of the actuating piston;
• b) the second active surface is formed by a resulting from the structural combination of actuating piston and valve slide ring surface;

Embodiment 13

Trailer brake valve with features of the embodiment 12, characterized in that both active surfaces through a second check valve are connected.

Embodiment 14

Trailer brake valve with features of the embodiment 13, characterized in that for the second check valve one of the second to the first effective area extending passage direction is provided.

Embodiment 15

• a) Die erste Wirkfläche ist pneumatisch mit dem Behälteranschluss verbunden;
• b) die zweite Wirkfläche ist pneumatisch mit dem Versorgungsanschluss verbunden.

Trailer brake valve according to one of the preceding embodiments, characterized by the following features:

• a) the first active surface is pneumatically connected to the container port;
• b) the second active surface is pneumatically connected to the supply connection.

Embodiment 16

• a) Es ist ein Löseanschluss vorgesehen;
• b) der Löseanschluss ist pneumatisch mit der ersten Wirkfläche verbunden.

Trailer brake valve according to one of the preceding embodiments, characterized by the following features:

• a) A release connection is provided;
• b) the release connection is pneumatically connected to the first effective surface.

Embodiment 17

• a) Das Ventil ist als Schieberventil ausgeführt;
• b) zur Verbindung mit den Lösekammern der Federspeicherbremszylinder ist im Ventil, gegebenenfalls unter Verwendung weiterer Pneumatik-Schaltelemente, ein separater Parkanschluss vorgesehen.

Trailer brake valve according to one of the embodiments 1 or 5, characterized by the following features:

• a) The valve is designed as a slide valve;
• b) for connection to the release chambers of the spring brake cylinder, a separate parking connection is provided in the valve, optionally using other pneumatic switching elements.

Embodiment 18

• a) Das Schieberventil weist einen mit einer Rückstellfeder belasteten Ventilschieber mit zwei Stellungen, einer Grundstellung und einer Abrissstellung, auf;
• b) die Grundstellung ist bei druckbeaufschlagtem Versorgungsanschluss durch eine auf den Ventilschieber über eine Wirkfläche einwirkende Druckkraft eingenommen;
• c) die Abrissstellung ist bei drucklosem Versorgungsanschluss durch die Wirkung der Rückstellfeder eingenommen.

Gate valve with features of embodiment 17, characterized by the following features:

• a) The slide valve has a loaded with a return spring valve spool with two positions, a basic position and a tear position on;
• b) the basic position is taken at pressurized supply connection by a force acting on the valve spool over an effective surface pressure force;
• c) the tear-off position is assumed by the action of the return spring when the supply connection is depressurised.

Embodiment 19

• a) Es ist ein mit dem Druck des Versorgungsanschlusses beaufschlagtes Vorsteuerventil mit zwei Stellungen, einer Ausgangsstellung und einer Schaltstellung, vorgesehen;
• b) die auf den Ventilschieber einwirkende Druckkraft ist von der Stellung des Vorsteuerventils abhängig.

Gate valve having the features of embodiment 18, characterized by the following features:

• a) It is provided with the pressure of the supply port pilot valve with two positions, a starting position and a switching position, provided;
• b) the pressure acting on the valve spool pressure depends on the position of the pilot valve.

Embodiment 20

• a) Bei Unterschreiten einer festlegbaren Druckschwelle durch den am Versorgungsanschluss anliegenden Druck ist am Vorsteuerventil durch die Wirkung einer Feder die Ausgangsstellung eingenommen;
• b) bei Erreichen oder Überschreiten der festlegbaren Druckschwelle durch den am Versorgungsanschluss anliegenden Druck ist am Vorsteuerventil die Schaltstellung eingenommen.

Gate valve having the features of embodiment 19, characterized by the following features:

• a) If the pressure falls below a definable pressure threshold due to the pressure applied to the supply connection, the pilot valve will be the starting position due to the action of a spring taken;
• b) on reaching or exceeding the definable pressure threshold by the voltage applied to the supply connection, the switching position is taken on the pilot valve.

Embodiment 21

spool valve with the features of the embodiment 20, characterized in that in the switching position of the pilot valve on the valve spool acting compressive force is increased.

Embodiment 22

spool valve with the features of the embodiment 21, characterized in that the Magnification of the realized on the valve spool pressure by a pressure increase is.

Embodiment 23

spool valve with the features of the embodiment 21, characterized in that the Pilot valve is integrated in the valve spool.

Embodiment 24

• a) In der Ausgangsstellung des Vorsteuerventils ist durch die Wirkung der Feder eine dichtende Verbindung eines Ventilschaltgliedes mit einem ersten Ventilsitz hergestellt;
• b) in der Schaltstellung des Vorsteuerventils ist eine dichtende Verbindung des Ventilschaltgliedes mit einem zweiten Ventilsitz hergestellt.

Gate valve having the features of embodiment 23, characterized by the following features:

• a) In the initial position of the pilot valve, a sealing connection of a valve switching member is made with a first valve seat by the action of the spring;
• b) in the switching position of the pilot valve, a sealing connection of the valve switching member is made with a second valve seat.

Embodiment 25

spool valve with the features of the embodiment 24, characterized in that the height of definable pressure threshold for taking the switching position of the pilot valve by the properties of acting on the valve switching member Spring and the effective diameter of the first valve seat are determined.

Embodiment 26

spool valve with the features of the embodiment 25, characterized in that the formation of a switching hysteresis for the definable pressure threshold of the effective diameter of the second valve seat is bigger than the effective diameter of the first valve seat is selected.

Embodiment 27

spool valve with the features of the embodiment 22, characterized in that the Pilot valve in a separately to the housing part of the valve spool attached housing part arranged is.

Embodiment 28

spool valve with the features of the embodiment 27, characterized in that the Pilot valve is realized as a 3/2-way valve.

Exemplary embodiment 29

spool valve with the features of the embodiment 28, characterized in that the Pilot valve as a combination of two 2/2-way valves is realized.

Claims (6)

Valve device for a towing vehicle connectable trailer, having the following features: a) the valve device has a trailer brake valve ( 8th ), a service brake release valve ( 33 ) and a parking valve ( 20 ), b) the trailer brake valve ( 8th ) b1) via the service brake release valve ( 33 ) supplied by the supply pressure of the tractor vehicle supply connection ( 1 ) (b2) a brake specification port supplied by the tractor's brake pressure ( 4 ), b3) one with a reservoir pressure vessel ( 9 ) of the trailer connected container connection ( 3 ) b4) a brake pressure connection ( 2 ) for outputting the brake pressure, possibly via a pressure control device ( 29 . 42 ), service brake chambers of provided in the trailer spring brake cylinder ( 38 . 39 . 40 . 41 ), b5) and a parking connection ( 21 ), via the parking valve ( 20 ) with the release chambers of the spring brake cylinder ( 38 . 39 . 40 . 41 ), if necessary using further pneumatic switching elements ( 52 ), c) the service brake release valve ( 33 ) and the parking valve ( 20 ) is manually operable via a respective actuating button, d) the service brake release valve ( 33 ) has a drive position and a release position, wherein in the release position of the supply pressure vessel ( 9 ) of the trailer with the supply connection ( 1 ) of the trailer brake valve, e) the parking valve ( 20 ) has a driving position and a parking position, wherein in the parking position to the release chambers of the spring brake cylinder ( 38 . 39 . 40 . 41 ) leading connection ( 51 ) of the parking valve is vented, f) with pressurized supply connection ( 1 ) is the at the brake pressure connection ( 2 ) applied pressure from at the brake specification port ( 4 ) depending pressure; g) with unpressurized supply connection ( 1 ) is the brake pressure connection ( 2 ) pneumatically with the container connection ( 3 ) connected; h) the parking connection ( 21 ) is via a first check valve ( 19 ) with the reservoir pressure vessel ( 9 ) of the trailer; i) with unpressurized supply connection ( 1 ) is independent of the pressure at the tank connection ( 3 ) the effect of the first check valve ( 19 ) canceled. Valve device for a towing vehicle connectable trailer, having the following features: a) the valve device has a trailer brake valve ( 8th ), a service brake release valve ( 33 ) and a parking valve ( 20 ), b) the trailer brake valve ( 8th ) b1) via the service brake release valve ( 33 ) supplied by the supply pressure of the tractor vehicle supply connection ( 1 ) (b2) a brake specification port supplied by the tractor's brake pressure ( 4 ), b3) one with a reservoir pressure vessel ( 9 ) of the trailer connected container connection ( 3 ) b4) a brake pressure connection ( 2 ) for outputting the brake pressure, possibly via a pressure control device ( 29 . 42 ), service brake chambers of provided in the trailer spring brake cylinder ( 38 . 40 . 41 ), b5) and a parking connection ( 21 ), via the parking valve ( 20 ) with the release chambers of the spring brake cylinder ( 38 . 39 . 40 . 41 ), if necessary using further pneumatic switching elements ( 52 ), c) the service brake release valve ( 33 ) and the parking valve ( 20 ) is manually operable via a respective actuating button, d) the service brake release valve ( 33 ) has a drive position and a release position, wherein in the release position of the supply pressure vessel ( 9 ) of the trailer with the supply connection ( 1 ) of the trailer brake valve, e) the parking valve ( 20 ) has a driving position and a parking position, wherein in the parking position to the release chambers of the spring brake cylinder ( 38 . 39 . 40 . 41 ) leading connection ( 51 ) of the parking valve is vented, f) in the event of a pressurized supply connection ( 1 ) is the at the brake pressure connection ( 2 ) applied pressure from at the brake specification port ( 4 ) depending pressure; g) with unpressurized supply connection ( 1 ) is the brake pressure connection ( 2 ) pneumatically with the container connection ( 3 ) connected; h) the parking connection ( 21 ) is via a first check valve ( 19 ) with the reservoir pressure vessel ( 9 ) of the trailer; i) with unpressurized supply connection ( 1 ) is independent of the pressure at the tank connection ( 3 ) the effect of the first check valve ( 19 ), j) in the event of a pressurized supply connection ( 1 ) is the brake pressure connection ( 2 ) pneumatically directly to the brake specification port ( 4 ) connected. Valve device for a towing vehicle connectable trailer with the further features: a) the valve device has a trailer brake valve ( 8th ), a service brake release valve ( 33 ) and a parking valve ( 20 ), b) the trailer brake valve ( 8th ) b1) via the service brake release valve ( 33 ) supplied by the supply pressure of the tractor vehicle supply connection ( 1 ) (b2) a brake specification port supplied by the tractor's brake pressure ( 4 ), b3) one with a reservoir pressure vessel ( 9 ) of the trailer connected container connection ( 3 ) b4) a brake pressure connection ( 2 ) for outputting the brake pressure, possibly via a pressure control device ( 29 . 42 ), service brake chambers of provided in the trailer spring brake cylinder ( 38 . 40 . 41 ), b5) and a parking connection ( 21 ), via the parking valve ( 20 ) with the release chambers of the spring brake cylinder ( 38 . 39 . 40 . 41 ), if necessary using further pneumatic switching elements ( 52 ), c) the service brake release valve ( 33 ) and the parking valve ( 20 ) is manually operable via a respective actuating button, d) the service brake release valve ( 33 ) has a drive position and a release position, wherein in the release position of the supply pressure vessel ( 9 ) of the trailer with the supply connection ( 1 ) of the trailer brake valve, e) the parking valve ( 20 ) has a driving position and a parking position, wherein in the parking position to the release chambers of the spring brake cylinder ( 38 . 39 . 40 . 41 ) leading connection ( 51 ) of the parking valve is vented, f) in the event of a pressurized supply connection ( 1 ) is the at the brake pressure connection ( 2 ) applied pressure from at the brake specification port ( 4 ) depending pressure; g) with unpressurized supply connection ( 1 ) is the brake pressure connection ( 2 ) pneumatically with the container connection ( 3 ) connected; h) the parking connection ( 21 ) is via a first check valve ( 19 ) with the reservoir pressure vessel ( 9 ) of the trailer; i) with unpressurized supply connection ( 1 ) is independent of the pressure at the tank connection ( 3 ) the effect of the first check valve ( 19 ), j) in the event of a pressurized supply connection ( 1 ) is the brake pressure connection ( 2 ) pneumatic di directly to the brake specification port ( 4 l) for actuating the valve slide, a piston with a first and a second effective area is provided, m) the valve is designed as a slide valve, n) for mutual sealing of the effective in the various valve switching positions pneumatic Pressure chambers for the pneumatic paths in the valve is provided more than a slide valve seal. Valve device for a towing vehicle connectable trailer with the further features: a) the valve device has a trailer brake valve ( 8th ), a service brake release valve ( 33 ) and a parking valve ( 20 ), b) the trailer brake valve ( 8th ) b1) via the service brake release valve ( 33 ) supplied by the supply pressure of the tractor vehicle supply connection ( 1 ) (b2) a brake specification port supplied by the tractor's brake pressure ( 4 ), b3) one with a reservoir pressure vessel ( 9 ) of the trailer connected container connection ( 3 ) b4) a brake pressure connection ( 2 ) for outputting the brake pressure, possibly via a pressure control device ( 29 . 42 ), service brake chambers of provided in the trailer spring brake cylinder ( 38 . 40 . 41 ), b5) and a parking connection ( 21 ), via the parking valve ( 20 ) with the release chambers of the spring brake cylinder ( 38 . 39 . 40 . 41 ), if necessary using further pneumatic switching elements ( 52 ), c) the service brake release valve ( 33 ) and the parking valve ( 20 ) is manually operable via a respective actuating button, d) the service brake release valve ( 33 ) has a drive position and a release position, wherein in the release position of the supply pressure vessel ( 9 ) of the trailer with the supply connection ( 1 ) of the trailer brake valve, e) the parking valve ( 20 ) has a driving position and a parking position, wherein in the parking position to the release chambers of the spring brake cylinder ( 38 . 39 . 40 . 41 ) leading connection ( 51 ) of the parking valve is vented, f) in the event of a pressurized supply connection ( 1 ) is the at the brake pressure connection ( 2 ) applied pressure from at the brake specification port ( 4 ) depending pressure; g) with unpressurized supply connection ( 1 ) is the brake pressure connection ( 2 ) pneumatically with the container connection ( 3 ) connected; h) the parking connection ( 21 ) is via a first check valve ( 19 ) with the reservoir pressure vessel ( 9 ) of the trailer; i) with unpressurized supply connection ( 1 ) is independent of the pressure at the tank connection ( 3 ) the effect of the first check valve ( 19 ), j) in the event of a pressurized supply connection ( 1 ) is the brake pressure connection ( 2 ) pneumatically directly to the brake specification port ( 4 k) there is provided a valve slide l) for actuating the valve slide, a piston with a first and a second effective area is provided, m) the valve is designed as a slide valve, n) for mutual sealing of the effective in the various valve switching positions pneumatic pressure chambers For the pneumatic paths in the valve more than one slide valve seal is provided, o) a separate parking connection is provided in the valve for connection to release chambers of a spring brake cylinder, p) the slide valve has a loaded with a return spring valve slide with two positions, a basic position and a tear-off , q) When the supply connection is pressurized, the basic position is assumed by a compressive force acting on the valve spool over an effective surface. r) The tear-off position is assumed when the supply port is depressurised due to the action of the return spring. Valve device for a towing vehicle connectable trailer with the further features: a) the valve device has a trailer brake valve ( 8th ), a service brake release valve ( 33 ) and a parking valve ( 20 ), b) the trailer brake valve ( 8th ) b1) via the service brake release valve ( 33 ) supplied by the supply pressure of the tractor vehicle supply connection ( 1 ) (b2) a brake specification port supplied by the tractor's brake pressure ( 4 ), b3) one with a reservoir pressure vessel ( 9 ) of the trailer connected container connection ( 3 ) b4) a brake pressure connection ( 2 ) for outputting the brake pressure, possibly via a pressure control device ( 29 . 42 ), service brake chambers of provided in the trailer spring brake cylinder ( 38 . 40 . 41 ), b5) and a parking connection ( 21 ), via the parking valve ( 20 ) with the release chambers of the spring brake cylinder ( 38 . 39 . 40 . 41 ), if necessary using further pneumatic switching elements ( 52 ), c) the service brake release valve ( 33 ) and the parking valve ( 20 ) is manually operable via a respective actuating button, d) the service brake release valve ( 33 ) has a drive position and a release position, wherein in the release position of the supply pressure vessel ( 9 ) of the trailer with the supply connection ( 1 ) of the trailer valve, e) the parking valve ( 20 ) has a driving position and a parking position, wherein in the parking position to the release chambers of the spring brake cylinder ( 38 . 39 . 40 . 41 ) leading connection ( 51 ) of the parking valve is vented, f) in the event of a pressurized supply connection ( 1 ) is the at the brake pressure connection ( 2 ) applied pressure from at the brake specification port ( 4 ) depending pressure; g) with unpressurized supply connection ( 1 ) is the brake pressure connection ( 2 ) pneumatically with the container connection ( 3 ) connected; h) the parking connection ( 21 ) is via a first check valve ( 19 ) with the reservoir pressure vessel ( 9 ) of the trailer; i) with unpressurized supply connection ( 1 ) is independent of the pressure at the tank connection ( 3 ) the effect of the first check valve ( 19 ), j) in the event of a pressurized supply connection ( 1 ) is the brake pressure connection ( 2 ) pneumatically directly to the brake specification port ( 4 k) there is a valve slide l) for actuating the valve slide, a piston with a first and a second effective area is provided, m) the valve is designed as a slide valve, n) for mutual sealing of the effective in the various valve switching positions pneumatic pressure chambers For the pneumatic paths in the valve more than one slide valve seal is provided, o) a separate parking connection is provided in the valve for connection to release chambers of a spring brake cylinder, p) the slide valve has a loaded with a return spring valve slide with two positions, a basic position and a tear-off , q) the basic position is occupied by a pressure force acting on the valve spool over an active surface in the case of a pressurized supply connection, r) the tear - off position is assumed by the action of the return spring when the supply port is depressurised; Pressure applied to the supply port applied pilot valve with two positions, a starting position and a switching position, t) the pressure acting on the valve spool pressure force is dependent on the position of the pilot valve. Valve device for a towing vehicle connectable trailer with the further feature: a) the valve device has a trailer brake valve ( 8th ), a service brake release valve ( 33 ) and a parking valve ( 20 ), b) the trailer brake valve ( 8th ) b1) via the service brake release valve ( 33 ) supplied by the supply pressure of the tractor vehicle supply connection ( 1 ) (b2) a brake specification port supplied by the tractor's brake pressure ( 4 ), b3) one with a reservoir pressure vessel ( 9 ) of the trailer connected container connection ( 3 ) b4) a brake pressure connection ( 2 ) for outputting the brake pressure, possibly via a pressure control device ( 29 . 42 ), service brake chambers of provided in the trailer spring brake cylinder ( 38 . 40 . 41 ), b5) and a parking connection ( 21 ), via the parking valve ( 20 ) with the release chambers of the spring brake cylinder ( 38 . 39 . 40 . 41 ), if necessary using further pneumatic switching elements ( 52 ), c) the service brake release valve ( 33 ) and the parking valve ( 20 ) is manually operable via a respective actuating button, d) the service brake release valve ( 33 ) has a drive position and a release position, wherein in the release position of the supply pressure vessel ( 9 ) of the trailer with the supply connection ( 1 ) of the trailer brake valve, e) the parking valve ( 20 ) has a driving position and a parking position, wherein in the parking position to the release chambers of the spring brake cylinder ( 38 . 39 . 40 . 41 ) leading connection ( 51 ) of the parking valve is vented, f) in the event of a pressurized supply connection ( 1 ) is the at the brake pressure connection ( 2 ) applied pressure from at the brake specification port ( 4 ) depending pressure; g) with unpressurized supply connection ( 1 ) is the brake pressure connection ( 2 ) pneumatically with the container connection ( 3 ) connected; h) the parking connection ( 21 ) is via a first check valve ( 19 ) with the reservoir pressure vessel ( 9 ) of the trailer; i) with unpressurized supply connection ( 1 ) is independent of the pressure at the tank connection ( 3 ) the effect of the first check valve ( 19 ), j) in the event of a pressurized supply connection ( 1 ) is the brake pressure connection ( 2 ) pneumatically directly to the brake specification port ( 4 k) there is provided a valve slide l) for actuating the valve slide, a piston with a first and a second effective area is provided, m) the valve is designed as a slide valve, n) for mutual sealing of the effective in the various valve switching positions pneumatic pressure chambers for the pneumatic paths in the valve more than one slide valve seal is provided, o) a separate parking connection is provided in the valve for connection to release chambers of a spring brake cylinder, p) the slide valve has a valve slide loaded with a return spring with two positions, a basic position and a tear-off position on, q) the basic position is occupied by pressurized force acting on the valve spool with pressurized supply connection, r) the tear-off position is occupied by the action of the return spring when the supply port is depressurized, s) it is one with the pressure t) the pressure acting on the valve spool pressure is dependent on the position of the pilot valve, u) the pilot valve is integrated in the valve spool, v) in the initial position of the pilot valve is through the W) in the switching position of the pilot valve, a sealing effect of the valve switching member is ensured with a second valve seat, x) the height of the definable Pressure threshold for taking the switching position of the pilot valve is determined by the properties of the spring acting on the valve member and the effective diameter of the first valve seat, y) to form a hysteresis for the definable pressure threshold, the effective diameter of the second valve seat is greater than the effective diameter the first valve seat selected.