DE102005050169A1 - LS control arrangement and LS directional control valve - Google Patents

Abstract

The linear saturation (LS) control device has a path valve (1), the valve slide (10) of which enables consumer connections (A, B) to be made for two consumers to an input connection (P) and an output connection (T). The flow path can be connected to two successive or overlapping pressure limiting chambers (24, 28) with pressure limiting valves (6, 8).

Description

The The invention relates to a LS control arrangement according to the preamble of the claim 1 and one for such a control arrangement suitable LS-way valve.

Such LS control arrangements are for example from the DE 197 15 020 A1 or from the datasheet published by the applicant RD 64 282 (Control block M4) known and are used for example in mobile work equipment to provide their consumers with pressure medium. Each of the consumers is assigned an LS directional control valve, via which the speed and the direction of the pressure medium volume flow conveyed by a pump are controlled. The pump pressure is set in LS systems so that it is above the highest load pressure of the consumer by a certain RegelΔp, for example 20 bar. The pressure medium volume flow over a set by an inlet control edge of the LS-way valve inlet orifice is kept constant independent of the load in the mentioned known solutions by a LS or individual pressure compensator. A pressure compensator piston of the individual pressure compensator is biased by a spring in the opening direction, in addition to the force of the spring acts downstream of the inlet orifice metered load pressure also in the opening direction. In the closing direction of the pressure compensator piston acts upstream of the inlet orifice and downstream of the individual pressure compensated tapped inlet pressure. In the prior art, the individual pressure compensator upstream of the inlet orifice plate, in principle, the individual pressure compensator also as in one of the US Pat. No. 4,787,294 known embodiment can be arranged downstream of the inlet orifice.

The Individual pressure balance reacts to load pressure changes and is at a Last booster in the opening direction and shifted at a load pressure reduction in the closing direction. This will the pressure in the inlet to the inlet orifice plate through the individual pressure compensator adjusted so that by this inlet pressure in the closing direction acting force is in equilibrium, with the opening direction acting force the spring and the force equivalent of the load pressure. Accordingly, the pressure in the inlet is always around the constant, the spring force corresponding amount higher than the load pressure adjusted so that above the inlet orifice constant pressure gradient and thus a constant volume flow is present (load pressure independent volume flow control).

at the known mobile control block M4 can protect the consumer side machinery equipment the load pressure at the two load ports of a piston axis through each a pressure relief valve can be limited individually. When responding This pressure relief valve will distort the actual load pressure the individual pressure compensator forwarded, so that the above Volume flow control to the consumer connection are disabled can. The over the inlet measuring orifice set pressure medium volume flow can be reduced, for example when the consumer is driven against a high resistance which is actually an inlet pressure above the set Would require maximum pressure. In this case, however, the inlet pressure on the pressure relief valve set value not more than to exceed the spring force. As each consumer connection assigned a pressure relief valve is, can for each Consumer connection set different pressure settings become.

It can However, operating conditions occur in which one direction of motion of the consumer at different working speeds different maximum pressures must be achieved. For example, it may be necessary to assist the consumer greater speed only with a low pressure, but at a lower speed with a higher one Pressure to operate.

at another application is z. For example, the speed of a sink movement a crane jib by a so-called flow rate control causes. For this purpose, a lowering brake valve from the inlet pressure in the Movement of crane boom controlling hydraulic cylinder controlled on. Because the opening pressure the lowering brake valve influences the lowering speed of the crane jib has, this opening pressure must preferably kept constant to possible To avoid vibrations. For this purpose, the above-described pressure relief valve can be to limit the load pressure, so that the inlet flow control is ineffective when the pressure relief valve responds. By the Kinematics of the crane boom, however, this can when lowering in Be moved positions in which a higher pressure is required as the set opening pressure. This is z. B. a small area at the end of the lowering, wherein the Crane boom is in a position of a load reversal, in its own weight requires a much higher inlet pressure - in this For safety reasons, the crane boom should only operate at low speed at higher Pressure to be moved.

Such operating conditions can not be controlled with the known solutions described above, since the inlet pressure through the egg nem consumer connection associated pressure relief valve can only be limited to one value.

In contrast, lies The invention is based on the object, a LS control arrangement and one for that suitable LS-way valve to create a multi-stage supply pressure limit.

These Task is in terms of LS control arrangement by the feature combination of claim 1 and in terms of LS-way valve by the features of the independent claim 14 solved.

According to the invention Adjusting a valve spool of the LS directional control valve in one direction an LS control oil flow path for picking up the load pressure successively or overlapping with two pressure limiting chambers each connected to a pressure relief valve for LS-pressure limitation assigned. The load pressure leaves so on in different stroke ranges of the valve spool on limit different values, so that a supply pressure limit in the manner described above is possible.

there it is preferred if the maximum pressure in during a first partial lift of the valve spool with the LS control oil flow path connected pressure limiting chamber is set to a higher pressure, as the one in the second pressure-limiting chamber during a subsequent Partial lift is effective. In this case, it may be allowed that in a transition area both pressure limiting chambers are connected to the LS control oil flow path, since then in any case the pressure limiting valve set to the lower value responds and thus limits the inlet pressure in the second partial stroke.

at a concrete solution the valve spool has a pressure limiting channel, the one part of the LS control oil flow path forms. This pressure limiting channel opens on the one hand during the Adjustment of the valve spool in one direction in one with associated with the associated load port work control chamber and on the other hand the first partial stroke of the valve spool in the first pressure limiting chamber during the second partial lift in the second pressure limiting chamber.

Around the size of the pressure relief valves and the tax oil loss preferably is low in the pressure limiting channel between the load tap and the pressure relief valve formed a Lastabgriffsdüse.

Of the Valve slide is particularly simple, if on the outer circumference two spaced circumferential recesses are formed, in which one with the valve spool penetrating pressure limiting channel connected nozzle channel opens d. h., the pressure limiting channel is over the first during the first partial stroke Circumferential recess and the associated first nozzle channel with the first pressure limiting chamber and while the further partial lift over the second circumferential recess and the second nozzle channel with the second pressure limiting chamber connected is. The function start and the functional area of the second pressure relief valve can then by the location and length of Circumferential recesses are determined in the valve spool. This very much simple construction allows es, the LS-way valve, except the control piston with series components to realize.

The Circumferential recesses are preferred for minimizing leakage designed as pockets.

In the neutral position of the LS-way valve is the LS control chamber via a the pressure limiting chambers and a tank groove on the valve spool with connected to a drain chamber.

In the other adjustment direction of the valve spool is the load pressure over a LS channel tapped and reported in the LS control chamber.

The Circumferential recesses are designed such that they can be adjusted the valve spool in the second adjustment direction the connection between shut off the LS control chamber and the pressure limiting chambers, wherein while a comparatively small hub still allowed a connection can be.

Of the Construction of the valve spool is particularly easy when the LS channel and the pressure limiting channel on the one hand in the same piston collar open.

This Piston collar can be designed with a control edge over the in the second partial stroke of the valve spool, the first pressure limiting chamber connected to a drain chamber.

As already mentioned at the beginning, can the individual pressure compensator of the LS control arrangement of the metering orifice be upstream, with a pressure compensator piston in the opening direction from a pressure compensator spring and the limited load pressure and in the closing direction from the pressure in the area between the individual pressure balance and the metering orifice is charged.

other advantageous developments of the invention are the subject of further Dependent claims.

in the The following will be a preferred embodiment of the invention explained in more detail with reference to schematic drawings. Show it:

1 a highly simplified schematic diagram of a piston axis of a mobile control block with two-stage supply pressure limitation;

2 Partial strokes of a valve spool of a LS-way valve 1 with adjustment in one direction and

3 Partial strokes of the valve spool with an adjustment in the other direction.

1 shows a schematic circuit diagram of a valve disc of a mobile control block, through which a piston axis for the pressure medium supply of a consumer, for example, an actuating cylinder of a crane jib is formed. Such a mobile control block has an input member, an end member, and a plurality of directional control elements each associated with a consumer of the mobile implement. This in 1 illustrated an LS control arrangement 1 forming directional control valve element of the valve control block has a pressure port P, two consumer ports A, B, a drain port T and a control oil drain Y. Usually, such directional control valves are still with other terminals, such as a LS connection, connections for tapping the individual load pressure at the load terminals and control terminals executed. Since these do not contribute to the understanding of the invention, they have been for simplicity in the illustration according to 1 omitted. The LS control arrangement 1 has a continuously adjustable directional control valve 2 , an individual pressure balance 4 and two adjustable pressure relief valves 6 . 8th for limiting the load pressure. The basic structure of such a LS control arrangement is already known from the prior art ( RD 64 282 ), so that only the components essential for understanding the invention are described here.

The continuously adjustable directional valve 2 has a valve spool 10 , by an unillustrated Zentrierfederanordnung in his in 1 shown basic position 0 is biased. The valve spool 10 can be moved electrically or hydraulically from its illustrated basic position to the left (working positions A) or to the right (working positions B). In a hydraulic pilot control, for example, pressure reducing valves can be used to the valve spool 2 for adjusting with a control pressure difference to apply. The valve spool 10 is in a valve hole 12 the valve disc out. This is in the illustration according to 1 from right to left in the radial direction to a first discharge chamber 14 , a working chamber 16 , an inlet chamber 18 , another working chamber 20 , a second drain chamber 22 , a first pressure limiting chamber 24 , an LS control chamber 26 and a second pressure limiting chamber 28 extended.

The valve spool 10 is executed with four tax codes, the in 1 right-hand tax bund as a tank collar 30 , the two middle piston collars as tax code 32 and tax code 34 and the in 1 left, slightly longer piston collar as end collar 38 referred to as. The aforementioned bundles are spaced from each other by piston necks. The tank collar 30 closes the valve bore 12 to the right frontally to a spring or control chamber, not shown. At the right-hand ring end face of the Steuerbundes 32 is a process control edge designed with fine control notches 40 and at the other annular end face an inlet control edge 42 educated. Accordingly, the second taxation 34 another inlet control edge 44 and another flow control edge 46 intended. The valve bore 12 to the left in the axial direction to a spring or control chamber towards sealing end collar 38 has a tank control edge formed by the adjacent piston neck 48 , In the illustrated basic position lock the inlet control edges 44 . 42 the pressure medium connection from the inlet chamber 18 to the two adjacent working chambers 16 . 20 from. Their connection to the external drainage chambers 14 . 22 is in the basic position 0 through the two flow control edges 40 . 46 blocked. The tank control edge 48 is inside the second drain chamber 22 , which has a circumferential tank groove 50 on the outer circumference of the end collar 38 with the adjacent pressure limiting chamber 24 connected is. On the outer circumference of the end waistband 38 are further two pocket-shaped or flattened circumferential recesses 52 . 54 provided, wherein the peripheral recess 52 a larger axial length than the other circumferential recess 54 having. In the illustrated basic position opens the smaller circumferential recess 54 in the LS control chamber 26 , the larger circumferential recess 52 connects the pressure limiting chamber 24 with the LS control chamber 26 ,

The valve spool 10 is from a pressure limiting channel 56 interspersed, in the illustrated embodiment of the left end face of the end collar 38 is drilled as axially parallel bore and by means of a sealing plug 58 is closed. The pressure limiting channel 56 extends in the axial direction of the basic position 0 to over the working chamber 20 out and then flows through a Lastabgriffsdüse 60 in the outer periphery of the tax code 34 , In the home position 0 is the load tap nozzle 60 from the ring land between the chambers 18 . 20 covered and thus closed. The pressure limiting channel 56 further opens via a first radial nozzle channel 62 in the larger circumferential recess 52 and a second radial nozzle channel 64 in the smaller circumferential recess 54 (Nozzle channels radial). Accordingly, in the home position, the LS control chamber 26 and the right pressure limiting chamber 24 as well as the pressure limiting channel 56 with the drainage chamber 22 connected and thus depressurized.

In the illustrated embodiment is in the valve spool 10 from the other side (right in 1 ) an axially extending LS channel 66 drilled, which also by a sealing plug 58 is closed and the one hand via a radial bore 68 in the basic position 0 in the pressure limiting chamber 28 opens and on the other hand via a radially extending load tap hole 70 on the outer circumference of the tax code 32 empties. This load tap hole 70 is through the web between the inlet chamber 18 and the working chamber 16 covered in the basic position 0. The inlet chamber 18 is via an inlet channel 72 to an output terminal A of the individual pressure balance 4 connected, whose input terminal P via a pump channel 74 with a LS pump 76 is connected, which can be designed as a variable or constant pump with bypass pressure compensator. The activation of this LS pump 76 takes place - as stated above - depending on the highest load pressure of the driven loads, the pump pressure is adjusted so that it is above the control Δp above this highest load pressure.

The individual pressure balance 4 is executed in the version shown with a load holding function. This is achieved by blocking the connection between P and A in its spring-biased basic position as long as no pump pressure is built up. Such an individual pressure balance 4 thus works in the load holding function similar to a check valve. In the illustrated embodiment, in the control positions (b) the pump pressure in the pump channel 74 via a control line 78 tapped and applied to the pressure compensator piston in the direction of his in 1 Closing position marked with (c). In the opening direction, ie, in the direction of the control positions identified by (b), the pressure compensator piston is on the one hand by the force of the pressure compensator spring 80 and acted upon by the individual load pressure, via one with the LS control chamber 26 connected LS control line 80 is tapped.

The two working chambers 16 . 20 are via a flow channel 82 or a return channel 84 connected to the load terminals A, B. Depending on the control of the directional control valve 2 can the return channel 84 also act as a flow channel and then corresponding to the flow channel 82 lie in the pressure medium return. The pressure relief valve 6 is via a load pressure limiting channel 86 with the pressure limiting chamber 24 connected, accordingly, the other pressure limiting chamber 28 via a further load pressure limiting channel 88 with the further pressure relief valve 8th connected. Upon reaching the on one of the pressure relief valves 6 . 8th set maximum value opens this a connection to the control oil drain Y, so that the pressure in the corresponding pressure limiting chamber 24 . 28 is limited to this maximum value. This maximum pressure is at both pressure relief valves 6 . 8th executed mechanically or electrically / hydraulically changeable. The drain port T is on a run-off channel 90 with the two drainage chambers 14 . 22 connected.

It is now assumed that by adjusting the directional control valve 2 From its illustrated basic position 0 pressure medium via the consumer port A flow to the consumer and should run from this via the consumer port B to the tank T out, so that, for example, a lowering movement of a crane jib can be effected. For this purpose, the valve spool 10 according to 1 shifted to the left, wherein when driving through the total stroke the in 2 positions A1, A2 and A3 are overrun. At the beginning of the adjustment of the valve spool 10 to the left (A1) is via the load tap nozzle 60 the connection of the pressure limiting channel 56 with the working chamber 20 opened before the inlet control edge 44 the connection between the inlet chamber 18 and the working chamber 20 aufsteuert and the flow control edge 40 the pressure medium connection between the drain chamber 14 and the working chamber connected to the consumer port B. 16 opens. The load tap hole 70 stays off the dock between the chambers 16 . 18 covered. During this first part of the stroke is also in the basic position by the tank groove 50 open connection between the drain chamber 22 and the first pressure limiting chamber 24 cordoned off. The LS control chamber 26 is about the larger circumferential recess 52 with the pressure limiting chamber 24 connected and thus also the pressure limiting channel 56 with the LS control chamber 26 connected - ie, in the LS control chamber 26 and into the pressure limiting chamber 24 will be with closed pressure relief valve 6 the pressure in the working chamber 20 reported. during further adjustment of the valve spool 10 is via the inlet control edge 44 an inlet orifice between the inlet chamber 18 and the working chamber 20 on controlled and promoted according to Druckmit tel to the consumer port A. The pressure medium flowing away from the consumer flows via the consumer connection B, the return channel 84 from the flow control edge 40 controlled flow cross-section between the working chamber 16 and the drainage chamber 14 towards the tank T out. The load pressure building up downstream of the inlet orifice is then transmitted via the load tap nozzle 60 , the pressure limiting duct 56 , the first nozzle channel 62 and the longer circumferential recess 52 until reaching the position marked A2 both in the LS control chamber 26 as well as in the pressure limiting chamber 24 reported, with the maximum in the pressure limiting chamber building load pressure through the pressure relief valve 6 is limited, which is set to a higher pressure than the other pressure relief valve 8th , The one in the LS control chamber 26 applied load pressure applied via the LS control line 80 the pressure compensator piston of the individual pressure balance 4 in the opening direction. As long as this load pressure is below the pressure relief valve 6 set value, the individual pressure compensator works 4 in the manner described above and regulates in the inlet channel 72 a pressure that is always around the constant amount of the force of the pressure compensator spring 80 corresponding value is higher than the individual load pressure, so that the pressure drop across the inlet orifice can be kept constant independent of the load pressure and thus depends only on the opening cross-section. When opening the pressure relief valve 6 the effective in the opening direction on the individual pressure compensator load pressure can not exceed this preset maximum value, so that the inlet pressure in the inlet channel 72 is limited accordingly. D. h., At the beginning of the stroke of the valve spool is the pressure relief valve 6 effective, so that the inlet pressure is limited to a relatively high value at low pressure medium flow rate. When moving the valve spool further 10 (Positions A2, A3) is over the longer recess 52 the connection between the pressure limiting chamber 24 and the LS control chamber 26 closed off and on the smaller circumferential recess 54 the connection of the pressure limiting channel 56 to the left pressure limiting chamber 28 over the other nozzle channel 64 controlled on. The over the load tap nozzle 60 Tapped load pressure is also transmitted via the first nozzle channel 62 in the LS control chamber 26 reported, as these in positions A2, A3 but not with the pressure limiting chambers 24 . 28 is connected, flows out of the LS control chamber 26 virtually no control oil off, leaving over the first nozzle channel 62 no pressure drop occurs. The maximum load pressure in the pressure limiting duct 56 and thus in the LS control chamber 26 is set in positions A2, A3 by the pressure relief valve set to a lower pressure 8th limited, whose input via the load pressure limiting channel 88 to the pressure limiting chamber 28 connected. The load tap nozzle 60 ensures that even with the pressure relief valve open 8th over the first nozzle channel 62 not directly the load pressure is reported because the control oil flow through the open pressure relief valve 8th at the load tap nozzle 60 a pressure drop arises. The actual pressure in the pressure limiting duct 56 and thus in the LS control chamber 26 is thus slightly above the pressure relief valve 8th The set value is adjusted until the desired maximum load pressure is set. Accordingly, upon response of the pressure relief valve 8th the inlet pressure is set to a lower value at a higher pressure medium volume flow. During the adjustment of the valve spool A in the direction of the position A3 is on the tank control edge 48 the connection between the drainage chamber 22 and the pressure limiting chamber 24 controlled on, so that the latter is depressurized. Furthermore, remains in the vorbe prescribed positions A1, A2, A3, the Lastabgriffsbohrung 70 from the bridge between the inlet chamber 18 and the working chamber 16 covered. As described above, the start of operation and the functional range of the second pressure relief valve is determined by the geometry of the peripheral recesses 52 . 54 certainly. It is not necessarily required that the pressure limiting channel 56 consecutively with the pressure limiting chamber 24 and the pressure limiting chamber 28 It is also possible, in a transition region, the pressure limiting channel 56 with both pressure limiting chambers 24 . 28 To connect - the pressure is then in any case on the lower, from the pressure relief valve 8th limited value.

If the consumer is now to be supplied with pressure medium via the consumer connection B and the pressure medium flowing away from the consumer flows through the consumer connection A to the tank T, the valve slide will be released from its in 1 shown basic position 0 to the right in the direction of the positions B1, B2 according to 3 postponed. During this adjustment of the valve spool 10 to the right, the load tap hole opens 70 to the working chamber connected to the consumer port B. 16 , At the same time or a little later will be on the inlet control edge 42 the inlet orifice between the inlet chamber 18 and the working chamber 16 controlled and accordingly over the flow control edge 46 a drain cross-section between the working chamber 20 and the drainage chamber 22 open. At the very beginning of the shift from the home position (0) out is the nozzle channel 64 of the valve spool 10 still to the pressure limiting chamber 28 open so that when the load pressure at the load connection is exceeded B is the pressure relief valve set to a lower value 8th can open and some control oil flows to the control oil drain Y - but this loss is relatively low and can be accepted.

The downstream of the inlet orifice in the working chamber 16 applied pressure is applied via the load tap hole 70 , the LS channel 66 and the radial bore 68 in the LS control chamber 26 reported. This load pressure is not limited, so that the individual pressure balance 4 always acted upon by the actual load pressure in the opening direction. during the entire stroke (B1, B2) of the valve spool 10 remains the load tap nozzle 60 from the bridge between the inlet chamber 18 and the working chamber 20 covered, so that no load pressure can be tapped on this.

The above-described construction can be realized in a very simple way with mass-produced components, wherein only the geometry of the control slide by providing the circumferential recesses and the pressure-limiting channel and the Lastabgriffsdüse 60 must be adjusted. In principle, it is also possible, the pressure limiting channel 56 and to open the LS channel in different piston collars.

As already mentioned, the individual pressure compensator can also be connected downstream of the metering orifice. Instead of the pocket-shaped circumferential recesses 52 . 54 also circumferential grooves can be selected - this variant is indeed easier to produce, but has the disadvantage that the leakage is increased.

Disclosed are an LS control arrangement and a LS-way valve, over the the load pressure in an adjustment of the LS-way valve to two different maximum values can be limited.

1

LS control arrangement

2

way valve

4

Individual pressure compensator

6

Pressure relief valve

8th

Pressure relief valve

10

valve slide

12

valve bore

14

drain chamber

16

working chamber

18

inlet chamber

20

Further working chamber

22

Second drain chamber

24

Pressure control chamber

26

LS-control chamber

28

Pressure control chamber

30

tank Bund

32

control collar

34

control collar

36

tank Bund

38

Dead end

40

Flow control edge

42

Inlet control edge

44

Further Inlet control edge

46

Further Flow control edge

48

Tank control edge

50

Tanknut

52

circumferential

54

smaller circumferential

56

Pressure relief channel

58

sealing plug

60

Lastabgriffsdüse

62

1. nozzle channel

64

Second nozzle channel

66

LS-channel

68

radial bore

70

Lastabgriffsbohrung

72

inlet channel

74

pump channel

76

pump

78

control line

80

LS control line

82

forward channel

84

Return channel

86

Load pressure relief channel

88

Another Load pressure relief channel

90

drain channel

Claims (14)

LS control arrangement with a directional control valve ( 2 ), via the valve slide ( 10 ) when adjusting in one direction a first consumer port (A) and when adjusting in the other direction, a second consumer port (B) with an inlet port (P) and the other consumer port with a drain port (T) are connectable via an inlet control edge ( 42 . 44 ) an opening cross-section of an inlet orifice plate is determined, which is an individual pressure balance ( 4 ) is associated with keeping the pressure drop across the inlet orifice plate constant, and with an LS control oil flow path via which the load pressure can be tapped off downstream of the inlet orifice plate and through the valve spool ( 10 ) into an LS control chamber ( 26 ) of the way valve ( 2 ), wherein a maximum pressure in the LS control oil flow path can be limited via a pressure limiting valve, characterized in that the LS control oil flow path is during the adjustment of the valve spool ( 10 ) in one direction successively or overlapping with two pressure-limiting chambers ( 24 . 28 ), to each of which a pressure relief valve ( 6 . 8th ) is assigned to the LS-pressure limitation. LS control arrangement according to claim 1, wherein the maximum pressure in an effective during a first partial lift pressure limiting chamber ( 24 ) to a higher pressure than in the second pressure limiting chamber ( 28 ) is limited. LS control arrangement according to claim 1 or 2, wherein in the valve slide ( 10 ) a pressure limiting channel ( 56 ) is formed, which during the adjustment in one direction on the one hand in a working chamber connected to the first consumer port (A) ( 20 ) and on the other hand during a first partial stroke in the first pressure-limiting chamber ( 24 ) and during a further partial lift in the second pressure-limiting chamber ( 28 ) opens. LS control arrangement according to claim 3, having a load-picking nozzle ( 60 ) in the working chamber-side mouth region of the pressure-limiting channel ( 56 ). LS control arrangement according to claim 4, wherein on the outer circumference of the valve spool ( 10 ) two spaced circumferential recesses ( 52 . 54 ) are formed, in each of which one with the pressure limiting channel ( 56 ) connected nozzle channel ( 62 . 64 ), wherein the pressure limiting channel ( 56 ) via a first circumferential recess ( 52 ) and a first nozzle channel ( 62 ) in the first adjustment range with the first pressure limiting chamber ( 24 ) and during the second partial stroke via the second circumferential recess ( 54 ) and the second nozzle channel ( 64 ) with the second pressure limiting chamber ( 28 ) connected is. LS control arrangement according to claim 5, wherein the circumferential recesses ( 52 . 54 ) are pocket-shaped. LS control arrangement according to one of the claims 3 to 6, having a tank groove ( 50 ), about which in a basic position (0) of the valve spool ( 10 ) the first pressure limiting chamber ( 24 ) with a discharge chamber (T) connected to the drain chamber ( 22 ) connected is. LS control arrangement according to one of the preceding claims, with a valve slide ( 10 ) passing LS channel ( 66 ), which when adjusting the valve spool ( 10 ) in the second direction to Lastabgriff a the second load port (B) zugeord Nete working chamber ( 16 ) with the LS control chamber ( 26 ) connects. LS control arrangement according to claim 5 and 8, wherein the first circumferential recess ( 52 ) is designed such that during the adjustment of the valve spool ( 10 ) in the second direction the connection between the LS control chamber ( 26 ) and the first pressure limiting chamber ( 24 ) locks. LS control arrangement according to one of the claims to claims 8 and 3, wherein the LS channel ( 66 ) and the pressure limiting channel ( 56 ) in the same piston collar ( 38 ). LS control arrangement according to one of the preceding claims, wherein a control edge ( 48 ) of a piston collar ( 38 ) during the second partial stroke, the first pressure limiting chamber ( 24 ) with a drain chamber ( 22 ) connects. LS control arrangement according to one of the preceding claims, wherein the individual pressure compensator ( 4 ) the metering orifice is connected upstream and the pressure compensator piston in the opening direction by the force of a pressure compensator spring ( 80 ) and the load pressure and in the closing direction of the pressure between the individual pressure balance ( 4 ) and the inlet orifice is acted upon. LS control arrangement according to one of the preceding claims, wherein the pressure relief valves ( 6 . 8th ) are made adjustable. LS-way valve, in particular for a LS control arrangement according to one of the preceding claims, via the valve slide ( 10 ) when adjusting in one direction, a first consumer port (A) and when adjusting in the other direction, a second consumer port (B) with an inlet port (P) and the other consumer port with a drain port (T) are connectable via an inlet control edge ( 42 . 44 ) an opening cross-section of an inlet orifice plate is determined, and with an LS control oil flow path, via which the load pressure can be tapped off downstream of the inlet orifice plate and through the valve spool ( 10 ) into an LS control room ( 26 ) is signaled, characterized in that the LS control oil flow path during the adjustment in one direction successively or overlapping with two pressure-limiting chambers ( 24 . 28 ) is connectable, in which the maximum pressure can be limited to different values.