DE102004010374A1 - Flow distributor with several flow valves for supplying different users has piston with to control edges, one for combining pressure flows and other for separating them - Google Patents

Abstract

The flow distributor for several consumers (4, 6, 8, 10) has a pressure regulating piston with to control edges, one for combining pressure flows and the other for separating them. There is also at least one LS-control edge providing an LS cross section when the pressure regulator (26) is open, to control the pressure in the flow path.

Description

The The invention relates to a flow control valve for a flow divider for pressure medium supply a plurality of hydraulic consumers according to the preamble of claim 1 and a flow divider with such flow control valves.

hydraulic Power dividers ensure that a given pressure medium flow load pressure independent in desired Subsets over a plurality of parallel hydraulic consumers or hydraulic loads flows. When the pressure medium flow is directed so that the individual Current valves of the flow divider upstream of the hydraulic consumers are arranged, one speaks of the operating state parts. Lie the individual flow valves, on the other hand, downstream of the hydraulic consumers, one speaks of the operating state summing.

each Flow control valve of a flow divider comprises an orifice plate and a pressure compensator, when sharing downstream of the orifice lies. The pressure compensators become parting in the closing direction from the highest load pressure pressurized and throttled between the respective metering orifice and the load the fluid flow so strong that the pressure after all metering orifices equal to the highest Load pressure is or slightly above this is. With regard to this arrangement and the pressurization The pressure compensator is similar to a flow divider of a so-called LUDV control, such as It shows, for example, WO 95/32364 and which is a special case of one Load sensing control is. In such a controller, the highest Load pressure reported to a variable displacement pump and so regulated, in that in the pump line to a certain pressure difference Ap over the Load pressure lying pump pressure prevails. In a LUDV control the division of the individual partial flows remains even with a drop in the Pump pressure received. Because in this case the so-called undersupply changes at the pressure downstream of the metering orifices Nothing. In front of all metering orifices is in the same way the dropped pump pressure, so that at all metering orifices the pressure difference has changed in the same way.

current divider can independently be used, whether as a pressure medium source a constant pump or a variable displacement pump is used and adjusted as the variable displacement pump becomes. When used in a traction drive, the flow rate for example, depending on adjusted by the deflection of a joystick or a pedal and then through the flow divider the hydraulic consumers in the wished proportions allocated.

A "summing of pressure medium subsets can the control according to WO 95/32364 not afford. When summing It must be ensured that the pressure compensators are not in the closing direction more of the highest, but from the lowest between pressure compensators and consumers upcoming pressures are applied, in which case the pressure at the highest-load consumer is the lowest.

A divider for dividing and summing is from the DE 195 31 497 A1 known. In such a control arrangement, the pressure compensators associated with the consumers are biased by centering springs in an open position, which are acted upon via a switching valve in the operating state "parts" with the highest load pressure and in the operating state "summing" with the lowest effective load pressure, so that in both Operating conditions, the pressure drop across the orifices can be kept constant regardless of load pressure.

adversely in this known solution is that the switching valve is driven according to the operating state must be and that a considerable device-technical effort to pick up the highest or lowest load pressure is required.

In contrast, lies The invention is based on the object, a flow control valve and a to create flow dividers constructed with such flow control valves, where the operating states "divide" and "totalize" with minimal effort are feasible.

These The object is with regard to the flow valve by the features of Claim 1 and in terms of the flow divider by the features of Claim 13 solved.

The inventive, each associated with a consumer flow valve has a metering orifice and a pressure compensator, which regulates on the one side of the metering orifice the highest or the lowest load pressure. A pressure compensator piston of the pressure compensator is designed according to the invention with two control edges, one of which is assigned to the operating state "sum" and the other to the operating state "parts". The flow control valve also has an LS control edge, with which an LS cross-section can be opened when the pressure compensator is fully open to report load in an LS line. When controlled LS cross section can then be tapped off the pressure in a pressure medium flow path between the metering orifice and the input of the pressure compensator. This pressure corresponds to first approximation of the load pressure at the associated consumer when the pressure compensator is completely turned on. This is when "sharing" at the highest load pressure leading consumer of the case, since the pressure compensator of this consumer associated flow control valve is fully open, while the pressure compensators of the other, lower-load consumers associated flow valves are moved to control positions to the output pressure after the orifices on to reduce the lower load pressure of these consumers.

in the Operating state "totalize" corresponds to the pressure in the addressed pressure medium flow path substantially that the lowest-load consumer, with its pressure balance at the beginning the control flows to the smallest amount of pressure medium and this open will or stays while through the pressure compensators of the other, higher-load consumers of the pressure in the pressure medium flow path is throttled until over the pressure compensator piston an equilibrium of forces established.

According to the invention switching between "divide" and "totalize" thus automatically, wherein the switching by tapping a pressure corresponding to the highest load pressure ("sharing") or a pressure corresponding to the lowest load pressure ("summing") in the pressure medium flow path between the open Pressure balance and the metering orifice takes place. At the flow valves of the higher-load or the lower-load consumer, the LS cross-section is controlled, so that the appropriate pressure compensators on a control surface in the closing direction with the highest load pressure corresponding pressure ("split") or in the opening direction with the pressure corresponding to the lowest load pressure ("summing") are applied.

at a particularly preferred solution the pressure compensator of the flow control valve is open in the basic position.

The The LS cross-section can be controlled by a 2/2-way valve with two LS control edges accomplished of which one is associated with the "sum" and the other with the "share".

at a particularly compact variant of the invention is the directional control valve integrated into a pressure compensator piston, wherein an inner piston of Directional valve in a pilot hole led the pressure compensator piston is and has a control collar, on whose two annular end faces the two aforementioned LS control edges are formed.

The Actuate of the inner piston (switching of the directional valve) is carried out by applying a face with the pump pressure and the other end face with the in the LS line adjacent LS-pressure. When "dividing" the inner piston is then due to the high pump pressure in a first switching position and the "summing" due to the low Pump pressure shifted to another switch position in which each one of said LS control edges is effective to aufzusteuern the LS cross-section.

at such a solution It is preferred if the LS line in a LS spring chamber of Pressure compensator opens, whereby by opening the LS cross section a connection between the spring chamber and a pressure corresponding to the load pressure leading Channel is made.

at an advantageous variant of the invention, the pressure compensator has a another spring chamber, which is connected to the LS spring chamber via a connecting channel is along the outer circumference of the Inner piston extends.

Of the Construction of the flow valve leaves further simplify when the inner piston beyond the LS spring chamber out extends and at this led out of the pressure compensator end portion a leadership alliance accomplished is that in a pressure chamber of a plug of the flow control valve guided is. In this pressure chamber, a stop for the inner piston is executed and he is further charged with the pump pressure.

to better leadership of the inner piston, this can be carried out with a radial collar, the along the inner peripheral portion of the guide bore of the pressure compensator piston is applied. These are either on the outer circumference of the Steuerbundes and the Radialbundes or along the inner peripheral surfaces of the guide bore Longitudinal scored executed, the a pressure medium flow between the two spring chambers enable.

Of the Pressure compensator piston is preferably provided with a middle control groove executed at their end faces the two control edges are executed. The pressure compensator piston is over two centering springs in its open Biased middle position.

To the Picking up the pressure in the pressure medium flow path between the pressure compensator and the metering orifice is the pressure compensator piston with one or more Radial drilling performed.

It is preferable to carry out the flow control valves each with a pressure feed valve, via which the consumers are secured against overload from the outside and further fed pressure medium If a lack of filling arises, so that cavitation phenomena are avoided and the system remains non-positive.

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 functional diagram of a flow divider in the "sharing"mode;

2 a sectional view of a flow control valve 1 ;

3 a detailed view of a pressure compensator of the flow control valve 2 ;

4 an inner piston of the pressure compensator 3 in different operating positions when "sharing";

5 the flow control valve of a lower-load consumer when "dividing";

6 the functional diagram according to 1 in the "sum"mode;

7 Positions of the inner piston according to 4 in summing up;

8th a sectional view of a flow control valve of a load lower consumer and

9 a circuit symbol of a flow control valve according to the invention.

in principle is the inventive concept in hydrostatically driven machines with closed or Can be used in open hydraulic circuit, with an application focus in Rotary drives, for example. Winding drives, belt drives or Travel drives is located.

In 1 is a functional diagram of a flow divider for a drive of a mobile implement shown. The control arrangement is designed as a closed circuit and has a variable displacement pump 2 , The traction drive has four hydraulic motors 4 . 6 . 8th . 10 coming from the pump 2 be supplied with pressure medium.

The distribution of pressure medium takes place in the illustrated embodiment via flow control valves 12 . 14 . 16 . 18 , each one of the consumer 4 . 6 . 8th . 10 assigned. The flow valves 12 . 14 . 16 . 18 are designed as valve segments and combined to form a control block.

As an example on the flow valve 12 shown, each valve segment has a housing plate 20 , at which a pressure connection P, a supply connection 5 , a working port A (B, C, D) and a LS port LS are formed. The load pressure connections LS of Steueranordung 1 are over an LS line 22 connected with each other. In the housing disc 20 are a variable or variable metering orifice 24 , a pressure balance 26 and a pressure feed valve 28 intended. In the direction of flow to the consumer 4 is the pressure balance 26 downstream of the metering orifice 24 arranged. As mentioned above, the pressure compensator 26 the pressure drop across the variable orifice 24 independent of load pressure, so that the pressure medium volume flows through the metering orifice 24 depend only on their opening cross-section.

About the pressure feed valve, the pressure at the working port A (B, C, D) is limited to a maximum value, so that the consumer 4 ( 6 . 8th . 10 ) is secured against overload. Furthermore, via the pressure feed valve 28 in a known manner in a lack of filling, for example, downhill or pulling load, via the feed port S and optionally via a pump 30 Pressure medium to be nachgefördert. It is sucked by this pressure medium from a tank T and a feed channel 34 to the respective supply connection S of the flow control valves 12 . 14 . 16 . 18 promoted.

The pressure connection P of the variable displacement pump 2 is via a branching pressure or supply line 36 connected to the pressure ports P of the valve segments. The respective working port A, B, C, D of the flow control valves 12 . 14 , 16 . 18 is via a supply line 38 . 40 . 42 . 44 with the pressure connections of the consumers 4 . 6 . 8th . 10 connected. The pressure medium flows from these via a common return line 40 to the suction connection R of the variable displacement pump 2 back. In 2 is the flow valve 12 out 1 shown enlarged. The other flow valves 14 . 16 . 18 have an identical structure.

The valve disc 20 is in the illustration according to 2 in the horizontal direction of a pressure balance well 42 interspersed, the front side of each a screw plug 44 . 46 is closed. In the pressure balance bore 24 is a pressure compensator piston 43 axially displaceable guided, the centering springs 50 . 52 is biased in a center position. The pressure balance bore 42 is in the middle area to two annuli 54 . 56 extended, between which a ring land 57 stop. The annulus 56 is connected to the working port A while in the annulus 54 one in 2 vertical measuring orifice bore 58 flows into the the metering orifice 24 is used. Their structural design is explained in detail in a separate application and plays no role in the present invention. It is only assumed that the metering orifice 24 designed with variable cross-section. However, the invention is not limited to such a construction.

In the meter hole 58 opens the pressure port P, which in the in 2 illustrated embodiment extends perpendicular to the plane. The meter hole 58 is down (view after 2 ) from a screw 60 locked.

In the annulus 56 further leads to an angle hole 62 , in the horizontally extending leg of which executed in cartridge design pressure feed valve 28 is screwed. The feed connection S opens via a in 2 perpendicular to the plane extending channel in a chamber 64 , which is a radial extension of the meter hole 58 is.

The pressure port P is via a sloping channel 66 with a ring channel 68 connected to the outer circumference of the screw plug 46 encircles annularly. In the screw plug 46 is a coaxial to the pressure balance hole 42 extending pressure chamber 70 formed, which via a connecting channel 72 with the ring channel 68 connected so that in the pressure room 70 always the pressure at the pressure port P, ie the pump pressure is applied.

The structure of the pressure compensator is based on the enlarged view in 3 explained.

Accordingly, the centering springs 50 . 52 of the pressure compensator piston 43 each on the adjacent locking screws 46 respectively. 44 supported and grab the pressure compensator piston 43 over cup-shaped spring plates 74 respectively. 76 and dive in sections in frontal images 78 . 80 of the pressure compensator piston 43 a, so that the pressure balance in the axial direction builds very short.

In the middle area of the pressure compensator piston 43 is circumferentially a circumferential cam 81 provided, the annular end faces form two control edges, with the ring land 57 interact. Here is the in 3 left control edge, in the following "split" control edge 82 called during the "divide" and the right, in the following "summing" control edge 84 called, during the "summing" effect. According to 2 stand the two control edges 82 . 84 in the illustrated basic position at a distance from the ring land 57 , so that the pressure fluid connection from the working port A (B, C, D) to the Meßblendenbohrung 58 and thus opened to the pressure port P.

The centering spring 52 is in a spring room 86 arranged, the front side of the pressure compensator piston 43 and from the screw plug 44 is limited. The other end portion of the pressure compensator piston 43 Limited together with the screw plug 46 a LS spring chamber 88 in which the load-signaling connection LS has a channel extending perpendicular to the plane of the drawing 90 empties. As a result, lies in the LS spring chamber 88 all flow valves 12 . 14 . 16 . 18 in each case the same pressure, which corresponds approximately to the highest load pressure when "sharing" and when summing about the lowest load pressure of the consumer.

According to 3 is the pressure compensator piston 43 in the axial direction of a guide bore 92 interspersed, in which an inner piston 94 is guided axially displaceable. This intersperses with its left end portion of the LS spring chamber 88 and has a leadership association there 96 with which he seals in the pressure room 70 the screw plug 46 is guided.

The other end portion extends into the spring chamber 86 into it and is in its illustrated end position on the screw plug 44 supported. When moving the inner piston 94 to the left, its left end section runs to the bottom of the pressure chamber 70 on, so that the end positions in each case by running on the locking screws 44 or 46 are limited.

Left of the rudder 81 is in the pressure compensator piston 43 at least one radial hole 98 executed, on the one hand in the guide bore 92 and on the other hand in the annulus 54 empties. In the area of these radial bores 98 is on the inner piston 94 a radially projecting control collar 100 educated. In the distance to the right of this is a radial collar 102 provided, over which the inner piston 94 in the guide hole 92 is guided. The to the frets 100 . 102 adjacent sections of the inner piston 43 are made with a smaller diameter and form with the inner peripheral surface of the guide bore 92 an annulus. As in 3 shown are the tax code 100 and the Radial Union 102 with longitudinal notches 104 . 106 executed, so that a control oil flow along said annular gaps and the longitudinal notches 104 . 106 between the spring chambers 86 . 88 is possible. Right from the radial bores 98 is the guide hole 92 radially to a section 105 extended, with the outer circumference of the tax code 100 forms an annular gap.

At the ring end faces of the tax code 100 are LS control edges 108 . 110 formed, wherein the control edge 110 at the flow control valve of the load pressurehöchsten consumer when "sharing" and "summing" the LS control edge 108 of the load-low consumer associated flow control valve is effective.

To further explain the function, it is first assumed that the control arrangement 1 is operated in the "split" operating state. According to 1 should the load pressure of the consumer 4-400 bar, the consumer at 6-300 bar, the consumer 8-200 bar and the consumer 10-100 bar, accordingly, a pump pressure is built up by pivoting the pump, which thus provides 410 bar (with a "10-bar Zumess spring"). This pump pressure (410 bar) lies above the canal 66 also in the pressure room 70 on, so that the left end face of the inner piston is loaded with the pump pressure, while on its right end face a lower pressure, as described below, the pressure in the pressure chamber 54 acts. Above the metering orifice 24 of the flow control valve 12 falls in the illustrated embodiment, a pressure of 10 bar, the pressure drop across the pressure compensator 26 is negligible in the middle position. The pressure at the outlet of the metering orifice 24 acts on the right end face of the inner piston 43 , This pressure corresponds in the open position of the pressure compensator 26 the highest load pressure, ie the one at the working port A. By the pressure difference (pump pressure minus maximum load pressure) is the inner piston 94 to the right into the in 3 moves shown position in which he with his right end of the screw plug 44 is applied. In this position, the LS control edge opens 110 of the tax association 100 a LS cross-section, over which the radial bores 98 with the spring chamber 88 are connected so that the pressure in the annulus 54 also in the spring room 88 is applied. This means that this pressure of 400 bar (highest load pressure) is transmitted via the LS line 22 also in the pressure chambers 88 the other flow valves reported. The inner pistons 94 the other, the lower-load consumers associated pressure compensators 26 are due to the high pump pressure also in the 3 shown end position are shifted to the right.

In 4 is for better understanding with the control edge 110 provided area of the inner piston 94 and the adjacent areas of the pressure balance piston 43 shown. 4b ) shows the above-described load message position of the pressure compensator 26 of the highest consumer 4 in which the highest load pressure (400 bar) in the LS line 22 is reported. As mentioned, controls in the middle position of the pressure compensator piston 43 and in the right end position of the inner piston 94 the control edge 110 of the tax association 100 a LS cross section 112 for load reporting, so that in the spring chamber 88 the corresponding load pressure, more precisely, the pressure at the outlet of the metering orifice 24 is applied. This is the above-described annular gap with the radially expanded section 105 and the longitudinal notch 106 also in the right spring room 86 reported so that the pressure compensator piston 43 of the flow control valve 12 pressure balanced on the front side and remains in its center position - the pressure balance 26 the load pressure highest consumer is thus completely open and does not throttle the pressure medium flow rate.

5 shows an example of a control position, the flow valves 14 . 16 . 18 the lower-load consumer 6 . 8th . 10 can be taken, which are connected to the appropriate working ports B, C and D. As described above, the inner piston is located 94 also with the flow valves 14 . 16 . 18 the lower-load consumer in its right end position on the screw plug 44 at. It is in the spring chambers 88 the flow valves 14 . 16 . 18 the signal of the pressure balance 26 of the flow control valve 12 reported, so in the spring chambers 88 also the highest load pressure of 400 bar is applied. At the beginning of the control, the pressure medium flows first to the consumers with the lowest hydraulic resistance - when sharing to the lower-load consumers. As a result, the pressure compensator pistons become 43 the flow valves 14 . 16 . 18 due to each in the LS spring chamber 88 acting highest load pressure from the center position against the force of the centering spring 52 moved to the right and corresponding by the "split" control edge 82 the flow cross-section between the pressure balance piston 43 and the Ringsteg 57 controlled, so that the pressure fluid flow is throttled. The pressure fluid flow is throttled until the balance of power is given to all pressure compensators and flow the amounts of pressure to the consumers. In the present example, this means that the pressure compensator of the last-lowest consumer closes relatively far, while the pressure compensators of the two higher-load consumers (200 bar, 300 bar) intermediate positions between the in 4a ) illustrated rest position and the in 5 take position shown with low flow cross-section. By shifting the pressure compensator piston 43 to the right opposite to the screw plug 44 adjacent inner piston 94 is according to 4 over the control edge 110 of the inner piston 94 and associated housing-fixed control edge 114 the LS cross section 112 controlled, so that the connection between the radial bores 98 and the LS spring space 88 is interrupted (see rest position 4a ). In his in 4c ) shown control positions is the tax code 100 about in the area where the bridge between the spring chamber 88 and the radial bores 98 is trained. The pressure at the outlet of the metering orifice 24 is then about the radial holes 98 from the section 105 the guide bore limited annular gap, the adjoining annular gap between the outer circumference of the inner piston 94 and the inner peripheral wall of the guide bore 92 as well as over the Längskerbe 106 of the Radial Union 102 in the spring chamber 86 reported so that the pressure compensator piston 43 to the left of the max load pressure and to the right of the pressure downstream of the orifice plate 24 is charged.

The small longitudinal notches 104 and 106 the inner piston and the annular space between the inner piston 94 and the guide bore additionally have the function that on this control oil flow path during a control movement of the pressure compensator piston 43 Control oil can be displaced from the decreasing spring chamber. A displacement of the control oil from the LS spring chamber 88 over the LS line 22 is not enough in this case, and is also not always fast enough, for example, when changing the load pressure extreme pressure compensator.

6 shows that 1 corresponding function diagram for the operating state "totalize".

It is believed that at the lowest pressure consumer 4 a load pressure of 35 bar is applied, while the load pressure of other consumers 50 . 100 respectively. 200 bar is. The at the input P of the variable displacement pump 2 to be summed pressure fluid flow rates have a pressure of 25 bar, while in the from port R to the consumers 4 . 6 . 8th . 10 leading return line 40 (Actually serves as a supply line) a pressure of 400 bar is applied.

Due to the low pressure in the supply line 36 (25 bar) is the inner piston 94 moved to the left by the higher pressure acting on his right end face until he with his left end face at the bottom of the pressure chamber 70 the screw plug 46 is applied. This switching takes place according to 6 at all flow valves 12 . 14 . 16 . 18 ,

At the beginning of the control, the pressure medium flows to the pressure compensators of the consumers with the lowest hydraulic resistance - when summing these are the higher-load consumers, so that their pressure compensators react first. The pressure balance 26 the lowest-load consumer 4 remains or moves to its middle position. The axial length of the tax code 100 is chosen so that by the displacement of the inner piston 94 opposite the pressure compensator piston 43 to the left now the right LS control edge 108 takes effect. This is in 7b ). In this Lastmeldestellung of the lowest load consumer associated pressure compensator 26 (Internal piston 94 shifted to the left, pressure compensator piston 43 in its middle position) controls the LS control edge 108 a LS cross section 112 on the housing side by a spring-side control edge 114 is limited. About the opened LS cross section 112 becomes the connection between the pressure room 54 and the LS spring space 88 open, leaving the lowest load pressure (35 bar) in the LS line 22 reported and thus in all LS spring chambers of the flow control valves 12 . 14 . 16 . 18 is applied. This lowest load pressure also acts on the right end face of the pressure compensator piston 43 of the flow control valve 12 so that it stays in its middle position. Due to the pressure medium flow to the other pressure compensators of higher-load consumers whose pressure compensator piston 43 , as in 8th shown, to the left in a control position (see also 7c )) postponed. In this control position is via the "totalize" control edge 84 the opening cross-section of the pressure compensators 26 the higher consumer 14 . 16 . 18 changed and the pressure fluid flow throttled until a balance of power is reached. The pressure medium can thus flow back load-independent from the consumers, wherein the pressure drop across the respective orifices 24 is kept constant. Depending on the load pressure on the load pressure higher consumers takes the pressure compensator piston 43 in its equilibrium position, a relative position with respect to the inner piston 94 one between a resting position ( 7a )) and the illustrated control position ( 7c )) lies. In the rest position according to 7a ) is the LS cross section through the control edges 108 . 114 zugesteuert, while in the illustrated control positions of the tax code 94 by axial displacement of the pressure balance piston 43 from the rest position to the left in the area of the bridge between the radial bores 98 and the LS spring space 88 lies.

In 9 is shown the circuit symbol of the flow control valves according to the invention. For example, the consumer 4 assigned valve segment is indicated by dash-dotted lines and has the ports P, S, A and LS. In the valve segment are the pressure feed valve 28 , the variable metering orifice 24 and the pressure balance 26 represented with the 2/2-way valve, which in the concrete solution by the pressure compensator piston 43 guided inner piston 94 is formed. As in 9 indicated, is this inner piston 94 mechanically with the pressure balance 26 connected. On the left end face of the inner piston 94 acts on the inclined channel 66 tapped pump pressure, while on the right end face of the over the radial bores 98 tapped pressure in the pressure medium flow path between the metering orifice 24 and the pressure balance 26 acts. When "dividing" the inner piston 94 against a housing-fixed stop, in the present case, the screw plug 44 moves, while "summing" is the inner piston 94 at the through the screw plug 46 stop formed.

In the open basic position of the pressure balance 26 is over the inner piston 94 and the appropriately switched 2/2-way valve, the pressure between the metering orifice 24 and the pressure balance 26 in the LS spring chamber 88 and thus into the LS line 22 reported and is therefore on all LS spring chambers 88 the flow valves. When moving the pressure compensator from the open position to a control position, the inner piston 94 moved by the mechanical coupling in one of the locking positions shown, so that the pressure in the pressure fluid flow path from the metering orifice 24 to the pressure balance 26 via the 2/2-way valve (inner piston 94 ) can not be tapped. The pressure in the LS line 22 also charges the in 9 right end face of the inner piston 94 ,

The pressure compensator piston 43 is on the one hand by the pressure in the LS channel 22 and on the other hand by the over the Längskerbe 106 tapped pressure between metering orifice 24 and the pressure balance 26 acted upon, wherein the pressure medium volume flow at equilibrium of forces by the pressure compensator 26 so throttled is that the pressure drop across the orifice plate 24 independent of load is constant.

As already mentioned, the pressure compensator reacts at the beginning of a control 26 as the first, which is assigned to the consumer with the lowest hydraulic resistance and thus receives the largest amount of pressure medium at the beginning. When "divide" this is the lowest pressure consumer associated pressure compensator, while the "summing" the pressure compensator reacts first, which is associated with the highest-load consumer.

Disclosed are a flow control valve and a flow divider for pressure medium supply several consumers. Each flow valve has a metering orifice and a Pressure compensator. A pressure compensator piston of the pressure compensator is equipped with two control edges one of which when "summing" of pressure medium flows and the other when "sharing" a pressure medium flow is effective. The flow control valve further has at least one LS control edge over which when open Pressure compensator a LS cross-section is controllable on the a pressure corresponding to the load pressure in a load reporting line is reported.

1

current divider

2

variable

4

hydraulic motor

6

hydraulic motor

8th

hydraulic motor

10

hydraulic motor

12

flow control valve

14

flow control valve

16

flow control valve

18

flow control valve

20

housing washer

22

LS line

24

metering orifice

26

pressure compensator

28

Druckeinspeiseventil

30

pump

32

feeding channel

34

feeder

36

supply line

38

supply line

40

Return line

42

Pressure compensator bore

43

Pressure regulator piston

44

Screw

46

Screw

50

centering

52

centering

54

annulus

56

annulus

57

ring land

58

Measuring orifice bore

60

screw

62

angle hole

64

chamber

66

oblique channel

68

annular channel

70

pressure chamber

72

connecting channel

74

spring plate

76

spring plate

78

admission

80

admission

81

control groove

82

Share control edge

84

Summing-control edge

86

spring chamber

88

LS spring chamber

90

channel

92

guide bore

94

internal piston

96

guide collar

98

radial bores

100

control collar

102

radial collar

104

longitudinal notch

105

radial extended section

106

longitudinal notch

108

LS control edge

110

LS control edge

112

LS-sectional

114

fixed to the housing control edge

116

spring-space side control edge

Claims (13)

Flow control valve for a flow divider for supplying pressure to several hydraulic consumers ( 4 . 6 . 8th . 10 ) with a pressure balance ( 26 ) and a metering orifice ( 24 ), which is used for power distribution towards the consumer ( 4 . 6 . 8th . 10 ) and for the summation of pressure medium flows in the opposite direction through which the pressure compensator ( 26 ) a biased in a basic position pressure compensator piston ( 43 ), on the one hand from the pressure in one LS line ( 22 ) and on the other hand by a pressure in the pressure medium flow path between the metering orifice ( 24 ) and the pressure balance ( 26 ) is acted upon, characterized in that the pressure compensator piston ( 43 ) two control edges ( 82 . 84 ) of which is effective in summing and the other in the sharing and that further at least one LS control edge ( 108 . 110 ) is present, with the open pressure compensator ( 26 ) for load reporting in the LS line ( 22 ) an LS cross section ( 112 ) is aufsteuerbar for tapping the pressure in the pressure medium flow path. Flow valve according to claim 1, wherein the pressure compensator ( 26 ) is open in the home position. Flow control valve according to claim 1 or 2, wherein an LS control edge ( 108 ) when summing and another LS control edge ( 110 ) is effective when sharing and these are formed by a 2/2-way valve. Flow control valve according to claim 3, wherein the 2/2-way valve by an inner piston ( 94 ) formed in a guide bore ( 92 ) of the pressure compensator piston ( 43 ) and a tax 100 ), on whose two annular end faces the two LS control edges ( 108 . 110 ) are arranged. Flow valve according to claim 4, wherein an end face of the inner piston ( 94 ) Can be acted upon by the pump pressure and the other end face with a pressure corresponding to the load pressure. Flow control valve according to claim 4 or 5, wherein the LS line ( 22 ) in a LS spring chamber ( 88 ) of the pressure balance ( 26 ) and via the LS control edges ( 108 . 110 ) of the taxation 100 ) the LS cross section ( 112 ) between the LS spring chamber ( 88 ) and a load-carrying channel ( 98 ) of the pressure compensator piston ( 43 ) is aufsteuerbar. Flow valve according to claim 6, wherein the LS spring chamber ( 88 ) over one between the inner piston ( 94 ) and the guide bore ( 92 ) extending connecting channel with a spring chamber ( 86 ), in which a radially recessed Innenkolbenendabschnitt dips and there against a stop ( 44 ) is movable. Flow control valve according to claim 7, wherein another end portion of the inner piston ( 94 ) the LS spring space ( 88 ) and with a leadership federation ( 96 ) in a pressure room ( 70 ) a locking screw ( 46 ) is guided, which is acted upon by the pump pressure and an axial stop for the inner piston ( 94 ) Has. Flow control valve according to claim 7 or 8, wherein the inner piston ( 94 ) a radial collar ( 102 ) for guiding the inner piston ( 94 ) in the guide bore ( 92 ) and at the Radialbund ( 98 ) and the tax 100 ) Longitudinal notches ( 104 . 106 ) and adjacent thereto areas of the inner piston ( 94 ) is performed with radial clearance to form a connection channel. Flow control valve according to one of the preceding claims, wherein the pressure balance piston ( 43 ) a middle control groove ( 81 ), at whose annular end faces the two control edges ( 82 . 84 ) are carried out and wherein the pressure compensator piston ( 43 ) via two centering springs ( 50 . 52 ) is biased in a middle position. Flow control valve according to claim 10, wherein the pressure balance piston ( 43 ) at least one radial bore ( 98 ), on the one hand in the field of taxation ( 100 ) in the guide bore ( 92 ) and on the other hand in a space carrying the load ( 54 ). Flow valve according to one of the preceding claims, with a pressure feed valve ( 28 ). Flow divider for pressure medium supply of several consumers, the several flow control valves ( 12 . 14 . 16 . 18 ) according to one of the preceding claims.