DE102008038338A1 - Valve arrangement and valve-controlled hydraulic machine - Google Patents

Abstract

Disclosed is a valve-controlled hydraulic machine and valve arrangement with a closing body for closing a pressure medium passage opening, wherein the closing body is adjustable via a first adjusting mechanism, so that the closing body performs an opening or closing stroke. A second adjusting mechanism of the closing body is adjusted so that it performs an additional stroke, wherein a total stroke of the closing body is greater or smaller than the stroke caused solely by the first adjusting mechanism.

Description

The The invention relates to a valve arrangement according to the Preamble of claim 1 and a valve-controlled hydraulic machine with such a valve arrangement.

Valve-controlled hydraulic machines and valve arrangements are for example from EP 1 537 333 B1 known. This document shows a hydraulic machine in axial or radial piston construction, which can be operated in principle as a motor or as a pump, wherein the delivery or absorption volume via the valve control is infinitely adjustable. In one described embodiment, the hydraulic machine is designed as an axial piston machine, wherein a plurality of piston arranged in a cylinder is supported on a rotatably mounted swash plate. Each piston defines with the associated cylinder chamber a working space which can be connected via an inlet valve and a drain valve with a pressure medium inlet or a pressure medium drain.

at The known solution, the two valves are electric openable or lockable non-return valves, which can be controlled via the pump control and the respective working space in "full mode", in the "partial mode "or in" idle mode "to operate. When "full mode" is essentially the entire Suction or delivery volume utilized, in the "partial Mode "only a part of the volume. In the "idle mode "is the delivery / intake volume of the respective Working space equals 0 - the machine is idling.

about a control unit is the hydraulic machine according to a control algorithm operated in order to minimize the pulsation sum flow volume (Pump) or total displacement (motor). The Volume flow adjustment often takes place after one Phase-angle control, but it can also be used after a phase-angle or phase cutout control.

at the solution described is in the feed to each workspace arranged inlet valve in the de-energized state by means of spring force closed. The check valve located in the drain is in the de-energized state by the spring force in the opening direction biased.

If the hydraulic machine is to be operated as a motor, is to drive a shaft connected to the swash plate, the drain valve Energizing an actuating magnet closed and simultaneously the inlet valve is opened. This allows pressure medium in pour in the working space, so that the hydraulic energy the pressure medium by the axial displacement of the respective piston and the corresponding rotational movement of the swash plate in a rotary motion the wave and thus converted into mechanical energy. Short before the inner dead center, in which the respective piston the full Has completed swallowing movement, the inlet valve is closed, so that by the remaining balance stroke of the piston to the dead center the working space is relieved of pressure. By this pressure relief can open the drain valve depressurized and the piston can be in its subsequent conveying movement swallow volume push out to the tank. Just before the outer dead center then the drain valve by energizing the corresponding actuating magnet closed. The remaining stroke of the piston to outer Dead center is then used to compress the trapped in the workspace Pressure medium used, so that the inflow valve on reaching the outer Totally depressurized open can. Through this process ensures that the check valves in the largely pressure-balanced state by relatively low Actuating magnetic forces can be switched. This control is necessary due to the required switching dynamics.

requirement for this type of control (DDP principle (digital displacement pump)) is that the low pressure and high pressure side valves can be switched with high dynamics, so that the above-described pressure medium flow paths very quickly shut off or can be released to flow through.

In the US 7,077,378 B2 a valve assembly for such a hydraulic machine is shown, in which an annular flow opening can be closed by a cup-shaped valve element. This annular flow opening is bounded by an inner and an outer sealing seat, so that the specific surface pressure at the sealing edge with respect to a valve cone is comparatively low. A disadvantage of this known solution is that due to the complex structure of the cup-shaped valve element and its guide and the valve housing designed with an annular flow opening of the device-technical complexity for the realization of the valve assembly is considerable.

One Another disadvantage of the known solution is that the flow resistance when flowing through the annular flow opening and the Flow around the cup-shaped valve element is relatively high, so that the efficiency of the hydraulic machine is comparatively low.

In contrast, the invention has the object, a valve assembly and a ven To provide tilgesteuerte hydromachine, in which the control modes described above with low device complexity and high dynamics can be realized.

These Task is achieved by a valve assembly having the features of claim 1 and a valve-controlled hydraulic machine with the features of Patent claim 18 solved.

According to the invention a valve arrangement a closing body for closing a pressure medium passage opening. The closing body is adjustable via a first adjusting mechanism, so that the closing body has an opening or closing stroke performs. About one second adjusting mechanism is the closing body adjustable so that it performs an additional stroke, bringing a total stroke of the closing body larger or smaller than alone by the first adjustment mechanism caused stroke is.

These Solution has the advantage that by the additional Hub the pressure medium passage opening is extended and thus flow resistance when flowing through the pressure medium passage opening to be reduced. Of Another is an extremely simple construction of Valve arrangement allows.

at a variant of the additional stroke of the first adjusting mechanism open closing body through in the opening direction acting on the closing body flow forces be effective.

at an advantageous embodiment of the invention, the closure body via the first adjusting mechanism in the opening direction of a first spring and in the closing direction of a magnetic force a lifting magnet acted upon.

Of the Closing body can via the second adjustment mechanism acted upon in the closing direction by a second spring be.

Of the Closing body is for example fixed with a out of a valve body and axially therein slidably mounted guide tappet connected.

In Another embodiment of the invention is the guide tappet in an axially slidably mounted on the valve housing Valve sleeve added. The valve sleeve can for adjusting the closing body over the first adjusting mechanism with a closing body assigning end face on the closing body and with one of the closing body repellent Face over a second spring on one with the guide ram connected support plate be supported.

expedient is at a closing body distal sleeve end area the valve sleeve a displaceable by the solenoid and arranged in approximately hollow cylindrical armature, the valve sleeve firmly engages with a first longitudinal section and with a second longitudinal section, the second spring and the backup plate of the guide tappet absorbs.

With Advantage, the first spring is supported on the valve housing from and over the armature and the valve sleeve the closing body in the opening direction in front.

The second spring is preferably associated with the second adjustment mechanism and clamps the closing body over the Bearing plate and the guide plunger in Closing direction before.

The opening stroke the first adjustment mechanism is for example by a a sleeve lateral surface of the valve sleeve trained stop ring limited, with the stop ring on a housing stop arranged on the valve housing is beatable.

at a further preferred embodiment of the invention the first spring is supported on the valve housing and spans over a first end face of a in approximately hollow cylindrical and sealed on both sides magnet armature this before, wherein by the armature of the guide tappet is passed approximately axially and a third spring itself is supported on a second end face of the magnet armature and one on the guide tappet axially slidable and attachable to a housing stop Attacking biasing ring, which has a driving projection on the guide tappet during a closing stroke away from the housing stop is displaceable. Through this solution is an extremely compact and simple design Valve arrangement allows.

Favorable Way, the second spring in the armature is supported on one pointing in the same direction as the first face first inner surface and biases one in the armature arranged and fixed to the guide tappet connected support plate, wherein the support plate in a non-executed additional stroke of the second adjustment mechanism opposite to one of the first inner surface second inner surface of the armature is supported.

In a simple embodiment, the closing body is displaceably guided axially on an end section, guided from a valve housing, of a guide plunger axially displaceably mounted in the valve housing. The end section of the Guide ram can be radially downgraded in the guide region of the closing body, whereby two annular surfaces are formed.

expedient It may be when the closing body at a not executed additional stroke of the second adjustment mechanism on the valve housing housing repellent first annular surface strikes with a stop surface and over the second spring is biased, located on the second annular surface supports and the closing body over one of the stop surface repellent support surface biases.

In supports further embodiment of the embodiment the first spring on the valve body and clamped one firmly connected to the guide tappet Magnetic anchor in front in the opening direction, with a fixed with the guide plunger connected stopper ring abuts against a housing stop.

With Advantage, a valve-controlled hydraulic machine has a valve arrangement, in which the second spring in one of the closing body arranged closable delivery chamber of the hydraulic machine is and on a trained in the delivery room support device supports and biases the closing body.

Preferably has a valve-controlled hydraulic machine as explained above Valve assembly.

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

in the Following are preferred embodiments of the invention explained in more detail with reference to schematic drawings. Show it:

1 a highly schematic representation for explaining the principle of operation of a valve-controlled hydraulic machine with variable displacement / delivery volume;

2a a first embodiment of an electrically actuated check valve of a hydraulic machine according to 1 in open position;

2 B the check valve off 2a in open position with an additional lift;

2c the check valve off 2a and 2 B in closed position;

3a A second embodiment of an electrically actuated check valve of a hydraulic machine according to 1 in open position;

3b the check valve off 3a in open position with an additional lift;

3c the check valve off 3a and 3b in closed position;

4 a third embodiment of a check valve in the closed position; and

5 A fourth embodiment of a check valve in the closed position.

The following is based on 1 the functional principle of a valve-controlled hydraulic machine 1 explained, whose delivery / displacement volume is digitally adjustable (DDP). The described hydraulic machine 1 is designed as an axial piston machine in a swash plate design, wherein 1 a very simplified processing of such a hydraulic machine 1 in axial piston design shows. In the following, only the components essential for understanding the invention will be explained. For more detailed information, reference is made to the above-mentioned prior art. In the following description is the hydromachine according to the invention 1 designed as a hydraulic motor, in principle, the versions of the hydraulic motor but also apply accordingly for a pump with adjustable delivery.

According to the schematic representation in 1 has the hydraulic machine 1 a cylinder 2 in which a variety of cylinder bores 4 are formed, in each of which a piston 6 is guided axially displaceable. Each of the pistons 6 limited with the cylinder bore 4 a workroom 8th whose volume depends on the stroke of the pistons 6 is dependent. The pistons 6 are each about a piston shoe 10 supported on an inclined swash plate, with an output shaft 12 connected is. In the illustration according to 1 is the cam formed due to the rotation of the swash plate 14 represented, which represents the rotation angle dependence of the piston stroke and thus the volume of the respective working space. As in 1 shown on the right, is every working space 8th via an inlet valve 16 with one all workspaces 8th common supply line 18 connected, which is subjected to a system or high pressure. This high pressure can for example via a pump 20 be generated.

Every working space 8th is also about a drain valve 22 with a likewise all working rooms 8th common drain line 24 connected in a tank 26 opens.

As already explained at the beginning, the drain valves are 22 and the inlet valves 16 each designed as electrically unlockable or lockable check valves. The inlet valve 16 is about one not shown spring biased in its illustrated basic position in a closed position and can be powered by energizing an actuating magnet 28 bring in an open position, so that the pressure medium from the supply line 18 in the respective workspace 8th can flow in. The drain valve 22 is biased in its illustrated basic position via a spring in an open position. By energizing an actuating magnet 30 can this drain valve 22 bring into a locked position in which the pressure medium is not from the work space 8th can flow out.

The control of the actuating magnet 28 . 30 via a control unit 34 , via which the modes described above (full mode, partial mode and idle mode) are adjustable, so that the displacement of the hydraulic machine 1 is infinitely adjustable, with suitable control of the valves 16 . 22 also the pulsation can be lowered to a minimum. In the illustrated embodiment, the control of the valves takes place 16 . 22 depending on the speed of the output shaft 12 that have a speed sensor 36 detected and via a signal line to the control unit 34 is reported. In principle, of course, other characteristics, such as that on the output shaft 12 acting torque or the displacement of the hydraulic machine 1 when controlling the valves 16 . 22 be taken into account.

2a shows the basic structure of a check valve according to a first embodiment, which in the hydraulic motor according to 1 corresponds to the drain valve. In a hydraulic pump is the valve 22 the inlet or suction valve 22 , which is assumed in the following figure descriptions.

The suction valve 22 has a through a first spring 38 in an open position biased valve element 40 , which by means of an actuating magnet 30 in the closed position against a valve seat 42 can move, so that an annular pressure medium passage opening or a flow cross-section 43 is closed off (see 2c ). The feather 38 is on a housing inner surface 44 a valve housing 46 supported.

The suction valve 22 is designed as a so-called "poppet valve", wherein the valve element 40 one the valve seat 42 passing through axial guide tappet 48 and a closing body attached thereto 50 Has. This closing body 50 is designed as a truncated cone, wherein on the lateral conical surfaces a circumferential, obliquely set sealing surface 52 is trained. The valve seat 42 is formed accordingly, so that a tight system in the closed state ( 2c ) is guaranteed. The guide tappet 48 is also in an approximately hollow cylindrical valve sleeve 54 slidably received axially. This is doing in the valve body 46 also axially slidably mounted and is located with a first closing body 50 facing end face 56 on the closing body 50 in about. At one of the closing body 50 facing away from the second end face 58 the valve sleeve 54 is a second spring 60 supported, wherein the second spring 60 a support plate 62 acted upon by spring force, on the closing body 50 remote end region of the guide tappet 48 is formed, whereby the closing body 50 over the guide tappet 48 and the backing pad 62 against the second end face 56 the valve sleeve 54 is biased. The valve sleeve 54 is in the illustrated embodiment of a hollow cylindrical armature 64 firmly gripped, with the spring force of the second spring 38 in the direction of in the 2a acted upon opening position shown. The magnet armature 64 encloses the valve sleeve with a first longitudinal section 54 and takes the second spring with a second longitudinal section 60 and the backing pad 62 of the guide tappet 48 on. The magnet armature 64 is sections of a magnetic coil 66 an actuating magnet or solenoid embraced in the valve housing 46 is included.

Adjacent to the magnet armature 64 is on the valve sleeve 54 a stop ring or a pole ring 68 made of magnetizable material. This sits in the spring-biased home position on a housing stop or permanent magnet 70 on, leaving the valve sleeve 54 and with this the valve element 40 by the force of the permanent magnet 70 and the bias of the first spring 38 is held in the open position. Pressure medium can thus via the annular flow area 43 in the workroom 8th out 1 flow.

2 B shows the suction valve 22 in a position where the closing body 50 performs an additional stroke, which is explained in more detail below. As a result of a suction process of the hydraulic pump pressure medium flows through the flow cross-section 43 , where flow forces on the closing body 50 act in the opening direction. Exceed the on the closing body 50 acting flow forces the spring force of the second spring 60 So this will be over the backing pad 62 , the guide tappet 48 and the closing body 50 cocked and the closing body 50 performs an additional stroke h. By this additional stroke h is the flow area 43 increased, wherein the flow resistance decreases and the working or delivery chamber 8th out 1 during the suction phase of the hydraulic pump is best filled. Be the on the closing body 50 acting flow forces less than the spring force of the second spring 60 , so will the closing body 50 over the guide tappet 48 and the backing pad 62 from the second spring 60 moved in the closing direction until the closing body 50 at the first end face 56 the valve sleeve 54 is applied.

As shown in 2c is used to close the flow cross-section 43 the magnetic coil 66 energized and the magnet armature 64 up in 2c moves, with the magnetic flux from the magnetic coil 66 over the adjacent housing walls, through the pole ring 68 through the valve sleeve 54 and the magnet armature 64 and then back over the adjacent housing walls back to the solenoid 66 he follows. This is the magnet armature 64 against the spring force of the first spring 38 and against the force of the permanent magnet 70 moved until the obliquely employed sealing surface 52 of the closing body 50 in sealing contact with the valve seat 42 has passed, so that the annular flow cross-section 43 is locked.

The spring force of the second spring 60 from the 2a -C is determined primarily by two opposing goals. On the one hand, the spring force should be as low as possible and, for example, smaller than one by the pressure fluid flow to the closing body 50 acting opening pressure of 0.3 bar, so that during the suction phase of the flow cross-section 43 is further opened by the additional stroke h at low flow forces, so that the delivery chamber 8th the hydraulic pump 1 out 1 during the suction phase best and quickly filled. On the other hand, the spring force of the second spring should 60 be as large as possible, so that the closing body 50 in the area of the bottom dead center of the piston 6 out 1 closes quickly to minimize backflow losses. Typical spring forces of the second spring 60 or opening pressures correspond to the size and speed of the hydraulic pump 1 out 1 an opening pressure between 0.3 and 1 bar.

Through the suction valve 22 from the 2a -C is the required stroke of the armature 64 for closing the flow cross-section 43 over the closing body 50 significantly reduced, since the additional stroke on the spring force of the second spring 60 is done. As a result, thus smaller magnetic currents and a lower magnetic force to close the suction valve 22 necessary.

The first spring 38 and the magnet armature 64 form a first adjustment mechanism and the second spring 60 and the flow forces in 2 B the pressure means a second adjusting mechanism.

By the additional stroke h in 2 B For example, a bypass valve to increase a flow cross-section is no longer necessary.

3a shows a second embodiment of the suction valve 22 that is considered essential to the difference 2a no valve sleeve 54 having. The magnet armature 64 is designed substantially hollow cylindrical and closed, wherein the guide tappet 48 is passed through this axially displaceable. The magnet armature 64 is doing over the first spring 38 , at its first, the closing body 50 opposite end face 72 attacks and over a third spring 74 at its second end face 76 engages, in an open position of the suction valve 22 held, with the first spring 38 on the valve body 46 and the third spring 74 on the on the guide tappet 48 axially displaceably mounted pole ring 68 supported. The magnet armature 64 further has two inner surfaces 78 . 80 on, wherein at the first the closing body 50 facing inner surface 78 the one with the guide tappet 48 connected support plates 62 with an additional stroke h not executed (compare with 3b ), which in this position by the second spring 60 that between this and the second, the closing body 50 opposite inner surface 80 of the magnet armature 64 is curious, is held.

3b shows the suction valve 22 according to the second embodiment, in an open position with the additional stroke h. By the on the closing body 50 acting flow forces, when the flow direction acting in the opening direction of the flow forces the spring force of the second spring 60 exceed, over the closing body 50 , the guide tappet 48 and the backing pad 62 the second spring 60 curious, whereby an additional stroke h takes place and the flow cross-section 43 is open further. The magnet armature 64 is about the third spring 74 held in an approximately constant position.

Once on the closing body 50 flow forces acting in the opening direction and the spring force of the second spring decrease 60 greater than the flow forces is, the backing pad 62 , the guide tappet 48 and the closing body 50 moved in the closing direction until the backing pad 62 on the first inner surface 78 of the magnet armature 64 approximately (see 3a ).

In the 3c will close the flow area 43 out 3b the magnetic coil 66 in accordance with the first embodiment in 2c energized. The magnet armature 64 moves in the closing direction and takes on the second inner surface 80 of the magnet armature 64 supporting second spring 60 , about these preloaded backing pads 62 and thus the guide tappet 48 and the closing body 50 with, until the closing body 50 with the sealing surface 52 at the valve seat 42 Approximately applied. During the movement of the guide tappet 48 in the closing direction is about one on this trained driving projection 82 the pole ring 68 carried. The driving advantage 82 lies with open suction valve 22 without additional stroke, see 3a , in about the pole ring 68 at.

4 shows a third embodiment of the suction valve 22 in the closed position, wherein the second adjusting mechanism with the second spring 60 outside the valve body 46 is arranged. The guide tappet 48 is in the valve body 46 guided and with the magnet armature 64 firmly connected, with the armature 64 as in the previous embodiments with a spring force of the first spring 38 is acted upon in the opening direction. Further, with the guide tappet 48 the pole ring 68 firmly connected.

A closing body guide plunger 85 , which has a reduced cross-section compared to the guide tappet 48 is outside the valve housing 46 substantially coaxial with the guide tappet 48 connected and points to his in the work space 8th out 1 arranged end portion of a support plate 86 on.

On the closing body guide tappet 85 is the approximately bell-shaped closing body 50 guided axially displaceable along its longitudinal axis. The closing body 50 is with an upper end face 88 with a non-executed additional stroke of the suction valve 22 easily from a ring surface 90 of the valve housing 46 spaced so that the closing body 50 not overdetermined and with the sealing surface 52 on the valve seat 42 in the closed state of the drain valve 22 is applied. The closing body 50 is here on the second spring 60 between the backing pad 86 the closing body guide plunger 85 and one of the backing pads 86 assigning inner surface 91 a cup-shaped spring receptacle 92 of the closing body 50 is tensioned, biased in the closing direction.

To open the suction valve 22 is the energization of the solenoid 66 interrupted, with the first spring 38 the guide tappet 48 over the magnet armature 64 moves in the opening direction until the pole ring 68 on the permanent magnet 70 Approximately applied. Exceeding in the open state of the suction valve 22 the flow forces the spring force of the second spring 60 so this gets over the inside surface 91 of the closing body 50 clamped in the opening direction and the closing body 50 performs an additional stroke.

The embodiment according to 4 offers a special advantage. The feather 60 Can be designed so that the closing body 50 on the one hand and the guide tappet 48 and the anchor 64 On the other hand, are mechanically decoupled and a damping effect is achieved by the spring. This allows the mechanical stress of the guide tappet 48 and the anchor 64 be kept low when closing the valve.

5 shows a schematic representation of a fourth embodiment of the suction valve 22 in a closed position with energized magnetic coil 66 , The second spring 60 the second adjustment mechanism is in the delivery room 8th the hydraulic machine 1 out 1 arranged and biases the closing body 50 in the direction of the guide tappet 48 and thus in the closing direction of the suction valve 22 before, with the second spring 60 at one in the pump room 8th trained support device 92 supported and a first the guide tappet 48 repellent face 94 the closing body 50 biases. With a second end face 96 lies the closing body 50 approximately at the guide tappet 48 and the valve seat 42 at.

In the illustration in 5 is the piston 6 indicated schematically and an open drain valve 98 of the promotion 8th shown. A closing body 100 the drain valve 98 is about a, for example, on a hydraulic machine housing 104 supporting valve spring 102 biased in the closing direction.

With a swallowing movement of the piston 6 in the 5 closes the drain valve 98 with the closing body 100 and the energization of the solenoid 66 of the suction valve 22 will be interrupted. The first spring 38 relaxes and moves the guide tappet 48 which in turn is the closing body 50 over the front edge 96 shifts in the opening direction. The second spring 60 clamps the closing body 50 in front. Flows pressure fluid through a flow cross-section, thereby exceeding the closing body 50 acting and acting in the opening direction flow forces the spring force of the closing body 50 biasing second spring 60 , this opens further to the additional stroke, the second spring 60 is stretched further.

Disclosed is a ventilgesteurte hydraulic machine and a valve assembly with a closing body for closing a Druckmitteldurchgangsöffnung, wherein the closing body via a first adjusting mechanism is adjustable, so that the closing body performs an opening or closing stroke. about a second adjusting mechanism is the closing body adjusted so that this performs an additional stroke, wherein a total stroke of the closing body larger or smaller than alone by the first adjustment mechanism caused stroke is.

1

hydromachine

2

cylinder

4

bore

6

piston

8th

working space

10

piston shoe

12

output shaft

14

cam

16

inlet valve

18

supply line

20

pump

22

drain valve

24

drain line

26

tank

28

actuating magnet

30

actuating magnet

34

control unit

36

Speed Sensor

38

feather

40

valve element

42

valve seat

43

Flow area

44

Housing inner surface

46

valve housing

48

guide tappet

50

closing body

52

sealing surface

54

valve sleeve

56

face

58

face

60

feather

62

backing pad

64

armature

66

solenoid

68

pole ring

70

permanent magnet

72

face

74

feather

76

face

78

palm

80

palm

82

driving projection

85

Closing body guide tappet

86

backing pad

88

face

90

ring surface

91

palm

92

support means

94

face

96

face

98

drain valve

100

closing body

102

valve spring

104

Hydro machine housing

H

Auxiliary

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• - EP 1537333 B1 [0002]
• US 7077378 B2 [0008]

Claims (19)

Valve arrangement with a closing body ( 50 ) for closing a pressure medium passage opening ( 43 ), which is adjustable via a first adjusting mechanism, so that the closing body ( 50 ) performs an opening or closing stroke, characterized by a second adjusting mechanism via which the closing body ( 50 ) is adjustable so that it performs an additional stroke (h), so that a total stroke of the closing body ( 50 ) is greater or smaller than the stroke caused solely by the first adjustment mechanism. Valve arrangement according to claim 1, wherein the additional stroke (h) by in the opening direction on the closing body ( 50 ) acting flow forces is effected. Valve arrangement according to claim 1 or 2, wherein the closing body ( 50 ) via the first adjusting mechanism in the opening direction of a first spring ( 38 ) and in the closing direction of a magnetic force of a solenoid can be acted upon. Valve arrangement according to one of claims 1 to 3, wherein the closing body ( 50 ) via the second adjusting mechanism in the closing direction of a second spring ( 60 ) and in the opening direction of the flow forces can be acted upon. Valve arrangement according to one of the preceding claims, wherein a valve housing (in 46 ) axially displaceably mounted guide tappets ( 48 ) with one from the valve housing ( 46 ) guided end portion with the closing body ( 50 ) is firmly connected. Valve arrangement according to claim 5, wherein the guide tappet ( 48 ) in a valve housing ( 46 ) axially slidably mounted valve sleeve ( 54 ) is recorded. Valve arrangement according to claim 6, wherein the valve sleeve ( 54 ) for adjusting the closing body ( 50 ) via the first adjusting mechanism with a closing body ( 50 ) assigning face ( 56 ) on the closing body ( 50 ) and with one of the closing body ( 50 ) repellent end face ( 58 ) over the second spring ( 60 ) at one with the guide tappet ( 48 ) ( 62 ) is supported. Valve arrangement according to claim 7, wherein at a closing body distal sleeve end region of the valve sleeve ( 54 ) a displaceable by the lifting magnet and in approximately hollow cylindrical magnet armature ( 64 ) the valve sleeve ( 54 ) firmly embraces with a first longitudinal section and with a second longitudinal section, the second spring ( 60 ) and the backing pad ( 62 ) of the guide tappet ( 48 ). Valve arrangement according to one of claims 8, wherein the first spring ( 38 ) on the valve housing ( 46 ) and via the magnet armature and the valve sleeve ( 54 ) the closing body ( 50 ) in the opening direction. Valve arrangement according to claim 9, wherein the second spring ( 60 ) is assigned to the second adjusting mechanism and the closing body ( 50 ) over the backing pad ( 62 ) and the guide tappet ( 48 ) in the closing direction. Valve arrangement according to one of claims 6 to 10, wherein the opening stroke of the first adjusting mechanism by a on a sleeve lateral surface of the valve sleeve ( 54 ) trained stop ring ( 68 ) is limited, wherein the stop ring ( 68 ) at one on the valve housing ( 46 ) arranged housing stop ( 70 ) strikes. Valve arrangement according to claim 5, wherein the first spring ( 38 ) on the valve housing ( 46 ) is supported and at a first end face ( 72 ) of an approximately hollow cylindrical and sealed on both sides magnet armature ( 64 ) and this biased, whereby by the magnet armature ( 64 ) of the guide tappet ( 48 ) is passed approximately axially, and a third spring ( 74 ) on a second end face ( 76 ) of the magnet armature ( 64 ) tensioning it and on one on the guide tappet ( 48 ) axially displaceable and on a housing stop ( 70 ) attachable stop ring ( 68 ) is supported, wherein the stop ring ( 68 ) on the guide tappet ( 48 ) take-off advantage ( 82 ) during a closing stroke away from the housing stop ( 70 ) is displaceable. Valve arrangement according to claim 12, wherein in the magnet armature ( 64 ) the second spring ( 60 ) at one in the same direction as the first end face ( 72 ) facing first inner surface ( 80 ) and one in the magnet armature ( 64 ) and fixed with the guide tappet ( 48 ) ( 62 ), wherein the support plate ( 62 ) at a non-executed additional stroke (h) of the second adjustment mechanism on one of the first inner surface ( 80 ) opposite inner surface ( 78 ) of the magnet armature ( 64 ) is supported. Valve arrangement according to claim 4, wherein the closing body ( 50 ) axially displaceable on one of a valve housing ( 46 ) guided end section ( 84 ) one in the valve housing ( 46 ) axially displaceably mounted guide tappet ( 48 ) is guided. Valve arrangement according to claim 14, wherein the end portion ( 84 ) of the guide tappet ( 48 ) in a management area ( 85 ) of the closing body ( 50 ) is radially stepped back and this is a support plate ( 62 ) and a ring surface ( 90 ) are formed. Valve arrangement according to claim 15, wherein the closing body ( 50 ) at a non-executed additional stroke (h) of the second adjusting mechanism on the closing body ( 50 ) repellent ring surface ( 90 ) with an end face ( 88 ) and via the second spring ( 60 ) is biased between the support plate ( 62 ) and one of the end face ( 88 ) repellent inner surface ( 91 ) of the closing body ( 50 ) is supported. Valve arrangement according to claim 16, wherein the first spring ( 60 ) on the valve housing ( 46 ) and one with the guide ram ( 48 ) fixedly connected armature ( 64 ) biased in the opening direction, one fixed to the guide tappet ( 48 ) connected stop ring ( 68 ) on a housing stop ( 70 ) is approximately present. Valve-controlled hydraulic machine with a valve arrangement according to one of claims 1 to 17. Valve-controlled hydraulic machine according to claim 18, as far as it is related to the claims 1 to 4, wherein the second spring ( 60 ) in one of the closing body ( 50 ) closable conveying space ( 8th ) of the hydraulic machine ( 1 ) is arranged and between the closing body ( 50 ) and one in the delivery room ( 8th ) trained support device ( 92 ) is supported.