EP1331393A2 - Solenoid pump with hydraulic transmission - Google Patents

Abstract

Hydraulic drive system has a cylinder bushing (40) connected to a dosing piston pump (3) directly on its housing. A hydraulic working piston (1) slides into the bushing forming a component body. Preferred Features: Oil pumped through the dosing piston pump is guided in a closed air-tight circulation. The circulation for the oil drives the working piston in a double-acting function. The movement of the working piston is controlled by the magnetic strength of a magnetic coil (7). Recoil of the working piston is regulated and/or blocked by controlling the oil volume stream using corresponding adjusting parts (11).

Description

The invention relates to a hydraulic drive system with a Schwingankerkolbenpumpe according to the preamble of patent claim 1.

In such oscillating armature piston pump engages around a magnet Pump housing and generates an axial magnetic field, which in the Sealing the pump housing, displaceably mounted pistons in one Workspace moves. The forward drive of the piston is performed by the applied magnetic field while the reset by a corresponding Return spring takes place, which acts on the piston.

With this known piston pump according to the Schwingankerprinzip results the advantage of a relatively small body, making this known pump For example, can be used as a fuel pump. However, it is not known that this pump is hydraulic Drive system is designed so that the pump, for example as Actuator interacts with a working piston.

By the same principle, by the way, DE 42 24 057 C2, which works as a metering pump with a suction piston effective, against the force of a Compression spring by exciting an electromagnet surrounding it centric movable anchor works.

Also in this known metering pump lacks the connection to a hydraulically driven working piston.

The invention is therefore based on the object, a complete propose hydraulic drive system with which it is possible on narrowest space to realize a hydraulic actuator.

To achieve the object, the invention is characterized in that that immediately after the metering piston pump to the housing sealing, axially directed a cylinder liner is connected in the one or a plurality of hydraulically movable working piston are displaceable.

Such a hydraulic actuator can in a wide Scope be used. An important area of application is e.g. the heating and air conditioning technology. Here, the inventive hydraulic drive system for raising and lowering of casements or Door panels, the pivoting of flaps, sliders and actuators be used. Likewise in the fluid technology in the control corresponding linearly adjustable actuators, such. B. flaps, slide and the like more for the control of water and Hydraulic fluids.

With the inventive compound known per se Vibrating piston pump with one or more hydraulic Power piston is now the main advantage that now a total of a very compact construction achieved with small volumes and high efficiency can be.

The pressure fluid generated by the metering piston pump is now directly and directly in the axial direction in the front flanged pump housing fed to a working cylinder and moves there one or more Working piston.

For the sake of simplicity of description, in the following description only from a single working piston, although one or more Working piston can be arranged in a pump housing.

So important is the crowded structure, because now according to the invention Pressure fluid directly in the axial direction of the Schwingankerkolbenpumpe is discharged and liquid-conducting in the Pump housing of the hydraulic drive system is fed. In order to There are several possibilities.

In a first embodiment, it is provided that the pump housing the vibration tank pump and the cylinder housing of the working cylinder form the only continuous part.

In a second embodiment of the invention, it is provided that the two parts are modularly separated from each other. This gives the advantage that one on the existing housing of the pump system any Cylinder housing of a drive cylinder modular can put on. In order to can use different working cylinder with the pump housing of the Vibrating anchor system are connected.

This also allows different demands on the forces in the hydraulic drive system and to meet the lifting requirements.

Another essential advantage results from the fact that according to the invention is also provided that the magnetic coil easily replaceable on Outer circumference of the pump housing is arranged. That's the way it is now simply possible, different drive power for the Transfer pump piston.

The hydraulic drive is based on the principle of a single-acting Piston pump. He also has an additional Rückströmsystem for the Reverse running of the working piston, which acts against a return spring.

In the following description of the invention, various Embodiments described as essential to the invention.

In a first embodiment, a backflow system is described, which between the pump piston of the pump system and the Working piston of the hydraulic drive system is arranged. This is at the same time a specific valve control as essential to the invention claimed.

In a second embodiment, with a second coil instead of a mechanically moving valve described a magnetically moving valve, which essentially consists of a magnetically movable control piston consists.

In the third embodiment, a magnetically movable spool described.

Variante Schiebekolben

Das Kolbenteil ist als Schiebekolben in Funktion eines Wegeventils ausführbar. Dabei können die Kanäle in Förder- und Rückströmrichtung vertauscht werden, so dass der Arbeitskolben hydraulisch doppelwirkend betätigt werden kann.

Below some variants of the invention are described in short form:

Variant sliding piston

The piston part is executable as a sliding piston in function of a directional control valve. In this case, the channels can be reversed in the conveying and return flow, so that the working piston can be hydraulically operated double acting.

Variant as a pure feed pump

The presented here linear drive can be used separately as a feed pump become.

Flow rate and pressure variation

One of the possible variants and advantage of the system is through different dimensions of the armature piston flow rate and pressure too vary. The design allows a very easy replacement of the Magnetic coil body without interfering with the closed drive part. By the use of different coils can be adapted electrical voltage and Performance requirements to the drive can be achieved.

Design variation of working piston

A variety of variants of the cylinder and working piston part in theirs Dimension allows forces and speeds according to the To adapt requirements.

Modular structure of the overall system

The entire system can be modular. Both pump part as Working cylinder parts are self-contained units and can be used in the Modular system be interconnected.

The scope extends to all applications where a linear Movement is required and any lifting and power requirements are covered shall be.

Additions:

The suction chamber may include an expansion element (spring-loaded piston, Membrane etc.), which applies a constant static pressure and thus on the one hand prevents harmful air formation in the suction and on the other hand takes into account the expansion behavior.

The subject invention of the present invention is not only evident the subject matter of the individual claims, but also from the Combination of the individual claims among themselves.

All disclosed in the documents, including the abstract Information and features, in particular those shown in the drawings Spatial training, are claimed as essential to the invention, as far as they are individually or in combination with the prior art are new.

In the following, the invention will be described with reference to only one embodiment illustrative drawings explained in more detail. Here are the Drawings and their description further features essential to the invention and advantages of the invention.

Figur 1:

Schnitt durch eine erste Ausführungsform eines hydraulischen Antriebssystems,

Figur 2:

Stirnansicht auf die Anordnung nach Figur 1,

Figur 3:

ein Teilschnitt aus der Anordnung der Figur 1 mit einer Abwandlung bei der Überleitung des Druckölstroms in das Antriebssystem,

Figur 4:

eine weitere Variante gegenüber Figur 3 mit einem magnetisch bewegbaren Steuerschieber.

Figur 5:

eine weitere Variante gegenüber Figur 3 mit einem magnetisch bewegbaren Steuerschieber und abgeänderten Pumpenkolben.

Show it:

FIG. 1:

Section through a first embodiment of a hydraulic drive system,

FIG. 2:

End view of the arrangement of Figure 1,

FIG. 3:

a partial section of the arrangement of Figure 1 with a modification in the transfer of the pressure oil flow in the drive system,

FIG. 4:

a further variant with respect to Figure 3 with a magnetically movable spool.

FIG. 5:

a further variant with respect to Figure 3 with a magnetically movable spool and modified pump piston.

In Figure 1, a Schwingankerkolbenpumpe is generally shown, whose Pump housing is referred to as a tubular body 3. The magnetic drive takes place via a magnetic coil 7, which is radially on the outer circumference of the Tube body 3 is arranged. The tubular body is about in the middle of the Solenoid 7 interrupted by a nonmagnetic middle part 8.

On one side of the tubular body 3 is a spring-loaded inlet valve. 4 arranged, which arranged from one at the rear end side Suction chamber 19 sucks the pressure oil.

The suction chamber 19 consists essentially of a locking ring 51, the formed inside the suction chamber 19, wherein the bias of the pressure oil in the suction chamber 19, a displaceable pressure piston 52 is arranged, the is displaced under the force of a spring 53 against the suction 19. On This way is always ensured that the pressure oil from the suction 19 is biased in the direction of arrow 66 and an associated Inlet bore 29 flows to the inlet valve 4.

The inlet valve and an associated transverse bore 25 are in this case rest stored in a fixed bearing part 17 in the tubular body 3. That about the Inlet valve 4 incoming pressure oil flows into the working space 18 behind the Piston 6 a. This piston essentially consists of a front Piston head and a firmly attached thereto piston rod 27, which at her the rear end carries a transverse bore, which in the marked position with a housing-fixed transverse bore 25 in the bearing part 17 is aligned.

The piston head of the piston 6 is by means of a return spring 9 in the biased rest position and counteracts in the working position a housing-fixed stop 31, the part of a likewise fixed to the housing Bearing parts 30 is.

With appropriate magnetic loading of the solenoid 7 is Therefore, the piston 6 in the indicated arrow direction 67 in the piston chamber 20 moves into it and compresses the pressure oil located there against a Pressure valve 5, which is opened accordingly.

The pressure oil enters the valve bore 33 of the pressure valve 5, overcomes the Valve spring and reaches the rear of a piston 11, as Control piston is used.

It is important that the control piston 11 radially outward a liquid-conducting gap 22 forms, so that the pressure oil through this gap 22nd axially forward in the arranged in front of the piston 11 piston chamber 21st flows.

The piston 11 is in this case by a return spring 15 in its closed position held and with appropriate admission with a Pressure surge in the axial direction forward against the force of the return spring 15 moves.

This piston 11 is firmly connected as a unit with a pipe section 12, which engages in an associated guide bore 68.

Furthermore, the piston 11 carries on its front side an axially forward directed approach with a return flow 13, which has a counterbore 23rd assigned in the tubular body 3.

The piston 11 together with the front-side front projection and the rear pipe section 12 is completely penetrated by an axial bore.

Upon impact of a pressure surge from the pressure valve 5 on the back of the Piston 11 is thus axially to the left against the force of the return spring 15 moves and the front, frontal approach with the axial Through hole so that it dips sealingly into the housing Counterbore 23 and is sealed there.

Thus, no return flow in the suction via the axial Channel and the adjoining transverse bore 32 and 25, and 26 respectively.

Rather, the pressure oil flows through the transverse bore 69 in the connector 34 in the cylinder liner 40 of the hydraulic drive system into it.

The pressure oil is from the connecting piece 34 in the direction of arrow 43 in the promoted rear cylinder space 43 and acts there on the back of the Piston part 41 which is sealingly guided in the cylinder chamber 39.

Thus, the entire working piston 1 in the direction of arrow 70 to the outside moves and acts on a non-illustrated return spring. 2

From the cylinder chamber 39, the displaced pressure oil on the transverse bore 71 promoted in the longitudinal channel 38 and flows there in the direction of arrow 44 back in Pump housing 40.

About the connector 37, the returning pressure oil enters the Return flow channel 36 in the tubular body 3 of the pump housing back and flows directly into the suction 19th

In addition to the above-mentioned large return flow there is still the small Return flow, which consists essentially of the transverse bore 32 and the adjoining return flow channel 24 in the pump housing of the pump results.

Namely, when stopped piston pump, the working piston 1 in The opposite direction to the arrow 70 runs back, this must be in the work area 42 located pressure oil in the opposite direction to the arrow 43 over the local there Channel and the connector 34 flow back into the plenum 19. This is achieved in that this pressure oil now on the transverse bore 69 flows into the front piston chamber 21, there in the front of the Return flow opening 13 on the piston 11 enters the piston in the axial direction flows through and enters the transverse bore 32 at the rear.

From there, the oil flows via said return flow channel 24 into the Storage room back. However, this is still another valve control provided that allows a backflow only if, on the one hand, the piston 11 is located in the marked rest position and on the other hand, the Piston 6 is also in the rest position.

For this case, namely the housing-fixed transverse bore 25 connects the in movable piston 6 arranged piston rod 27, so that the oil over the arranged in the piston rod 27 transverse bore in the housing fixed Longitudinal bore 26 enters and flows from there into the storage room 19.

This would be the case even if the piston 11 with the arranged therein Pipe 12 on the working side no device for regulating the blocking time would have for the reflux of the oil via this return path. In In this case, the oil reflux would be during the bottom dead center of the piston 6 or its piston rod 27 so large that at least part of the straight subsidized oil would flow back through this path, and thus counterproductive for the feed of the working piston would act. This results itself from the vibration system consisting of the mass of the piston 6 with its individual parts, the spring force of the return spring 9 and the Magnetic force of the solenoid 7, which performs the driving work.

To prevent this, a device is provided according to the invention a certain, by appropriate dimensioning of the parameters involved, Spring force and effective flow of oil, adjustable dead time for the Release of the return line provides. This can, taking into account static and dynamic characteristics of the system, whether or not at all, and when, how much oil will flow back through the return lines can. It is preferably provided that no oil during the lower Dead center of the piston 6 flows through the transverse bore 25, since this yes Feed of the working cylinder 1 would affect. This would be for Swinging be excited. However, if a vibration behavior desired Of course, the reflux can of course be regulated so that the Working piston 1 at least one superimposed vibration in his Drive movement experiences.

The regulation of this dead time is now in the present invention in one preferred embodiment by the embodiment of the piston 11 with the associated components and functions realized.

To in the return line of the oil to a corresponding dead time control realize an actuator has been developed according to the invention, which in the form a piston 11 is formed with a valve function. A big part of the pro Working stroke of the pump piston 6 to be pumped oils is characterized by in the Piston 11 arranged through hole 12 (pipe section) conveyed through, that due to the effective cross-section, the oil through the here significantly lower resistance to the gap 22 towards the working piston 1 searches. Only when the piston 11 with its return flow 13 in the Counterbore 23 is immersed, if necessary, still oil through the gap 22nd further into the space 21 and from there into the connecting piece 34 towards the Working piston flow.

The main conduit for the reflux, the pipe section 12, so ineffective. About this connection can flow as long as no oil until the Return flow opening 13 is released again. This release can now by the influence of the relevant parameters are regulated. Thus, can be set exactly when the pipe section 12 again oil-tight is switched.

In addition, by appropriate parameterization and the Displacement of the individual pistons 6, 11, 1 are influenced, so that these For example, do not perform the full stroke, and thus also not at the corresponding end faces with the assigned surfaces collide. As a result, an enormous noise reduction is possible, so far that the entire hydraulic drive system almost noiselessly works.

In general, it is stated that the control of the dead time for the Backflow of the oil not necessarily by a so-called Control piston / cylinder, as here the piston 11 must be done. There are also given different other possibilities. So z. B. in one another embodiment of the control cylinder 57 described in the figure 4, the also works in this #weise. The embodiment in FIG. 3 shows a magnetically actuated control piston 56, which also performs this function. Further, corresponding embodiments are thus within the scope of Invention.

It should be noted that to the piston 6 at all to move magnetically, this on the outer circumference with a Magnetic ring 28 is provided with the magnetic field of the magnetic coil. 7 interacts.

The magnet ring 28 can be used together with the piston head and the piston rod also form a unitary body.

There is another operating case where it is intended that the piston 6 against the force of the spring 9 in its shifted to the left position remains when it is accordingly acted upon by the magnetic coil 7. In order to avoid a backflow for this operating case, it is intended that then the transverse bore in the piston rod 27 is no longer with the housing-fixed transverse bore 25 in the bearing part 17 is aligned, and thus is the Backflow blocked off.

In the drawing, only indicated that the front, hydraulic Drive system 35 with the working piston 1 via the said Connectors 37 and 34 releasably connected to the tubular body 3 of the Pump housing is connectable. However, the invention is not limited. It can also be provided that the front, hydraulic Drive system 35 fixed and insoluble with the tubular body 3 of the behind connected subsequent pumping system.

However, the modular structure (pluggability) of the two parts is preferred, because it is a simple replacement of the front drive system 35th allows. This allows different working piston 1 with different strokes are used.

The connection of the two parts takes place otherwise by a on the front side the cylinder liner 40 attached screw 49, which in an associated Threaded sleeve 50 can be screwed onto the pump housing of the tubular body 3.

The front working piston 1 is otherwise fixed with a piston neck 45th connected, which is sealingly guided in the cylinder liner 40.

The piston shoulder 45 forms a neck of reduced diameter, by a vent hole 46 is provided. This vent hole flows into the atmosphere. The stop reduced diameter acts with a housing-fixed stop 47 in the cylinder liner 40 together. The working piston 1 is otherwise sealing in a frontal Guide member 48 of the cylinder bush 40 slidably guided in the longitudinal direction.

It is important that in the inventive pump when sucking always a constant volume exists because by the bias with a Plunger 52 of the suction chamber 19 and the hydraulic oil located there always is held under a certain bias. There is no moving volume, and the oil will not come from a free tank removed, but kept under lock.

Regardless of this constant volume in the suction 19, which is held under spring preload, the working piston can be. 1 move according to the mode of operation of the metering piston pump and displace different liquids.

FIG. 2 generally shows the end view of the arrangement, where it can be seen that that the magnetic coil 7 centrally forms a Innenbohrugn 54, over the Tube body 3 of the pump system is pushed.

FIGS. 3 and 4 now show modifications of the control valve system Figure 1. Here is shown how the piston 11 shown in Figure 1 by other controls can be replaced.

FIG. 3 shows a magnetically driven control piston 56 which is acted upon by its own magnetic coil 55. Here is in the Pump housing in turn arranged a magnetic separation 65 to to avoid a short circuit of the magnetic field.

Accordingly, the control of the solenoid 55 so that the control piston 56 is moved in the axial direction against the force of the return spring 15 back and forth.
The control piston 56 then abuts against a housing-fixed end face 14.

For the sake of clarity is still another variant of the Return control the already described in Figure 1 pipe section 12th represented with the axial through hole, which sealing - depending on Displacement position of the control piston 56 - in an associated blind bore 23rd immersed in the housing-fixed part and thus the axial through hole closes.

Alternatively, however, an axial through hole 72 in the control piston 56 is provided, associated with an associated, spring-loaded valve 73 is.

This valve opens into a through hole 74 and this in turn the front piston chamber 20 of the pump.

Now calls for the piston of the pump not shown in detail pressure oil Arrow direction to the left, this pressure oil passes through the through hole 74th overcoming the valve 73 through the through hole 72 in Control piston 56 through and passes through the connecting pin 34 in the Drive system 35.

At the same time the return flow is closed with the pipe section 12, because the front, front end dips into the blind bore 23.

In the rest position of the control piston 56, the reverse case applies. The valve 73 is closed, and there is a backflow over the Connector 34 and the now open axial bore in the pipe section 12 and the transverse bore 32 in the suction 19th

The valve holes complement each other in the transverse bores 25 in housing-fixed bearing part 18 and the associated transverse bore in the Piston rod 27 is then no longer necessary.

FIG. 4 shows a further variant of a corresponding piston control, also using a magnetically movable spool 57, which is driven by a magnetic coil 55.

In front of the piston chamber 20, the bearing part 30 is arranged, which is the Valve bore 33, through which the non-illustrated Piston generated pressure oil in the direction of arrow overcomes the pressure valve 5.

This pressure oil first enters the working space 75 in front of the spool 57 a, wherein the spool by means of a return spring 58 in its left Stop side is held.

If, however, the spool 57 is activated by the solenoid, then He takes his first control position. In this position flows in the Working chamber 55 located pressure oil through the center channel 59 and a associated transverse bore in an adjoining housing fixed Cross hole 76 a, from where the pressure oil in the direction of arrow 77 in the Drive system 35 flows into it.

In this way, the pressure oil is fed into the drive system 35.

The return flow of the oil from the drive system via the Connector 37, which via transverse bores with the return flow 36 is connected. This is again fluid-conducting with a Cross channel 60 connected, which is fixed to the housing. This case-fixed Transverse channel 60 is a corresponding - arranged in the spool 57 - Cross hole 61 opposite, so that in the activated position of the Control spool 57, a return flow through the transverse bore 61 in the Spool 57 takes place in and over the centrally disposed transverse channel 62 in the spool 57 in a fixed housing in the pump housing arranged longitudinal channel 78 flows back into the suction chamber 19.

Advantage of this embodiment is that in the embodiment in conjunction can be omitted with the piston rod 27 described valve control and the entire control of reflux already in the area of Spool 57 takes place.

Incidentally, this is also the advantage of the exemplary embodiment according to FIG. 3.

The other displacement position of the spool 57 allows a Comparison of the housing-fixed transverse bore 64 to an associated, arranged in the spool, transverse bore 63rd

So if the spool 57 in its left stop position is located so that the transverse bore 64 comes in accordance with the Transverse channel 63 and the pressure oil flows in the axial direction to the left (Arrow 79), wherein the working piston 1 a backward movement performs.

Depending on the position of the spool 57 thus the working piston 1 can its front or back are supplied with pressurized oil.

It is also added to the embodiment of Figure 1, that arranged in the pipe section 12 of the piston 11 bore as Guide bore 68 is designated.

With the integrated pump and working piston system in a pipe section is a simple space-saving and therefore inexpensive drive system been created. The easy interchangeability of the solenoid allows to quickly meet other performance specifications.

FIG. 5 shows a further variant of the present invention which compared to the embodiment in Figure 3 with a magnetically movable Spool and modified pump piston is equipped.

In this embodiment with spool 57 is the anchor part with Kolben27 in contrast to the above-mentioned embodiments in the suction 19 and promotes the oil on the inlet valve 4 in the Pressure chamber 20 and from there via the Druckvenitl 5 via the spool 57th in a working cylinder. The special feature of this embodiment is that while the pressure chamber 20, the inlet valve 4, the pressure valve 5 and the Reflux channel 24 can be integrated in a component, and thus consuming return flow channels in the tubular body 3 can be omitted.

In summary, it is stated that the system in a first Embodiment has four pistons, which for the oil guide and To blame power transmission. These are the piston 52, for the permanent pressurization on the system is responsible, and so on ensures that the closed oil system works almost air entrapment, the piston 6, which is responsible for the compression and transport of the oil, the piston 11, which is responsible for controlling the flow of oil, and Finally, the working piston 1 with its effective piston part 41 for the to be generated, effective linear motion.

Due to the fact that the entire system in each embodiment is designed as a closed oil system, consists in the present Technical teaching the advantage that virtually no blistering and thus inevitably prevents problems caused by air pockets in the oil become. Thus, the system structure prevents as a double-acting Working cylinder 1 the usual way occurring problems due to air entrapment for example in the form of blistering caused by free flow of the Returning oil in the tank or suction of the system. Thus results the advantage that the system has a permanent frictional connection, whereby a continuous linear movement of the working piston is ensured and not by air bubbles fluctuations in the delivery volume which cause abrupt movement states.

It is made possible by the technical teaching of the present invention also a targeted, adjustable in their speed provision of the Working piston. The adjustment takes place by means of dimensioning of Line cross-section of the oil. By influencing the cross section is regulated according to the return flow, resulting in Finally, the return speed can be influenced.

The training as a double-acting cylinder is done by means of two correspondingly controllable oil ducts in the pipe formed as System. This means that the piston part 41 of the working piston 1 on both Sides of oil is lapped. The oil in the front / outer part of the cylinder 39 is caused by the outward movement of the piston member 41 through the Cross hole 71 pressed into the return system and so immediately again fed to the suction chamber 19, whereby the oil circulation air-free closed is. When returning the working piston 1, the oil flow takes place in reverse direction. However, according to the technical teaching, the Possibility to control the volume flow by the return speed in desired way to influence.

An influence on the feed of the working piston 1 is after the technical teaching of the present invention also provided. These can by adjusting the magnetic coil force on the oil promotional piston 6 done. The control takes place in such a way that the maximum feed rate at 100% delivery stroke, and one Reduction of the delivery stroke to less than 100% Accordingly, also has a reduced feed movement result, which due to the known connections and their speed reduced.

The reduction of the delivery stroke takes place through the use of a correspondingly weaker selected magnetic coil 7, which the piston. 6 only able to move more along its maximum working distance.

The already extensively described control of the oil flow can now in various embodiments of the present invention done in different ways. Once, as just mentioned again, by means of the piston 11 controlled by the oil pressure itself Cooperation with the corresponding valves, inlet 4 and outlet 5, which are designed here as check valves. In addition, the effect Return spring 15 and position of the oil-promoting piston 6 on this, so that only by influencing the position of the piston 6 the Resetting speed can be controlled.

However, the control of the piston can also by means of spring force and / or Magnetic force done.

Once again, the control by means of a two-way valve, here as Control slide 57 denotes, and the check valves 4, 5 performed. This spool causes the oil supply for feed, lock and Return of the working piston 1. The spool can by means of oil pressure and / or spring force and / or magnetic force are actuated to the to exercise the desired control function.

drawing Legend

1

working piston

2

Return spring

3

Tubular body (pump)

4

intake valve

5

pressure valve

6

piston

7

solenoid

8th

midsection

9

Return spring

10

pipe section

11

piston

12

pipe section

13

return flow

14

face

15

Return spring

16 17

bearing part

18

working space

19

suction

20

Piston chamber (front)

21

Piston chamber (rear)

22

Gap (piston 11)

23

counterbore

24

backflow

25

transverse hole

26

longitudinal bore

27

piston rod

28

magnetic ring

29

inlet bore

30

bearing part

31

Stop (bearing part 30)

32

transverse hole

33

valve bore

34

joint

35

drive system

36

backflow

37

joint

38

longitudinal channel

39

cylinder space

40

cylinder liner

41

piston part

42

cylinder space

43

arrow

44

arrow

45

piston extension

46

vent hole

47

attack

48

guide part

49

screw

50

threaded bushing

51

lock ring

52

pressure piston

53

feather

54

internal bore

55

solenoid

56

spool

57

spool

58

Return spring

59

center channel

60

Querkanal

61

transverse hole

62

Querkanal

63

Querkanal

64

transverse hole

65

magn. separation

66

arrow

67

arrow

68

guide bore

69

transverse hole

70

arrow

71

transverse hole

72

Through Hole

73

Valve

74

Through Hole

75

working space

76

transverse hole

77

arrow

78

longitudinal channel

79

arrow

Claims (14)

Hydraulic drive system with Schwingankerkolbenpumpe with magnetic drive, characterized in that following a Dosierkolbenpumpe (3) to the housing directly sealingly, axially directed a cylinder liner (40) is connected, in which at least one hydraulically movable working piston (1) is displaceable, so that together they form a continuous component body. Hydraulic drive system according to claim 1, characterized in that the oil pumped by the metering piston pump (3) is guided in a closed, air-free circuit. Hydraulic drive system according to one of claims 1 or 2, characterized in that the circuit for the oil drives the working piston (1) in a doppelwikenden function. Hydraulic drive system according to one of claims 1 to 3, characterized in that the feed of the working piston (1) on the basis of the magnetic strength of the magnetic coil (7) can be controlled. Hydraulic drive system according to one of Claims 1 to 4, characterized in that the return of the working piston (1) can be regulated and / or blocked by the control of the oil volume flow by means of corresponding actuators (11; 56; 57). Hydraulic drive system according to one of claims 1 to 5, characterized in that the actuator (11; 56; 57) is actuated by means of magnet and / or oil pressure and / or spring force. Hydraulic drive system according to one of claims 1 to 6, characterized in that the stroke of each conveying or control element (6; 11; 56; 57) can be adjusted in the system by appropriate parameterization of the effective components so that it does not face the front side associated component abuts. Hydraulic drive system according to one of claims 1 to 7, characterized in that for biasing the pressure oil in the suction chamber (19) a displaceable pressure piston (52) is arranged, which is displaced under the force of a spring (53) against the suction space (19) , Hydraulic drive system according to one of claims 1 to 8, characterized in that the supply and return lines for the oil are guided in part in the walls of the tubular body (3) and the Arbreitszylinders (40). Hydraulic drive system according to one of claims 1 to 9, characterized in that the pressure fluid is discharged directly in the axial direction of the Schwingankerkolbenpumpe (3) and liquid-conducting in the pump housing (40) of the hydraulic drive system is fed. Hydraulic drive system according to one of claims 1 to 10, characterized in that the Schwingankerkolbenpumpe is modular. Hydraulic drive system according to one of claims 1 to 11, characterized in that on the housing of the pump system (3) an arbitrary cylinder housing (40) of a drive cylinder can be placed modular, whereby different working cylinder can be connected to the pump housing of the oscillating armature system. Hydraulic drive system according to one of claims 1 to 12, characterized in that the hydraulic drive system (35) with the working piston (1) via connecting pieces (37) and (34) is detachably connected to the tubular body (3) of the pump housing. Hydraulic drive system according to one of claims 1 to 13, characterized in that the magnetic coil (7; 55) is arranged easily replaceable on the outer circumference of the pump housing, whereby it is easily possible to transfer different drive powers for the pump piston or to replace defective coils, without that the system must be completely disassembled.

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