ES2304473T3 - HYDRAULIC DRIVE PUMP SYSTEM WITH OSCILLATING PISTONS. - 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

Hydraulic drive system with pump a oscillating armature pistons.

The invention is about a drive system hydraulic with an oscillating armature piston pump, according to the generic term of claim 1.

In an oscillating armature piston pump of this type, a magnet wraps around the pump housing and produces a axial magnetic field, which moves a piston arranged in shape movable and hermetic inside a working chamber of the pump housing Piston feed drive occurs using the installed magnetic field while the repositioning occurs by a spring repositioning that acts on the piston.

From this piston pump known by the oscillating induced principle results the advantage of a relatively small structure, so that this known pump can be used, for example, as a feed pump for fuel.

However, it is not known that said pump is configured as a hydraulic drive system, so that the pump acts as a regulating drive in conjunction with a working piston

Otherwise, according to the same principle it works DE 195 42 914 C2, which functions as a metering pump with a mobile induced in the form of an active suction piston against the force of a pressure spring, by exciting a electromagnet that wraps it centrally.

Also in this known dosing pump connection to a driven work piston is missing hydraulically

With US 4,458,487 A a electromagnetic regulator drive that takes advantage of pressure of a liquid produced by an electromagnetic pump. In the bomb  a distribution element is available, which can be removed as reaction to the pressure of the liquid, when the liquid is pushed to a second camera from a first camera. The element of distribution can drive a similar valve part, connected in a proven way with it in an all or nothing regulation or a proportional regulation with a long career.

US 4,201,522 discloses a pump containing a pressure boosting device of feeding with a cylinder connected between the suction side and the relief side of the pump. A moveable and mobile piston gone and turn, adjusted to the cylinder and one step of pipe is between the intake side and the relief side divided by the piston. An adjustable spring presses the piston against the side of relief and a valve mechanism limits the discharge of the liquid from the relief side to the suction side, the discharge being felt contrary to a movement of the piston towards the suction side.

With EP 0 065 011 A a hydraulic valve actuation, producing pressure Hydraulic using an electromagnetic pump. Drive comprises a regulating drive for the drive Simultaneous number of valves of this type. The device Opens and closes countless valves, connected in series with a main step by means of a single drive device of valves and can control a proportional valve freely selectable, so that operation is achieved Reliable pump.

The disadvantages of the inventions before mentioned is that they do not have a modular structure within the meaning of the present application (system structure consistent of the pump part and the work cylinder part) and, thus, a simple replacement of work cylinder housings. In addition, in this application, by using a spring loaded piston (see position 52, position 53) harmful air formation is prevented in the intake chamber (19).

In addition, the aforementioned oppositions have a continuous flow of the hydraulic fluid in the resting position of the working piston, which, according to the present application, represents a low performance for the entire
system.

Consequently, the invention aims at of perfecting a hydraulic drive system of such mode, that the replacement of components is guaranteed due to a modular structure

To achieve the stated objective, the invention It is characterized by the features of the claim one.

In the following description of the invention, describe as essentials of the invention different forms of manufacturing.

In a first manufacturing model described a return system, arranged between the pump piston of the pump system and the working piston of the hydraulic system of drive In this way, at the same time it is claimed as essential for the invention a certain distribution by valves

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In the second manufacturing model with a second coil instead of a mechanically moved valve describes a magnetically moved valve, which essentially is It consists of a magnetically movable distributor piston.

The third manufacturing model describes a magnetically movable distribution slide.

In the following, they are also described in abbreviated some variants of the invention:

Variant of sliding piston

The piston part can be realized as a piston  sliding depending on a directional valve. In this way, the channels can be exchanged in the direction of transport and return, so that the working piston can be operated hydraulically with double effect.

Flow rate and pressure variation

One of the possible variants and advantage of system consists of varying the flow rate and pressure through the armature piston

The construction allows a very simple replacement of the magnetic coil body, without intervention in the part of armored drive.

Due to the application of different coils adjusted requirements of electric voltage and power.

Variation of work piston configuration

A diversity of variants in the dimensioning of the working cylinder and piston part It allows adjusting forces and speeds according to the requirements.

Modular structure of the entire system

The complete system can be built in a way modular. Both the pump part and the cylinder part of work are armored units and in the modular system can interconnect

The linear drive presented here can used separately as a feed pump not claimed.

The field of application extends to all applications where linear movement is necessary and should cover all requirements of career and strength.

Complements

The intake chamber can contain an element  dilatable (spring loaded piston, membrane, etc.), which produces a permanent static pressure and, in this way, prevents, by a side, the harmful formation of air in the intake chamber and, on the other hand, it takes into account the behavior of expansion.

The objective of the present invention is not only of the purpose of the different claims, but also of the combination of the different claims.

Next, the invention is explained in detail based on drawings that represent only one means of execution. In this case, arise from the drawings and their description others essential features and advantages of the invention.

They are shown in the:

Figure 1, a section through a model of manufacture of a hydraulic drive system;

Figure 2, a front view of the arrangement, according to figure 1;

Figure 3, a partial section of the provision of Figure 1, with a variation in the flow transfer of hydraulic oil to the drive system;

figure 4, another variant with respect to figure 3, with a magnetically movable distribution slide;

figure 5, another variant with respect to figure 3, with a magnetically movable distribution slide and piston of modified pump.

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In figure 1 a pump is shown in general  oscillating armature pistons, whose pump housing is designated as a tubular body 3. In this case, the magnetic drive is produced by a magnetic coil 7, arranged radially in the outer circumference of the tubular body 3. The body tubular is interrupted in the central zone of the magnetic coil 7 for an antimagnetic centerpiece 8.

On one side of the tubular body 3 is arranged an intake valve 4 loaded by spring, which sucks oil hydraulic from an intake chamber 19 arranged in the face front back.

The intake chamber 19 is composed essentially of a closure ring 51 that internally forms the intake chamber 19, being arranged in the intake chamber 19, for prestressing hydraulic oil, a pressure piston movable 52 which, under the force of a spring 53, moves against the intake chamber 19. This way, you always make sure that the hydraulic oil of the intake chamber 19 is prestressed in the direction of arrow 66 and flows to the intake valve 4 a through a corresponding intake hole 29.

Otherwise, in this case, the valve intake and a corresponding cross hole 25 are mounted on a fixed support piece 17 in the tubular body 3. The hydraulic oil flowing through the intake valve 4 flows behind the piston 6 to the working chamber 18. This piston It consists essentially of a front piston head and, firmly attached to it, a piston rod 27, which in its rear end has a transverse hole that, in the position schematized, it is aligned on the support piece 17 with a cross hole 25 fixed to the housing.

The piston head of the piston 6 is prestressed by repositioning spring 9 in the position of schematized rest and acts in the work position against a stop 31 fixed to the housing, part of a support piece 30 equally fixed to the housing. Consequently, with a load corresponding magnetic of the magnetic coil 7, the piston 6 is moved in the direction of the schematic arrow 67, inwards the piston chamber 20 and seals the hydraulic oil that is found there against a pressure valve 5, which is open correspondingly.

Hydraulic oil enters the orifice of valve 33 of pressure valve 5, overcomes the valve spring and reaches the back of a piston 11, which serves as a piston distributor.

In this case, it is important that the piston distributor 11 form a conductive outer radial groove 22 of liquid, so that hydraulic oil flows through said slit 22 axially forward, to the piston chamber 21, arranged in front of the piston 11.

In this case, the piston 11 is held in its closing position by means of a repositioning spring 15 and is moved forward against the spring force of repositioning 15, by a corresponding application of a pressure stroke axially.

Said piston 11 is fixedly connected as a unit to a tubular part 12, which fits into a hole of corresponding guide 68.

In addition, the piston 11 has on its front side a heel directed axially forward, with a return hole  13 which has a counter hole 23 assigned in the tubular body 3.

The piston 11, together with the front heel front and the rear tubular part 12 is completely crossed by an axial hole.

When hitting a pressure stroke from the pressure valve 5 against the rear of the piston 11, the it is moved axially to the left against the repositioning spring force 15, and the front heel front with the through hole penetrates in this way tight in the counter hole 23 fixed to the housing and is sealed there.

In this way, a return to the intake chamber through axial channel and hole consecutive transverse 32 and 25, as well as 26.

Rather, hydraulic oil flows through from the transverse hole 69 to the connecting piece 34 in the jacket of cylinder 40 of the hydraulic drive system.

Hydraulic oil is transported from the connecting piece 34 in the direction of arrow 43 to the chamber of rear cylinder 43 and acts there on the rear of the piston piece 41, conducted in a sealed manner in the chamber of cylinder 39.

In this way, the entire working piston 1 is move out in the direction of arrow 70 and act on a repositioning spring 2, not shown in detail.

From the cylinder chamber 39, the oil displaced hydraulic is transported through the hole transverse 71 to longitudinal channel 38 and refluxes there in the direction from arrow 44 to pump housing 40.

By means of connection piece 37, the oil hydraulic return enters the return channel 36 in the body tubular 3 of the pump housing and flows directly to the chamber of admission 19.

In addition to the large return channel mentioned previously, there is still the small return channel, which in the essential results from the transverse hole 32 and the channel of 24 consecutive return in the pump housing.

That is, when the piston pump is stopped, the working piston 1 returns in the opposite direction to the direction of arrow 70, the hydraulic oil that is still in the working chamber 42 must return against the direction of the arrow 43 to the collecting chamber 19, through the channel there existing and connection piece 34. This is achieved, because said hydraulic oil now flows through the transverse hole 69 to the front piston chamber 21, enter there in the part front of the return hole 13 in the piston 11, crosses the piston axially and enters the rear of the hole transversal 32.

From there the oil refluxes to the tank, to through the return channel 24 indicated. In this case, it is still foreseen another valve distribution, which allows backflow only when, on the one hand, the piston 11 is in the position of schematized rest and, on the other hand, also the piston 6 is found in rest position.

That is, in this case the transverse hole 25 fixed to the housing is connected to the piston rod 27 arranged in the mobile piston 6, so that oil enters the hole longitudinal 26 fixed to the housing through the transverse hole disposed in the piston rod 27 and from there flows to the reservoir 19.

This would also occur when piston 11 with the tubular part 12 disposed therein it does not present on the side working, a device to regulate the closing time for the return of the oil through said return path. In this case, the return of oil during the bottom dead center of the piston 6 or its piston rod 27 would be so large that at less a part of the finished transport oil would reflux by said path and would act counterproductively to advance of the work piston. This occurs due to the oscillating system composed of the mass of the piston 6 with its different parts, the elastic force of the repositioning spring 9 and the force magnetic coil magnetic 7, which executes the work of drive

To avoid this, according to the invention, a device that, by appropriate sizing of Participating parameters, elastic force and efficient passage of oil, has a certain adjustable dead time for return pipe release. In this way, respecting the static and dynamic system properties, can be regulated, if oil can flow back through the return pipes, and in case positive, in what quantity. Preferably, it has been provided that during the bottom dead center of the piston 6 do not flow oil to through the transverse hole 25, as this would damage the working cylinder advance 1. This could be induced to vibrate. But, if vibratory behavior is required, naturally it would be possible to regulate the reflux, so that the Work piston 1 experiment in its drive movement, At least one superimposed vibration.

Now, the regulation of said dead time is carried out in the present invention in a manufacturing model preferred by configuring piston 11 with the corresponding components and functions.

To perform in the return pipe of the oil a respective downtime regulation, it developed, according to the invention, a regulation element that, in the form of a piston 11, is configured with the valve function. A great part of the oil to be transported for each work run of the pumping piston 6 is passed through the hole 12 (piece tubular) arranged in piston 11, sought by the oil, due to the effective section, on its way to the working piston 1 by the ostensibly lower resistance to the slit 22. Only when piston 11 enters with its return hole 13 in counter-hole 23 it still flows, if necessary, oil through the slit 22 to chamber 21 and from there through the connecting piece 34 towards the work piston.

That is, in this way, the main pipe for the return, the tubular part 12, is ineffective. Through this connection cannot flow oil until the return hole 13. Now this release can be regulated, influencing the respective parameters. This way, you can precisely determined when the tubular part 12 is switched again for oil flow.

Otherwise, by means of a parameterization appropriate can also influence the travel path of the different pistons 6, 11, 1, so that, for example, the they do not complete the entire career and, in this way, neither collide on the respective front faces with the surfaces corresponding. In this way, a huge noise reduction, that is, that the entire hydraulic system He works almost silently.

Generally, it is still argued that the regulation of dead time for oil return not necessarily must be done by means of a so-called piston / cylinder distributor, as in this case piston 11. For this, they are given Different other possibilities. Thus, for example, in the Figure 4 describes in another manufacturing model the cylinder of distribution 57, which also works in this way. The embodiment in figure 3 presents a distributor piston 56 magnetically operated, which also performs this function. From this way, other corresponding manufacturing models they belong to the volume of the invention.

\hbox{magnética 7.}

It is further noted that, in order to at least move the piston 6 magnetically, it is provided on the outer circumference of a magnetic ring 28, which acts in conjunction with the magnetic field of the coil

 \ hbox {magnetic 7.} 

The magnetic ring 28 can also conform a unitary body in conjunction with the piston head and the rod piston

There is another way of functioning in which arranges that the piston 6 remain in its position moved towards left against the force of spring 9 when it is loaded correspondingly by magnetic coil 7. Stop in this way operating prevent a return, it is arranged that the hole transverse in the piston rod 27 no longer aligns in the part of support 17 with the transverse hole 25 fixed to the housing and, of This way, the return is closed. In the drawing it is indicated only, that the front hydraulic system 35 is connected so removable with the tubular body 3 of the pump housing, by the working piston 1 through the connecting parts 37 and 34 indicated.

Modular construction is preferred (plug-in) of both pieces, because it allows a replacement single of the front drive system 35. Thus, it is possible to use different work pistons 1 with runs different.

For the rest, the connection of both parts is performed using a screw 49 applied to the front face of the cylinder sleeve 40, screwed into a threaded bushing 50 corresponding in the pump housing of the tubular body 3.

For the rest, the front working piston 1 is firmly attached to a piston heel 45, driven sealing in cylinder liner 40.

The piston heel 45 forms a heel in diameter  decreased, because it has a ventilation hole 46. This ventilation hole flows into the open air. The top of decreased diameter acts on cylinder sleeve 40 together with a stop 47 fixed to the housing. For the rest, the piston of Work 1 is driven in a sliding way longitudinal in a guide piece 48 of the cylinder sleeve 40

In the pump, according to the invention, it is important that when sucking there is always a constant volume, because due to prestressed with a pressure piston 52 the intake chamber 19 and the existing hydraulic oil is always kept under a true prestressed In this way, there is no mobile volume, and the oil is not extracted from a free tank, but kept low closing.

Regardless of this constant volume in the intake chamber 19, which is kept under pretense elastic, the working piston 1 can move according to the working way of the piston dosing pump and displace Different liquids

Figure 2 shows, in general, the view front of the layout, in which it can be displayed, that the magnetic coil 7 centrally forms an inner hole 54 slid on the tubular body 3 of the pump system.

Figures 3 and 4 show system variants of control valves, according to figure 1. Here is shown, how the piston 11 shown in figure 1 can be replaced by others control elements

In this case, the figure shows a piston magnetically operated distributor 56, loaded by a coil own magnetic 55. Moreover, in this case, in the housing of  pump is a magnetic separation 65, to avoid a short circuit of the magnetic field.

According to the control of the magnetic coil 55, thereby moving the distributor piston 56 back and forth  axial, against the force of the repositioning spring fifteen.

The distributor piston 56 impacts next against a front surface 14 fixed to the housing.

For clarity, it shows how another variant of the return control the tubular part 12, already described in Figure 1, with the axial through hole, which in shape sealant - according to the piston travel position distributor 56 - enters a corresponding blind hole 23 fixed to the housing and thus closes the hole axial.

However, alternatively to this, it is arranged an axial through hole 72 in the distributor piston 56, to which a corresponding valve 73 loaded by  dock.

Said valve flows into a through hole 74 and is in turn in the front piston chamber 20 of the bomb.

If now the pump piston, not shown in detail, requires hydraulic oil in the direction of the arrow to the left, said hydraulic oil, overcoming the valve 73, passes through the passage hole 74 and crosses the hole of passage 72 in the distributor piston 56 and arrives through the bolt connection 34 to drive system 35.

At the same time, the return channel is closed with the tubular part 12, because the front front end enter the blind hole 23.

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In the resting position of the piston Distributor 56 is the reverse case. Valve 73 is closed and a return is made to the intake chamber 19 through of the connecting piece 34, the now open axial hole in the tubular part 12 and the transverse hole 32.

Consequently, the transverse holes 25, complementary to each other with respect to the valves, in the support piece 18 fixed to the housing and in the transverse hole corresponding on the piston rod 27 are no longer necessary.

Figure 4 shows another variant of a remote control. corresponding piston, controlled by a magnetic coil 55, in which also uses a distribution slide 57 magnetically movable.

In front of the piston chamber 20 is arranged the support piece 30, which has the valve hole 33, a through which the hydraulic oil produced by the piston, does not shown in detail, it exceeds the pressure valve 5 in the direction of the arrow.

Said hydraulic oil enters first in working chamber 75 in front of the distribution slide 57, the distribution slide being maintained on its side of left stop by a repositioning spring 58.

On the contrary, if the distribution slide 57 is activated by the magnetic coil, it adopts its first distribution position In this position, hydraulic oil existing in working chamber 55 flows through the channel center 59 and a transverse hole corresponding to a hole cross 76 consecutive fixed to the housing, from where the oil hydraulic flows in the direction of arrow 77 to the system drive 35.

In this way, hydraulic oil feeds the drive system 35.

The return oil flow from the system of actuation is carried out through connection piece 37, connected by transverse holes with the return channel 36. It, in turn, is connected to a cross channel 60 fixed to the housing, carrying liquid. To this cross channel 60 fixed to the housing opposes a transverse hole 61, arranged in the distribution slide 57, so that it is carried out in the activated position of the distribution slide 57 a reflux to through the transverse hole 61 to the distribution slide 57 and, through the central transverse channel 62 in the slide of distribution 57, by a longitudinal channel 78 arranged fixed in the pump housing, back to the intake chamber 19.

The advantage of this manufacturing model is that the valve distribution described in the manufacturing example in connection with the piston rod 27 and The entire distribution of the return was already made in the area of the distribution slide 57.

By the way, this is also the advantage of manufacturing example, according to figure 3.

The other offset position of the distribution slide 57 makes it possible to oppose the hole transverse 64 fixed to the housing to a transverse hole 63 corresponding, arranged in the distribution slide. That is, when the distribution slide 57 is in position with a left stop, the transverse hole 64 coincides with the channel transverse 63 and the hydraulic oil flows axially towards left (arrow direction 79), executing the piston of Work 1 a recoil movement.

Therefore, according to the position of the distribution slide 57, the working piston 1 can be fed with hydraulic oil in its front or part later.

For the rest, it must be argued regarding the example manufacturing, according to figure 1, that the hole provided in the tubular part 12 of piston 11 is designated as a guide hole 68.

With the pump and work piston system integrated into a tubular part a system of simple operation, which occupies little place and, consequently, economic. The easy replaceability of the magnetic coil makes it possible to quickly meet other specifications of performance.

Figure 5 shows another variant of the present invention that, contrary to the manufacturing model in the figure 3, is equipped with a movable distribution slide magnetically and modified pump pistons.

In this example of manufacturing with sliding distribution 57, the armature with piston 27 is located at contrary to the manufacturing models mentioned above, in the intake chamber 19 and transports the oil through the intake valve 4 to the pressure chamber 20 and from there, to through the pressure valve 5, through the slide of 57 distribution to a working cylinder. The particular of this manufacturing model is that during this process the chamber of pressure 20, the intake valve 4, the pressure valve 5 and the return channel 24 can be integrated into a module, being able to this way suppress expensive return channels in the body tubular 3.

In short, it is possible to maintain that the system presents in its first manufacturing model four pistons, responsible for oil conduction and force transmission. They are piston 52, responsible for pressurization permanent system and that ensures that the closed system works almost without air inclusion, piston 6, responsible for the compression and transport of oil, piston 11, competent for oil flow distribution, and finally, the piston of work 1 with its active piston part 41 for movement linear effective to produce.

Due to the fact that the whole system is configured in any manufacturing model as a system closed oil, in the present technical education there is the advantage, that almost no bubbles are formed and the unavoidable consequential problems due to air inclusions in Oil. Thus, the structure of the system as a piston of double action work 1 avoids the usual problems by air inclusion, for example, as bubble formation due to the freely flowing return oil to the tank or chamber of aspiration of the installation. Consequently, the advantage that the system has a non-positive force permanent, which guarantees a continuous linear movement of the working piston and there are no variations in the flow that cause situations of sudden movements.

Due to the technical teaching of the present invention, a selective adjustment of the speed of the  repositioning of the work piston. With this, the setting is produced by sizing the pipe section of oil. Through the influence of the section is regulated properly the volume of refluxing flow, with which it is finally possible to influence the speed of repositioning

The configuration as double acting cylinder It is produced by two oil ducts respectively controllable in the system configured as a tube. It means, that the piston piece 41 of the working piston 1 is bathed with Oil on both sides. The oil in the part front / outside of cylinder 39 is pressed, by means of the upward movement of the piston part 41, through the cross hole 71 to the return and driven system directly back to the intake chamber 19, bringing the Oil circuit closes free of air inclusions. At repositioning of the work piston 1 the flow of oil in reverse. In it, however, according to the teaching technique there is the possibility of distributing the volume to influence repositioning speed as intended.

It is also expected, according to technical education of the present invention, the influence of the advance of the piston of work 1. This can be done by adjusting the Magnetic coil force on the piston 6 conveyor oil. In this case, the distribution is done so that the maximum forward speed occurs with an impending run of 100% and the reduction of the race to respectively less 100%, also resulting in a forward movement reduced, which, due to known relationships, also reduce your speed

The reduction of the running stroke is done by using a selected magnetic coil 7 respectively weaker, capable of moving piston 6 only in part along its maximum work path.

The distribution of the oil flow, already described  broadly, it can happen now in the most diverse way in Different manufacturing models of the present invention. For side, as now presented again, by piston 11 self-controlled by oil pressure, in joint action with the corresponding, intake 4 and relief 5 valves, configured in this case as check valves. Additionally, the repositioning spring 15 and the position of the oil impeller piston 6 act on it, so that only by the influence of the position of the piston 6 is possible to control the repositioning speed.

However, the piston control can also  be performed by elastic force and / or magnetic force.

In another instance, the distribution is made through a two-way valve, in this case called a slide distribution 57, and check valves 4, 5. Said Sliding distribution produces oil conduction for advance, close and reposition of the working piston 1. For execute the desired distribution function, the Sliding distribution by oil pressure and / or force elastic and / or magnetic force.

Reference list

one

Work piston

2

Repositioning spring

3

Tubular body (pump)

4

Admission valve

5

Pressure valve

6

Piston

7

Magnetic coil

8

Center piece

9

Repositioning spring

10

Tubular piece

eleven

Piston

12

Tubular piece

13

Return hole

14

Front surface

fifteen

Repositioning spring

16

17

Support piece

18

Working chamber

19

Admission chamber

twenty

Piston chamber (forward)

twenty-one

Piston chamber (rear)

22

Slit (piston 11)

2. 3

Counter hole

24

Return channel

25

Cross hole

26

Longitudinal hole

27

Piston rod

28

Magnetic ring

29

Intake hole

30

Support piece

31

Stop (support piece 30)

32

Cross hole

33

Valve hole

3. 4

Connecting piece

35

Drive system

36

Return channel

37

Connecting piece

38

Longitudinal channel

39

Cylinder chamber

40

Cylinder liner

41

Piston piece

42

Cylinder chamber

43

Arrow direction

44

Arrow direction

Four. Five

Piston heel

46

Vent hole

47

Stop, top, maximum as a noun, top as an adverb

48

Guide piece

49

Screw

fifty

Threaded bushing

51

Locking ring

52

Pressure piston

53

Dock

54

Inner hole

55

Magnetic coil

56

Distributor piston

57

Sliding distribution

58

Repositioning spring

59

Center channel

60

Cross channel

61

Cross hole

62

Cross channel

63

Cross channel

64

Cross hole

65

Magnetic separation

66

Arrow direction

67

Arrow direction

68

Guide hole

69

Cross hole

70

Arrow direction

71

Cross hole

72

Hole

73

Valve

74

Hole

75

Working chamber

76

Cross hole

77

Arrow direction

78

Longitudinal channel

79

Arrow direction.

Claims (12)

1. Hydraulic drive system with an oscillating armature piston pump with magnetic drive, a cylinder liner (40) followed by a metering piston pump (3) being connected to its housing, directly sealed and axially oriented, in which at least one hydraulically movable working piston (1) is movable, so that together they form a continuous modular body, and for the prestressing of the hydraulic oil a pressure piston (19) is arranged in the intake chamber (19). 52) movable, which is displaced under the action of the force of a spring (53) against the intake chamber (19), characterized in that the hydraulic distribution system (35) is removably communicated by means of connecting parts ( 37) and (34) with the tubular body (3) of the pump housing. 2. Hydraulic drive system according to claim 1, characterized in that the magnetic coil (7; 55) is arranged easily replaceable on the outer circumference of the pump housing. 3. Hydraulic drive system according to one of claims 1 or 2, characterized in that the oil pumped by means of the metering piston pump (3) is conducted in a closed, air-free circuit. 4. Hydraulic drive system according to one of claims 1 to 3, characterized in that the oil circuit drives the working piston (1) in a double acting function. 5. Hydraulic drive system according to one of claims 1 to 4, characterized in that the advance of the working piston (1) can be controlled by the magnetic force of the magnetic coil (7). 6. Hydraulic drive system according to one of claims 1 to 5, characterized in that the repositioning of the working piston (1) can be regulated and / or blocked by controlling the oil volume flow by means of control elements (11; 56; 57) corresponding. 7. Hydraulic drive system according to one of claims 1 to 6, characterized in that the control element (11; 56; 57) is actuated by means of a magnet and / or oil pressure and / or elastic force. 8. Hydraulic drive system according to one of claims 1 to 7, characterized in that the stroke of each drive or control element (6; 11; 56; 57) can be adjusted in the system by the respective parameterization of the effective components, so that it does not impact frontally against the respective component. 9. Hydraulic drive system according to one of claims 1 to 8, characterized in that the supply and return pipes for the oil are partly made in the walls of the tubular body (3) and the work cylinder (40). 10. Hydraulic drive system according to one of claims 1 to 9, characterized in that the pressurized liquid is supplied by the oscillating armature pump (3) directly in the axial direction and feeds the pump housing (40) of the system Hydraulic drive, driving liquid. 11. Hydraulic drive system according to one of claims 1 to 10, characterized in that the oscillating armature piston pump is modularly constructed. 12. Hydraulic drive system according to one of claims 1 to 11, wherein it is possible to easily transmit different drive powers for the pump piston or renew defective coils, without it being necessary to disassemble the entire system.