DE102010013108A1 - Double diaphragm pump - Google Patents

Abstract

The invention relates to a diaphragm pump in which a fluid moves at least a first piston (1) of a first piston-cylinder system (1, 2, 3) back and forth, the first piston (1) having at least one further hydraulic piston ( 9) is mechanically connected, and the hydraulic piston (9) drives at least one membrane (M1, M2) by means of a hydraulic medium.

Description

The present invention relates to a diaphragm pump having at least one membrane.

In membrane pumps, the membrane limits a delivery chamber into which a supply line and an outlet line open. As a rule, non-return valves are arranged in the supply and discharge lines in such a way that, by moving the membrane back and forth, the conveying medium can first be sucked into the conveying space via the feed line and then be forced out of the conveying space via the outlet line.

So that a continuous pumping is possible, usually two diaphragm pumps are connected in parallel, wherein one sucks the fluid and the other presses out the pumped fluid from its pumping chamber in the same time.

Double diaphragm pumps are also known in which the diaphragms, which are usually designed as disc diaphragms, are adjusted by means of a common piston-cylinder system or by means of an electric drive. In rooms in which explosive gases may occur, no electric pumps may be operated or the strict requirements of explosion protection must be taken into account. Here, pneumatic pumps are generally used, in which a piston which is mechanically connected to the membranes, is moved by means of compressed air in a cylinder back and forth. The compressed air is switched by means of a main valve such that the two working spaces are alternately filled with compressed air. Such a pump is out of the US 4,818,191 known. The separate from the pump room from the membranes chambers are connected by channels with the environment, so that in case of leakage, the fluid can escape from the pump and does not hinder the movement of the membranes. A disadvantage of this pump is that the membranes are exposed to a high differential pressure load due to the high pressure in the delivery chamber and the pressure prevailing behind the membrane ambient pressure, resulting in rapid wear of the membranes.

A further developed pneumatically driven double diaphragm pump is from the WO2009 / 024619 known. In this pump, the compressed air driving the piston is simultaneously directed into the space behind the membrane. At the same time, the membrane is supported by a plate, which, however, only fully supports the membrane in one dead center. The disadvantage of this pump is that in case of a defect of the membrane, the fluid enters the pneumatic and the valves and thus the entire pump is out of action. The pump can then be repaired, if at all, only with great effort.

A double-chamber diaphragm pump without driven piston is out of the DE 32 06 242 known. A disadvantage of this pump are the large spaces that must be filled after reaching dead center with compressed air, so that the membrane can be moved in the other direction. This requires a lot of compressed air, which increases the maintenance costs of the pump. A similarly constructed pump with the same disadvantages is from the CA 1172904 , of the WO97 / 10902 and the US 5,368,452 known. Also at the time of the W2009 / 024619 known pump disproportionately much compressed air is required for the operation of the pump. Also, these pumps are not pressure-translated, so that the delivery pressure is always below the feed pressure.

Object of the present invention is to provide a diaphragm pump, in which the membranes have a long service life and are subjected to low differential pressures and has a good efficiency.

This object is achieved with a diaphragm pump having the features of claim 1. Advantageous embodiments of the diaphragm pump according to claim 1 result from the features of the subclaims.

The invention is based on the idea that the diaphragm pump has a first piston-cylinder system whose piston drives at least one hydraulic cylinder. The piston can thereby by means of a fluid, for. B. compressed air or a liquid medium, d. H. be moved back and forth. As a result, the at least one hydraulic piston is also moved back and forth. The hydraulic piston is in turn arranged in a cylinder and divides this into two working spaces, a first and a second working space. At least one first working space is filled with a hydraulic medium which acts on the membrane of the diaphragm pump. Advantageously, the diaphragm pump is designed as a double diaphragm pump, so that in each case the two membranes promote alternately. Advantageously, the first working space is limited in each case by the hydraulic piston and the membrane. However, it is also possible that the working space is connected via a connecting line with the space separated from the diaphragm by the pumping chamber, and thus the hydraulic medium moved by the hydraulic piston acts on the diaphragm and adjusts it.

The first piston of the first piston-cylinder system is advantageously driven by compressed air, so that the diaphragm pump can also be used in explosion-proof rooms.

Due to the freely selectable surfaces of the first piston and hydraulic piston, any desired pressure ratio between the driving pneumatic pressure and the delivery pressure of the pump can be adjusted.

Regardless of the delivery pressure of the diaphragm pump, the diaphragms are exposed to a maximum of one differential pressure load (maximum suction power) of one bar, which advantageously results in a long service life of the diaphragms.

Advantageously, as the hydraulic medium, an inert liquid is selected for the conveyed medium, so that in the event of a defect in the membrane, the fluid being conveyed is not contaminated. If the fluid enters the first working space in the event of a malfunction, this will not affect the pump.

Advantageously, the second working spaces of the hydraulically acting piston-cylinder systems are interconnected so that they function as damping members by pumping the medium in these work spaces, which is advantageously the same inert hydraulic medium as in the first work spaces, back and forth.

If the pump is designed as a double diaphragm pump, the membranes are advantageously connected to each other by means of a connecting element, which synchronizes the movement of the membranes. This connecting element is not used to drive the membranes. Advantageously, the connecting element at its ends in each case a thread with which it is screwed into the membranes. The screwing can be done directly in the material, in particular rubber, or in an inset in the membrane threaded bushing. Since the connecting element does not transmit large forces, it is usually possible to dispense with a threaded bushing.

A small construction is advantageously achieved if the driving first piston-cylinder system is arranged between the hydraulically acting piston-cylinder systems. The first piston is rigidly connected by means of piston rods with the two hydraulic pistons, whereby they are adjusted synchronously with him. The connecting element of the membranes can advantageously pass through the tubular piston rods and is mounted in these displaceable. At the same time, the connecting element passes through the hydraulic pistons, with correspondingly arranged seals preventing hydraulic fluid from passing from one working space to the other through the piston rods.

Advantageously, the diaphragm pump has at least one device for monitoring the quantity of hydraulic medium present in one and / or several working chambers of the hydraulically acting piston-cylinder systems and / or in their connecting line. If hydraulic medium escapes and is sucked out of a storage container, this is detected by the device and the pump stopped and / or sent an error signal to a higher-level control system.

The first piston of the first piston-cylinder system reciprocating fluid, in particular compressed air, is guided by a main valve, which is controlled in particular by the movement of the first piston, alternately into the first and second working space of the first piston-cylinder system.

In the working spaces axially or frontally bounding walls of the first piston-cylinder system are each of the first piston before or upon reaching the respective dead center or switching point mechanically operated changeover valves, in particular 3/2-way valves arranged. The switching valves control the main valve switching compressed air. Advantageously unregulated compressed air is used, d. H. Compressed air provided by an external source of compressed air. This pressure is usually higher than the pressure with which the diaphragm pumps are operated according to the prior art. This ensures that the diaphragm pump according to the invention safely switches. This is often not the case with diaphragm pumps of the prior art, in which the main valve has only one input for regulated air, since the regulated pressure to the first piston-cylinder system is often very low.

The first piston actuates the valve actuators of the changeover valves mechanically, wherein the changeover valves are designed in particular as a cartridge valve, d. H. from the outside in the respective frontally limiting wall of the first piston-cylinder system can be used, in particular screwed, are. This results in a particularly favorable structure, since the valves can be replaced without opening the delivery chambers.

The main valve is advantageously arranged outside of the housing of the diaphragm pump, so that the main valve can be easily cleaned, repaired or replaced.

Advantageously, the main valve is designed as a 4/2-way valve or as a 5/2-way valve. Ie. the valve control element of the main valve moves alternately back and forth between two end positions. It thus has only two defined positions in the form of end positions. On the way from one end position to the other end position, that is, during the movement, in a middle region between the end positions, the two working spaces of the first piston-cylinder system connected to each other via the valve control element of the main valve and thus pre-filled receiving the working space with the compressed air from the transferring workspace. Thereafter, the working space, which was pre-filled, filled with regulated air on. The other working space is connected to the valve outlet, so that the remaining working air from the working space can relax via muffler. This results in a better efficiency of the diaphragm pump according to the invention, since less compressed air is required for the operation of the pump.

Advantageously, the main valve has an input for unregulated compressed air of an external compressed air source, wherein the main valve itself may have a pressure control device for generating regulated compressed air of a certain pressure. About a slidably disposed in the housing of the main valve control valve, which is controlled by the controlled by the switching valves compressed air, in particular the uncontrolled compressed air, the regulated compressed air is passed alternately into the working chambers of the first piston-cylinder system.

So that the remaining working space in the dead centers of the first piston is as small as possible, the axial cylinder walls of the cylinder of the first piston-cylinder system can be advantageously adapted to the shape of the axial walls of the first piston. A planar design of the walls is to be preferred here.

The switching valves may advantageously have throttles, so that the forced out of the respective working space air is braked by the throttle and this advantageously leads to a slowed movement of the valve control element of the main valve from the central region, whereby the phase of pressure equalization between the prestressed and soon To be emptied work space and the next to be filled work space is as long as possible. The throttle at the beginning of the movement of the pneumatic piston is not so strong, so that the valve control element of the main valve is moved at high speed from its end position in the direction of the central region in which the working spaces of the pneumatic cylinder are short-circuited.

Each delivery chamber can advantageously be connected via a respective feed channel to a common supply line and / or via an outlet channel to a common pressure line, wherein the supply line and / or the pressure line is floatingly mounted on at least one connection region of the pump housing. This advantageously ensures that no mutually occurring stresses occur at the joints mechanical fatigue. Valves, in particular non-return valves, are respectively arranged in the feed channels and in the outlet channels.

It is of course possible that by means of the first piston-cylinder system, which is in particular pneumatically driven by compressed air, a plurality of mutually parallel hydraulic piston can be driven. As a result, more than two membranes, in particular a multiple of two, can be driven or adjusted for sucking and pressing by means of a pneumatic drive.

Hereinafter, a possible embodiment of the diaphragm pump, which is designed as a double diaphragm pump, explained in more detail with reference to drawings.

Show it:

1 : Perspective view of the diaphragm pump according to the invention in the form of a double diaphragm pump;

2 : sectional view of the diaphragm pump according to 1 ;

3 : Cross-sectional view through the double diaphragm pump according to the 1 and 2 ;

4 : Partial excerpt from the 3 ;

5 : Pneumatic plan for a diaphragm pump according to the invention with a 5/2-way valve as the main valve;

6 : Pneumatic plan for a diaphragm pump according to the invention with 4/2-way valve as the main valve.

The 1 and 2 show a perspective view of the diaphragm pump according to the invention in the form of a double diaphragm pump. The double diaphragm pump has a housing cover 19 as well as the cylinder 10 of the hydraulically acting piston-cylinder system 9 . 10 receiving housing part 11 on. The housing part 11 is how in 2 represented by means of coaxial screws 11a on the axial cylinder wall 3 attached to the first piston-cylinder system. From the housing cover 19 and the housing part 11 is at 22 (S. 3 and 4 ) the membrane M is clamped. housing cover 19 and housing part 11 are by means of screws 19a connected together and hold the membrane M in position. The housing cover 19 forms below and above each a receptacle for a check valve 24 , The check valves 23 . 24 be before the Screw on the housing flanges 25 . 27 to the housing cover 19 in the corresponding recesses of the housing cover 19 used. Additional seals prevent the fluid around the housing of the check valves 23 . 24 can penetrate around. The axial walls 3 of the first piston-cylinder system are by means of spacers 7 kept at a distance and by means of screws 6 connected with each other. Between the walls 3 is also pressure-tight, the cylindrical wall sleeve 2 , which forms the cylinder, arranged, with additional seals provide for the tightness. The screws 6 have a screw head 6a and at the end of a thread 6b on, with which they have one axial wall 3 are bolted.

In the cylinder 2 . 3 of the first piston-cylinder system is the first piston 1 arranged by two slices 1a . 1b is formed and the work spaces A and B separated from each other. The disks 1a . 1b are by means of screws 4 screwed together. The cylindrical wall 2 has on its outside ribs for absorbing heat from the ambient air to prevent icing of the diaphragm pump. The axial walls 3 also have recesses 3b on, which also serve better heat conduction and for stiffening and material savings. The piston 1 has a circumferential seal 1c on, the sealing on the inner wall of the cylinder 2 is applied.

When assembling the piston 1 beforehand through the holes 1d the piston stands 8a . 8b pushed until the collar 8c in the corresponding recesses 1e the piston discs 1a . 1b einliegen. By assembling the piston discs 1a . 1b are the piston rods 8a . 8b positively on the piston 1 attached.

The piston rods 8a . 8b go through the holes 3a the axial walls 3 , where seals 56 ensure that no compressed air from the working spaces A, B enters the hydraulic chambers H ₂ . With their ends 8d are the piston rods 8a . 8b with the hydraulic piston sealing by means of screws 60 connected. The piston rods 8a . 8b are formed as tubes in which the connecting element 5 displaceable in the form of a rod rests. The connecting element 5 is with its externally threaded ends 5a in the diaphragm plate 20 screwed. The diaphragm plate 20 is in the membrane M _i in the middle 21 formed.

The hydraulic pistons 9 each have a circumferential seal 12 on, the sealing on the inner wall of the cylinder wall 10 abut and the two work spaces H ₁ , H ₂ separate. The two hydraulic chambers H _{2 of} the two hydraulic piston-cylinder systems are via the connecting channels 16 . 17 and 18 connected with each other. In the hydraulic piston 9 are each differential pressure valves 13 arranged. If, when working the pump, the differential pressure between the working spaces H ₁ and H ₂ exceeds a certain value, the differential pressure valve opens 13 and the differential pressure can be lowered to a predetermined value. The connection channel 16 . 17 . 18 can be connected by means of a further connection line, not shown, with a storage container and / or a sensor. If there is now an inflow or outflow of hydraulic medium on the reservoir or the connecting line, this may mean a breakage of the membrane, whereupon a fault signal can be sent to a higher-level control and / or the membrane pump is automatically stopped. This can be z. B. by the positively controlled closing of the pump supplying compressed air supply line.

The feed channels 28 are by means of the feed line 36 connected to each other, wherein the supply line 36 with their one end 41 forms the delivery medium inlet of the pump. The other end of the tube designed as a supply line 36 is by means of a screwed plug 34 locked. The feed line 36 lies with their areas 36a floating in the housing flanges 27 one, with seals 39 provide the necessary tightness. The housing flanges 27 show one the areas 36a comprehensive annulus 40 on, which is formed by a circumferential groove. In the area 36a has the supply line 36 window-like openings 38 on, through which the fluid from the interior 37 the supply line 36 in the annulus 40 and from there into the feed channel 28 arrives.

The outlet channels 26 are by means of the pressure line 29 interconnected, the pressure line 29 with their one end 33 forms the pumped fluid outlet of the pump. The other end of the pipe designed as a pressure line 29 is by means of a screwed plug 34 locked. The pressure line 29 lies with their areas 29a floating in the housing flanges 25 one, with seals 39 provide the necessary tightness. The housing flanges 25 show one the areas 29a comprehensive annulus 32 on, which is formed by a circumferential groove. In the fields of 29a indicates the pressure line 29 window-like openings 31 on, through which the fluid from the annulus 32 in the interior 30 the pressure line 29 can get.

In the axial walls 3 are changeover valves 14 arranged with an extension 15 extend their valve control elements in the working spaces A, B. If the piston 1 reaches its dead center, the respective changeover valve is actuated, whereby compressed air for not main valve 50 is passed, and the main valve in turn switches.

The main valve 50 is arranged on the outside of the pump housing, so that a good heat exchange with the ambient air can take place, whereby the risk of icing is reduced.

If the diaphragm plate 20 by means of the hydraulic piston 9 is adjusted so that the delivery space F _{i is} reduced, the delivery medium located in the delivery chamber F _i through the check valve 24 in the outlet channel 26 promoted. The check valve 23 is closed during this. If it is subsequently increased into the delivery space F _i by retraction of the membrane M _i , then the now open check valve is opened 23 from the supply line 36 Feed medium sucked into the delivery chamber F _i . During the intake phase is the check valve 24 locked.

The 5 shows a pneumatic diagram of the diaphragm pump according to the 1 to 4 , The compressed air operated diaphragm pump has a compressed air inlet 43 that is beneficial to the main valve 50 is arranged. In or at the main valve 50 can the pressure regulator 45 be arranged, which by means of the connecting line 44 with the entrance 43 connected is. The pressure regulator 45 may be a proportional valve, which has an adjustment mechanism, for. B. in the form of an adjusting screw, may have with which a spring for pressure adjustment can be biased. If an unregulated pressure of 7 bar provided by the external compressed air source (not shown), so can by the pressure control device 45 via the connecting line to the main valve 50 a regulated compressed air of z. B. 5.5 bar.

The entrance 43 is over interconnections 48 . 49 with the changeover valves 14 in connection. The switching valves are designed as 3/2-way valves and are by means of extending into the working spaces A, B extensions 15 switched their valve control members. A spring presses the valve control members in the position shown, in which the control lines 52 . 53 not with the valve inlet or the connection line 48 . 49 are connected. As soon as the piston 1 the respective valve control member 15 adjusted, the switching valve 14 switched and the uncontrolled compressed air of the external pressure source switches the main valve 50 around.

The main valve 50 is designed as a 5/2-way valve. In the illustrated position, the regulated compressed air passes through the connecting line 57 in the working space A. The piston 1 thus becomes together with the hydraulic piston 9 adjusted to the right. By means of the hydraulic medium located in the hydraulic spaces H ₁ , the right-hand membrane (not shown ₎ is now adjusted to the right, which reduces its associated delivery space. The right membrane thus promotes. At the same time sucks in as well 5 not shown left membrane conveying medium from the supply line into its delivery chamber. When reaching the right dead center, the right switching valve 14 about the extension 15 switched so that the main valve 50 also switched. On the way to the left, first, the connection of the working space A with the connecting line 47 interrupted. Thereafter, the two work spaces are shorted together, so that the biased compressed air located in the working space B can relax into the working space A inside. There is a certain amount of time available for this until finally the main valve 50 has completely switched through and over the connecting line 47 regulated compressed air is directed into the working space B, causing the piston 1 now moved to the left. The remaining not yet relaxed compressed air in the pressure chamber B relaxes then via the valve outputs 51 over the silencers 35 in the nearby areas.

The 6 shows an alternative embodiment in which the main valve 50 is designed as a 4/2-way valve. The main valve 50 is different from the one in 5 illustrated main valve only in that only one output 51 is provided.

LIST OF REFERENCE NUMBERS

A, B

Working space of the first piston-cylinder system

M ₁ , M ₂

membrane

1

First piston of the first piston-cylinder system

1a, 1b

piston discs

1c

poetry

1d

drilling

1e

Recess for collar 8c

2

Cylinders of the first piston-cylinder system

2a

Outer cooling ribs of the cylinder 2

3

axial cylinder wall of the first piston-cylinder system

4

screw

5

connecting element

5a

Thread of the connecting element 5

6

connecting screw

7

spacer

8a, 8b

piston rod

8c

collar

9

hydraulic pistons

10

Cylinder of the hydraulically acting piston-cylinder system

11

housing part

12

poetry

13

Differential pressure _valve (p _H1 > p _H2 )

14

switching valve

15

Valve control member

16, 17, 18

Channel / link line

19

housing cover

20

diaphragm plate

21

Membrane area in which the diaphragm plate 20 arranged is

22

Clamping area of the membrane M _i

23

Check valve in the feed channel (only shown in left chamber)

24

Check valve in outlet channel (only shown in left chamber)

25

Housing flange with outlet channel 26 (Outlet housing)

26

exhaust port

27

Housing flange with feed channel 28 (Inlet housing)

28

feed

29

pressure line

30

Interior of the pressure line 29

31

Passage opening in the wall of the pressure line 29

32

Annulus, the pressure line 29 includes

33

Pump outlet for pumped medium

34

Plug with screw thread

35

Silencer for emanating the relaxing compressed air

36

feed

37

Interior of the supply line 36

38

Passage opening in the wall of the supply line 36

39

seals

40

Annulus, which is the supply line 36 includes

41

Pump inlet for pumped medium

42

foot

43

Input for uncontrolled compressed air from an external compressed air source

44

connecting line

45

Pressure control device in the form of a proportional valve

46

Adjustment mechanism for regulated output pressure of the pressure regulator 46

47

Connecting line, supplies regulated compressed air to the main valve 50

48, 49

Connecting line for uncontrolled compressed air

50

main valve

51

Outputs of the main valve, with the silencers 35 are in communication

52, 53

Control line from the changeover valve 14 to the main valve 50

54, 55

Exit to the outside

56

poetry

57

Connecting line to the working space A

58

Connecting line to the working space B

66

Throttle in the changeover valve 14

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• US 4818191 [0004]
• WO 2009/024619 [0005, 0006]
• DE 3206242 [0006]
• CA 1172904 [0006]
• WO 97/10902 [0006]
• US 5368452 [0006]

Claims (28)

A diaphragm pump in which a fluid has at least one first piston ( 1 ) of a first piston-cylinder system ( 1 . 2 . 3 ), the first piston ( 1 ) with at least one further hydraulic piston ( 9 ) is mechanically connected, and the hydraulic piston ( 9 ) drives by means of a hydraulic medium at least one membrane (M ₁ , M ₂ ). Diaphragm pump according to claim 1, characterized in that the diaphragm pump is a double diaphragm pump with at least two diaphragms (M ₁ , M ₂ ), wherein a hydraulic medium moves or drives the diaphragms (M ₁ , M ₂ ), wherein at least one hydraulic piston ( 9 ) moves the hydraulic medium. Diaphragm pump according to claim 2, characterized in that in each case two membranes (M ₁ , M ₂ ) by means of a connecting element ( 5 ), in particular a rod or a tube, are mechanically interconnected. Diaphragm pump according to claim 3, characterized in that the connecting element ( 5 ) with each of its ends ( 5a ) in each case connected to a membrane (M ₁ , M ₂ ), in particular screwed into this or pressed, is. Diaphragm pump according to one of the preceding claims, characterized in that a membrane (M ₁ , M ₂ ) in a membrane space of a housing ( 11 . 19 ), and subdivided into a delivery space (F ₁ , F ₂ ) and a hydraulic space (H ₁ ). Diaphragm pump according to claim 5, characterized in that the hydraulic space (H ₁ ) communicates with the first working space of the piston-cylinder system of a hydraulic piston ( 9 ), in particular by means of a duct or a conduit, is in communication, forms a part of the working space or is the working space itself. Diaphragm pump according to one of the preceding claims, characterized in that compressed air is the first piston ( 1 ) of the first piston-cylinder system ( 1 . 2 . 3 ), whereby a main valve ( 50 ), which in particular by the movement of the first piston ( 1 ), the compressed air is alternately in the first and second working space (A, B) of the first piston-cylinder system ( 1 . 2 . 3 ). Diaphragm pump according to one of the preceding claims, characterized in that the first piston-cylinder system ( 1 . 2 . 3 ) between two hydraulically acting piston-cylinder systems ( 9 . 10 ), the first piston ( 1 ) with the hydraulic pistons ( 9 ) via at least one piston rod ( 8a . 8b ), in particular the first piston ( 1 ) passes through and / or is attached to this / are in communication. Diaphragm pump according to claim 8, characterized in that the connecting element ( 5 ) freely displaceable to the first piston ( 1 ) and to the hydraulic pistons ( 9 ), in particular in the piston rod ( 8a . 8b ) is displaceably mounted and the two hydraulic pistons ( 9 ). Diaphragm pump according to claim 9, characterized in that sealing elements between the connecting element ( 5 ) and the hydraulic piston ( 9 ) and / or the piston rod ( 8a . 8b ) are arranged such that no hydraulic medium along the connecting element ( 5 ) can get from one hydraulic chamber (H ₁ , H ₂ ) in the other hydraulic space. Diaphragm pump according to one of the preceding claims, characterized in that the hydraulically acting piston-cylinder systems ( 9 . 10 ) each having a first and a second working space (H ₁ , H ₂ ), and in each case the first working space (H ₁ ) is part of the hydraulic space forms this or is connected to this via a channel, and the second working spaces (H ₂ ) via a connecting line ( 16 . 17 . 18 ) are in communication with each other. Diaphragm pump according to claim 11, characterized in that the second working spaces ( 112 ) as well as the connecting line ( 16 . 17 . 18 ) are filled with a hydraulic medium. Diaphragm pump according to claim 11 or 12, characterized in that the diaphragm pump at least one means for monitoring the amount of in one and / or more working spaces (H ₁ , H ₂ ) of the hydraulically acting piston-cylinder systems ( 9 . 10 ) and / or in the connecting line ( 16 . 17 . 18 ) has located hydraulic medium. Diaphragm pump according to claim 13, characterized in that the second working spaces (H ₂ ) and these interconnecting connecting line ( 16 . 17 . 18 ) are connected via a further connecting line with a storage container containing a hydraulic medium, wherein the device determines a discharge and / or inflow of hydraulic medium through the further connecting connecting line. Diaphragm pump according to one of the preceding claims, characterized in that at least that in the hydraulic spaces (H ₁ , H ₂ ) located hydraulic medium is inert to the pumped medium. Diaphragm pump according to one of the preceding claims, characterized in that each delivery chamber (F ₁ , F ₂ ) via a respective feed channel ( 28 ) with a common supply line ( 36 ) and / or via a respective outlet channel ( 26 ) with a common pressure line ( 29 ), wherein the supply line ( 36 ) and / or the pressure line ( 29 ) floating on at least one connection area ( 25 ) of the pump housing is mounted. Diaphragm pump according to claim 16, characterized in that in the feed channel ( 28 ) and in the outlet channel ( 25 ) one valve each ( 23 . 24 ), in particular check valve, is arranged. Diaphragm pump according to one of the preceding claims, characterized in that the piston surface of the first piston ( 1 ), in particular of the pneumatic piston, greater than or equal to, in particular in a certain ratio, in particular in the ratio 1: 1 to 1:40 to the piston surface of the or the hydraulic piston (s) ( 9 ). Diaphragm pump according to one of the preceding claims, characterized in that an exchange of hydraulic medium from one to the other working space (H ₁ , H ₂ ) of a hydraulically acting piston-cylinder system ( 9 . 10 ) via a valve ( 13 ), in particular overpressure or vacuum valve, when exceeding or falling below a certain pressure difference between the working spaces (M ₁ , M ₂ ) takes place. Diaphragm pump according to claim, characterized in that in the hydraulic piston ( 9 ) an overpressure or vacuum valve ( 13 ) is arranged, which axially through the hydraulic piston ( 9 ) running connecting channel normally shuts off. Diaphragm pump according to one of the preceding claims, characterized in that the axial cylinder walls ( 3a ) of the working spaces (A, B) of the first piston-cylinder system ( 1 . 2 . 3 ) to the shape of the axial walls ( 1c ) of the first piston ( 1 ) are adapted, in particular plan are formed, such that the remaining working space in the dead centers of the piston ( 1 ) is minimal. Diaphragm pump according to one of the preceding claims, characterized in that in the working spaces (A, B) axially or frontally bounding walls ( 3 ) of the first piston-cylinder system ( 1 . 2 . 3 ) one each from the first piston ( 1 ) before or upon reaching the respective dead center or switching point mechanically actuated changeover valve ( 14 ), in particular a 3/2-way valve is arranged, wherein the switching valves ( 14 ) the main valve ( 50 ) switching compressed air, in particular uncontrolled compressed air control. Diaphragm pump according to claim 22, characterized in that the piston ( 1 ) the valve actuators of the changeover valves ( 14 ) mechanically operated, wherein the switching valves ( 14 ) are formed in particular as a cartridge valve, that is, from the outside into the respective end wall ( 3 ) of the first piston-cylinder system ( 1 . 2 . 3 ) can be used, in particular screwed, are. Diaphragm pump according to one of the preceding claims, characterized in that the main valve ( 50 ) is a 5/2-way valve or 4/2-way valve, in particular in the switching phase, the two working spaces (A, B) of the first piston-cylinder system ( 1 . 2 . 3 ) and thus the receiving working space (A, B) with the compressed air from the transferring working space (B, A) prefilled. Diaphragm pump according to one of the preceding claims, characterized in that the main valve ( 50 ) an entrance ( 43 ) for unregulated compressed air from an external source of compressed air, the main valve ( 50 ) itself a pressure control device ( 45 ) for generating regulated compressed air of a certain pressure. Diaphragm pump according to one of the preceding claims, characterized in that the main valve ( 50 ) has a valve control member, which of the switching valves ( 14 ) controlled compressed air, in particular unregulated compressed air, is adjusted. Diaphragm pump according to claim 26, characterized in that the valve control member of the pressure control device ( 45 ) controlled compressed air and for adjusting the first piston ( 1 ) in the working spaces (A, B) of the first piston-cylinder system ( 1 . 2 . 3 ). Diaphragm pump according to one of the preceding claims, characterized in that the switching valves ( 14 ) Throttling ( 66 ) exhibit.

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