EP1953387A2 - Pompe à déplacement positif pour transporter un fluide avec adaptation automatique pour la compressibilité du fluide - Google Patents

Pompe à déplacement positif pour transporter un fluide avec adaptation automatique pour la compressibilité du fluide Download PDF

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Publication number
EP1953387A2
EP1953387A2 EP08000832A EP08000832A EP1953387A2 EP 1953387 A2 EP1953387 A2 EP 1953387A2 EP 08000832 A EP08000832 A EP 08000832A EP 08000832 A EP08000832 A EP 08000832A EP 1953387 A2 EP1953387 A2 EP 1953387A2
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EP
European Patent Office
Prior art keywords
pumping chamber
fluid
positive displacement
displacement pump
rod
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP08000832A
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German (de)
English (en)
Inventor
Peter Muschalek
Gunther Erich Schmid
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gardner Denver Thomas GmbH
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Gardner Denver Thomas GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gardner Denver Thomas GmbH filed Critical Gardner Denver Thomas GmbH
Publication of EP1953387A2 publication Critical patent/EP1953387A2/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
    • F04B45/04—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having plate-like flexible members, e.g. diaphragms

Definitions

  • the invention relates to a positive displacement pump.
  • Positive displacement pumps for transporting a fluid have been known for a long time.
  • the dimensions and operating properties of such pumps are usually adapted to a particular type of fluid. They may in particular be adapted to the transport of a compressible fluid, such as a gas, or to the transport of an incompressible fluid, such as a liquid.
  • a change in the composition, and thus the compressibility, of the fluid to be transported may, on the one hand, result in an unwanted reduction of the flow rate and, on the other hand, in an increased stress on the pump, in the worst case the pump may even be damaged.
  • the goal of the invention is to create a positive displacement pump in which a suction or displacement element, respectively, comprising a diaphragm is connected to a drive device in an elastically sprung manner. Depending on the compressibility of the fluid to be transported, this spring element is more or less stressed during each pumping cycle. This leads to an increased suction capacity at a constant flow rate of the fluid while the stress, in particular on the moving parts of the pump, is reduced.
  • a positive displacement pump 1 has a substantially cuboid-shaped housing 2 with a housing base 3 aligned perpendicularly to a longitudinal direction, a first and a second side wall 4 and 5, a housing back wall 6 and a housing cover 7. Additionally, the housing 2 may have a cover, not shown in the drawings, at the housing front side opposite the housing back wall 6.
  • the housing cover 7 has a square cross-section in the direction perpendicular to the longitudinal axis and has a circular opening 8.
  • the side walls 4 and 5 have the shape of an L, the width of the side walls 4 and 5 in the area of the housing cover 7 thus exceeding that in the area of the housing base 3.
  • the housing is substantially mirror-symmetric to a central-longitudinal plane 51.
  • the housing 2 consists of a solid material, such as plastics or metal.
  • a suction or displacement element, respectively, comprising a flexible diaphragm 9 is located adjacent to the housing cover 7 opposite the housing base 3. In a plane perpendicular to the longitudinal direction, the diaphragm 9 has the same external dimensions as the housing cover 7 and completely covers the opening 8.
  • Alternative embodiments of the displacement element, such as pistons, are also conceivable.
  • a chamber cover plate 10 and a cap 11 are located adjacent thereto, both of which having, in a direction perpendicular to the longitudinal direction, the same external dimensions as the housing cover 7.
  • the diaphragm 9 of a fluid-tight material, the chamber cover plate 10 and the cap 11 all have a cross-section in a direction perpendicular to the longitudinal direction which is identical to that of the housing cover 7.
  • the chamber cover plate 10 On its side facing towards the diaphragm 9, the chamber cover plate 10 has a recess in the shape of a spherical segment which is substantially rotation-symmetric to the longitudinal axis and is thus plane-concave.
  • the diaphragm 9, the chamber cover plate 10 and the cap 11 have one bore each 13 in each corner for receiving a cap screw 12.
  • Each of the cap screws 12 engages with a corresponding threaded bore 14 in the housing 2.
  • the housing 2, the diaphragm 9, the chamber cover plate 10 and the cap 11 are safely held in place.
  • the diaphragm 9 is clamped in an immovable and/or gas- or fluid-tight manner along its edge between the housing cover 7 and the chamber cover plate 10.
  • the diaphragm 9 In its central area covering the opening 8, the diaphragm 9 is displaceable along the longitudinal axis in a way as to pass through the opening 8 on the one hand and into the spherical-segment shaped recess of the chamber cover plate 10 on the other hand until it bears against the chamber cover plate 10.
  • the chamber cover plate 10 on the one hand and the diaphragm 9 on the other hand define, or delimit, a pumping chamber 15 with a variable volume V.
  • the chamber cover plate 10 has at least one inlet opening 16 disposed, or arranged, slightly off-centre and at least one outlet opening 17. Via the inlet opening 16, the pumping chamber 15 is connected to a suction channel 20 in the cap 11.
  • a suction valve 19 is disposed between the suction channel 20 and the inlet opening 16.
  • the suction valve 19 comprises a flexible non-return flap.
  • the non-return flap is pivotally disposed in a suction passage 18 between the chamber cover plate 10 and the cap 11. A part of the cap 11 forms a stop for the non-return flap.
  • the suction valve 19 is configured in a way as to allow fluid to enter the pumping chamber 15 in an inlet direction 21 through a suction channel 20, the suction passage 18 and the inlet opening 16 but prevents a fluid flow in the opposite direction, i.e. from the pumping chamber 15 through the inlet opening 16 and the suction passage 18 into the suction channel 20.
  • the outlet opening 17, is connected to an outlet channel 24 in the cap 11 by means of an outlet valve 22 also comprising a flexible non-return flap in a discharge passage 23.
  • the outlet valve 22 enables fluid to be discharged from the pumping chamber 15 through the outlet opening 17 into the outlet channel 24 but prevents a backflow of the fluid opposite to the discharge direction 25 into the pumping chamber 15.
  • a part of the chamber cover plate 10 forms a stop for the non-return flap of the outlet valve 22.
  • the suction channel 20 and the outlet channel 24 may for example be configured as bores or independent pipes in the cap 11.
  • Alternative designs of the suction or outlet valve 19, 22, respectively, are conceivable.
  • a motor 26 is attached to the outside of the housing back wall 6 in a non-rotational manner by means of fixing screws 27.
  • the motor 26 has a shaft 28 which projects into the inside of the housing 2 through a recess, not shown in the figures, in the housing back wall 6.
  • a drive device 29 is attached to the shaft 28.
  • the drive device 29 may be driven by means of alternative drives such as a linear or piezoelectric drive.
  • the drive device 29 comprises an eccentric disk 30, a rod 32 connected to the eccentric disk 30 in a virtually frictionless manner by means of a bearing 31, and a diaphragm connecting element 34 which is displaceable along the rod 32 and spring-mounted by means of a spring element in the shape of a leaf spring 33.
  • the spring element is replaceable.
  • the eccentric disk 30 has a circular cross-section with a symmetry axis and is eccentrically secured to the shaft 28, which is mounted rotatably about an axis of rotation 35, by means of a force-fit and/or a form-fit and/or bonding.
  • the symmetry axis of the circular eccentric disk 30 is located at a distance d from the axis of rotation 35.
  • the bearing 31 may be a slide bearing or, advantageously, a rolling-element bearing. The distance d delimits the maximum travel, or displacement, of the diaphragm 9 and, therefore, the maximum displacement volume of the positive displacement pump 1.
  • the rod 32 has a longitudinal rod axis 50 and is substantially symmetric to the central longitudinal plane 51 when in the top or bottom dead-centre position, respectively, i.e. when the symmetry axis of the eccentric disk 30 and the longitudinal rod axis 50 coincide with the central longitudinal plane 51.
  • the diaphragm connecting element 34 is spring-mounted in the rod 32 and is displaceable along the longitudinal rod axis 50.
  • the diaphragm connecting element 34 is secured to the leaf spring 33 by means of a force-fit and/or a form-fit and/or bonding.
  • the leaf spring 33 is force-fitted and/or form-fitted to the rod 32.
  • the leaf spring 33 is mounted in a rod recess 36 in the rod 32 in an elastically deformable manner.
  • the rod recess 36 substantially has the shape of a D.
  • a through-opening 38 passes through the upper stop 37.
  • the lower stop 39 substantially has the shape of a circular arc. Passing through the through opening 38, the diaphragm connecting element 34 is disposed between the leaf spring 33 in the rod recess 36 and the diaphragm 9. In this position, the diaphragm connecting element 34 is at least force-fitted to both the leaf spring 33 and the diaphragm 9.
  • the diaphragm connecting element 34 may be integral with the leaf spring 33.
  • the diaphragm connecting element 34 has a cylindrical projection 42.
  • the diaphragm 9 On the side facing towards the diaphragm connecting element 34, the diaphragm 9 has a hollow cylindrical recess 40 into which the cylindrical projection 42 is inserted in a form-fit engagement.
  • the spring element is a helical compression spring 33a.
  • the helical compression spring 33a is replaceable.
  • the rod recess 36a has a substantially cuboid shape.
  • the helical compression spring 33a is disposed on the rod 32a on a cylindrical spring mandrel 41 disposed in the centre of the rod recess 36a.
  • the length of the spring mandrel 41 at least equals the length of the helical compression spring 33a in a fully compressed state.
  • the diaphragm connecting element 34a comprises a hollow cylinder which is substantially closed on one side and surrounds the helical compression spring 33a.
  • the cylinder barrel may be interrupted, thus ensuring that the diaphragm connecting element 34a does not protrude beyond the rod 32a in the direction of the axis of rotation 35.
  • the diaphragm connecting element 34a is form-fitted to the receiving element 40 of the diaphragm 9 by means of the cylindrical projection 42.
  • a stop collar 43a is attached to the outside of the cylinder barrel.
  • the diaphragm connecting element 34a is thus mounted in the rod recess 36a for displacement in the longitudinal direction, with the stop collar 43a bearing against the upper stops 37a in a first end position and against the lower stop 39a in a second end position.
  • the lower stops 39a are plane and extend parallel to the upper stops 37a.
  • the front wall closing one end of the hollow cylinder is advantageously flush with the spring mandrel 41. In that case, it is not absolutely necessary for the stop collar 43 to bear against the lower stops 39a in the second end position.
  • the length and compressibility of the helical compression spring 33a are adapted to the dimensions of the spring mandrel 41, or in particular to the distance between the upper stops 37a and the lower stops 39a, in a way that said helical compression spring 33a is pre-stressed both in the first end position of the diaphragm connecting element 34a as well as in the second end position of the diaphragm connecting element 34a.
  • the spring element comprises an elastomer spring 33b.
  • the elastomer spring 33b is replaceable. It is advantageously made of an elastically deformable plastic material, such as EPDM or NBR.
  • the elastomer spring 33b has a substantially cuboid shape, with a length 1 along the longitudinal rod axis 50, a depth t in the direction of the axis of rotation 35 and a width b perpendicular to the two other directions.
  • the rod recess 36b has a substantially cuboid shape. It may be delimited by a support plate 44 on the side facing towards the housing back wall 6. Moreover, the recess 36b may be at least partially delimited by another support plate on the side facing away from the housing back wall 6. In the direction of the longitudinal rod axis 50, the recess has upper and lower stops 37b and 39b.
  • the diaphragm connecting element 34b has an angled U-profile. Stop collars 43b are disposed on the outside of the two free ends of the U-profile.
  • the cylindrical projection 42 is disposed on the side of the U-profile facing towards the diaphragm 9.
  • the pumping cycle may substantially be subdivided into two phases, i.e. a suction phase on the one hand during which the suction valve 19 is open and fluid enters the pumping chamber 15 through the suction channel 20 and the inlet opening 16 while the outlet valve 22 is closed, thus preventing a backflow of fluid opposite to the discharge direction from the outlet channel 24 into the pumping chamber 15, and a discharge phase on the other hand during which the suction valve 19 is closed and the outlet valve 22 is open, thus preventing a backflow of fluid opposite to the inlet direction 21 from the pumping chamber 15 through the suction channel 20, and enabling fluid to flow through the outlet channel 24 and out of the pumping chamber 15 in the discharge direction 25.
  • a suction phase on the one hand during which the suction valve 19 is open and fluid enters the pumping chamber 15 through the suction channel 20 and the inlet opening 16 while the outlet valve 22 is closed
  • one of the two valves 19, 22 is open at a particular time substantially during the normal operation of the positive displacement pump 1, while the other of the two valves 19, 22 is closed, and vice versa.
  • the pressure difference applied to the valve 19 or 22, respectively i.e. the difference between the fluid pressure pK(t) in the pumping chamber 15 and the pressure pI in the suction channel 20 or the pressure pO in the outlet channel 24, respectively, determines whether the valve 19 or 22, respectively, is open or closed.
  • pO ⁇ pI with both pO as well as pI being substantially constant at least for the duration of a cycle.
  • the fluid pressure pK(t) in the pumping chamber 15 varies cyclically due to the movement of the drive device 29, in particular the corresponding movement of the diaphragm 9, thereby causing a cyclic variation of the volume V(t) of the pumping chamber 15.
  • the pressure pK(t) in the pumping chamber 15 may be increased by reducing the volume V(t) while the pressure pK(t) in the pumping chamber 15 may be reduced by increasing the volume V(t).
  • the goal of the positive displacement pump 1 according to the invention is to connect the diaphragm 9 to the rod 32 in a spring-mounted manner by means of a spring element 33; 33a; 33b, thereby damping in particular the pressure increase or pressure reduction, respectively, in the pumping chamber 15, the amount of damping being a function of the stiffness of the spring element 33; 33a; 33b and said pressure increase or pressure reduction, respectively, depending on the compressibility of the fluid to be transported.
  • the shaft 28 is driven by a motor 26 about the axis of rotation 35 in a direction of rotation 45.
  • the following is a description of a complete pumping cycle starting from a top dead centre position of the drive device 29.
  • a pumping cycle is described during which the spring element 33; 33a; 33b is rigid, therefore not changing its shape. This may be the case during the transport of a compressible fluid and/or at a low speed of rotation of the shaft 28 and/or if the spring element 33; 33a; 33b is very stiff.
  • the diaphragm 9 is substantially pressed against the concave side of the chamber cover plate 10 ( Fig. 2 ; Fig.
  • the pumping chamber 15 has a minimum volume.
  • a rotation of the shaft 28 in the direction of rotation 45 causes the diaphragm 9 to be pulled away from the chamber cover plate 10 ( Fig. 3 ; Fig. 10 ; Fig. 17 ).
  • the volume of the pumping chamber 15 increases.
  • pK(t) is reduced.
  • a relative low pressure is generated in the pumping chamber 15, with pK(t) ⁇ pI.
  • This causes the outlet valve 22 to close the outlet opening 17 while the suction valve 19 opens, thus enabling fluid to flow into the pumping chamber 15 through the suction channel 20, the suction passage 18 and the inlet opening 16.
  • the rotation of the eccentric disk 30 causes the volume of the pumping chamber 15 to increase until the drive device 29 has reached the bottom dead centre ( Fig. 4 ; Fig. 11 , Fig. 18 ).
  • a further rotation of the eccentric disk 30 in the direction of rotation 45 causes the diaphragm 9 to be pressed in the direction towards the chamber cover plate 10, thereby reducing the volume of the pumping chamber 15. Consequently, the pressure pK(t) in the pumping chamber increases.
  • a relative overpressure is generated in the pumping chamber 15, with pK(t) > pO.
  • the overpressure in the pumping chamber 15 causes the suction valve 19 to close, thus preventing a backflow of the fluid from the pumping chamber 15 through the inlet opening 16 and into the suction channel 20. Moreover, the overpressure in the pressure chamber 15 causes the outlet valve 22 to open, thus enabling the fluid to flow out of the pumping chamber 15 through the outlet opening 17 and into the outlet channel 24. A further rotation of the eccentric disk 30 in the direction of rotation 45 reduces the volume of the pumping chamber 15 until the drive device 29 has reached the top dead centre (cf. Fig. 2 ; Fig. 9 ; Fig. 16 ) again.
  • the volume of the pump chamber 15 increases, this in turn causing the pumping chamber pressure pK(t) to be reduced to a low pressure in the pumping chamber 15, pK(t) ⁇ pI.
  • the low pressure if pK(t) > pI, causes the suction valve 19 to open, thus enabling fluid to flow from the suction channel 20 through the inlet opening 16 and into the pumping chamber 15.
  • the volume of the pumping chamber 15 increases until the drive device 29 has reached the bottom dead centre ( Fig. 4 ; Fig. 11 ; Fig. 18 ).
  • a further rotation of the eccentric disk 30 about the axis of rotation 35 then reduces the distance along the longitudinal rod axis 50 between the drive device 29 and the diaphragm 9.
  • the force acting on the spring element 33; 33a; 33b increases, thus causing the diaphragm connecting element 34; 34a; 34b to be displaced in the rod recess 36; 36a; 36b until the force of the spring element 33; 33a; 33b acting on the diaphragm connecting element 34; 34a; 34b prevents any further displacement, at the most until the diaphragm connecting element 34; 34a; 34b comes to bear against the lower stops 39; 39a; 39b or the spring mandrel 41, respectively ( Fig. 7 ; Fig. 14 ; Fig. 21 ).
  • the rod 32; 32a; 32b presses the diaphragm 9 in the direction towards the chamber cover plate 10 by means of the diaphragm connecting element 34; 34a; 34b, thus causing the volume of the pumping chamber 15 to be reduced.
  • the outlet valve 22 opens ifpK(t) > pO, thus enabling the fluid to flow out of the pumping chamber 15 in the discharge direction 25, i.e. through the outlet opening 17 and into the outlet channel 24.
  • the volume of the pumping chamber 15 reduces until the drive device 29 has reached its top dead centre ( Fig. 6 ; Fig. 13 ; Fig. 20 ).
  • Both the extent of deformation of the spring element 33; 33a; 33b during a particular cycle and the particular phase of the cycle during which the diaphragm connecting element 34; 34a; 34b comes to bear against the upper stop 37; 37a; 37b and, as the case may be, against the lower stop 39; 39a; 39 are individually determined by, amongst other things, the compressibility of the fluid to be transported, the speed of rotation of the shaft 28 and the stiffness of the spring element 33; 33a; 33b.
  • Force peaks on the drive device 29, the diaphragm 9, the pumping chamber 15 and the valves 19, 22 occurring in particular in the top or bottom dead centre position, respectively, are damped due to the diaphragm 9 being spring-mounted to the drive device 29.
  • a systematic selection of a spring element 33; 33a; 33b having corresponding damping properties enables the positive displacement pump 1 to be specifically adapted to the expected operating conditions. Thereby, the suction capacity of the positive displacement pump 1 may be optimized, depending on the fluid to be transported, while reducing the stress on the positive displacement pump 1, in particular on the moving parts thereof.
  • the displacement volume of the positive displacement pump 1 is automatically adapted to the compressibility of the fluid to be transported and to the drive speed of the drive device 29.
  • the less the displacement of the diaphragm connecting element 34; 34a; 34b in the rod recess 36; 36a; 36b during a pumping cycle i.e. the higher the compressibility of the fluid to be transported while using the same spring element 33; 33a; 33b, or the stiffer the spring element 33; 33a; 33b while retaining the compressibility of the fluid to be transported, respectively, the larger the compression ratio of the fluid to be transported in the pumping chamber 15.
  • a softer spring element 33; 33a; 33b causes the compression ratio, and thus me displacement volume of the positive displacement pump 1, to be reduced.
  • the rod 32c comprises a rod drive area 46 which is concentric with the eccentric disk 30, two rod recess side walls 47 extending parallel to the longitudinal rod axis 50 and tangentially adjoining said rod drive area 46 in an integral manner as well as rod stop walls 48 which are integral with said rod-recess side walls 47.
  • the upper rod stop walls 48 are deformable with respect to the rod-recess side walls 47.
  • Each of the upper rod stop walls 48 has a free end 56 facing towards the through-opening 38c. When the rod 32c is unstressed, the upper rod stop walls 48 are substantially perpendicular to the rod-recess side walls 47.
  • the rod-recess side walls 47 and the rod stop walls 48 form the spring element 32c.
  • the side of the upper rod stop wall 48 facing towards the rod recess 36c forms the upper stop 37c for the diaphragm connecting element 34c.
  • the lower stop 39c is formed by the side of the rod stop area 46 facing towards the rod recess 36c.
  • the through-opening 38c disposed between the upper rod stop walls 48 is advantageously configured as a longitudinal recess extending in the direction parallel to the axis of rotation 35 along the entire depth of the rod 32c. This results in an improved deformability of the upper rod stop walls 48 with respect to the rod-recess side walls 47. Moreover, this provides for a simpler arrangement of the diaphragm connecting element 34c in the rod 32 during the assembly.
  • the diaphragm connecting element 34c is slidable in particular over the rod 32c.
  • the diaphragm connecting element 34c is symmetric, in particular rotation-symmetric, with respect to the longitudinal rod axis 50. It has a rod connecting portion 49 which is integral with the cylindrical projection 42.
  • the rod connecting portion 49 comprises an upper transverse wall 52, a lower transverse wall 53 and a connecting piece 54 disposed therebetween.
  • the upper transverse wall 52 and the lower transverse wall 53 define a bead-like groove 55.
  • the diaphragm connecting element 34c is relatively stiff. In particular, the modulus of elasticity thereof exceeds that of the material the rod 32c is made of. This results in a particularly effective transmission of force from the rod 32c to the diaphragm 9.
  • the diaphragm connecting element 34c may also be elastic, thus contributing to the resilience of the diaphragm 9.
  • the diaphragm connecting element 34c is replaceable. It may be chosen in particular in accordance with the respective requirements.
  • the side of the upper transverse wall 52 facing towards the groove 55 is positioned at an angle w 1 with respect to a horizontal plane which is perpendicular to the longitudinal rod axis 50.
  • the angle w 1 is in the range of 1° to 10°.
  • the side of the lower transverse wall 53 facing towards the groove 55 is positioned at an angle w 2 .
  • the angle w 2 is in the range of 0.5° to 5°.
  • the angle w 2 is in particular small enough to ensure a maximum deflection of the diaphragm 9 in the bottom dead centre position of the drive device 29c.
  • the groove 55 thus widens outward. At its inner end, i.e. in the area of the connecting piece 54, the configuration of the groove 55 substantially corresponds to that of the free ends 56 of the upper rod stop walls 48. Each of the upper rod stop walls 48.is in engagement with the groove 55.
  • the lower transverse wall 53 of the diaphragm connecting element 34c is thus disposed in the rod recess 36c. In the direction perpendicular to the longitudinal rod axis 50, the dimensions thereof are thus smaller than those of the rod recess 36c in this direction. Thus, a clearance is formed between the lower transverse wall 53 of the diaphragm connecting element 34c and the rod-recess side walls 47.
  • the lower transverse wall 53 On its side facing towards the lower stop 39c, the lower transverse wall 53 has a central recess in the shape of a cylindrical portion the curvature of which just corresponds to that of the lower stop 39c in the area of the longitudinal rod axis 50.
  • the rod 32c In the top dead centre position, shown in Fig. 22 , of the drive device 29c, the rod 32c is substantially mirror-symmetric to the central longitudinal plane 51. In this position, the dimension of the through-opening 38c in the direction perpendicular to the central longitudinal plane exceeds the dimension of the connecting piece 34 of the diaphragm connecting element 34c in the same direction.
  • the diaphragm connecting element 34c is thus displaceable in the directions perpendicular to the longitudinal rod axis 50 and perpendicular to the axis of rotation 35.
  • the functioning of the positive displacement pump 1 substantially corresponds to that of the previous embodiments to which reference is made.
  • the function of the spring element 33c is performed by the elastic rod 32c, in particular by the upper rod stop walls 48.
  • the rod 32c exerts a tensile force on the diaphragm connecting element 34c.
  • the upper rod stop walls 48 increasingly come to bear against the lower transverse wall 53 of the diaphragm connecting element 34.
  • the angle, measured inside the rod recess 36c, between the upper rod stop walls 48 and each of the rod-recess side walls 47 adjacent thereto increases more and more until it has reached the value of 90° + w 2 . In this position shown in Fig.
  • the eccentric disk 30 performs a rotation in the direction of rotation 45 during the discharge phase, thus reducing the volume of the pumping chamber 15, the rod 32c exerts a thrust force on the diaphragm connecting element 34c.
  • the upper rod stop wall 48 is increasingly pressed against the side of the upper transverse wall 52 of the diaphragm connecting element 34c facing towards the groove 55. The upper rod stop wall 48 is thus more and more pressed into the rod recess 36c.
  • the angle between the upper rod stop wall 48 and each of the adjacent rod-recess side walls 47 is reduced to an angle of 90°-w 1 at which at least part of the surface of the upper rod stop wall 48 bears against the upper transverse wall 52.
  • the respective sides of the upper transverse wall 52 and the lower transverse wall 53 of the diaphragm connecting element 34c facing towards the groove 55 are inclined by the angles w 1 or w 2 , respectively, thus ensuring that the diaphragm connecting element 34a gradually comes to bear against the upper rod stop wall 48.
  • the elastic rod 32c is thus a spring element 33c providing a progressive damping effect.
  • the damping behavior may be influenced by means of the exact configuration of the upper transverse wall 52 or the lower transverse wall, respectively.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP08000832A 2007-01-31 2008-01-17 Pompe à déplacement positif pour transporter un fluide avec adaptation automatique pour la compressibilité du fluide Withdrawn EP1953387A2 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007005736A DE102007005736A1 (de) 2007-01-31 2007-01-31 Verdrängungs-Pumpe zur Förderung eines Fluids mit automatischer Anpassung an die Kompressibilität dieses Fluids

Publications (1)

Publication Number Publication Date
EP1953387A2 true EP1953387A2 (fr) 2008-08-06

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EP08000832A Withdrawn EP1953387A2 (fr) 2007-01-31 2008-01-17 Pompe à déplacement positif pour transporter un fluide avec adaptation automatique pour la compressibilité du fluide

Country Status (4)

Country Link
US (1) US20080181800A1 (fr)
EP (1) EP1953387A2 (fr)
CN (1) CN101235813A (fr)
DE (1) DE102007005736A1 (fr)

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WO2014174072A1 (fr) * 2013-04-26 2014-10-30 Continental Teves Ag & Co. Ohg Ensemble pompe
KR101616964B1 (ko) 2014-06-16 2016-05-11 강소대 크랭크축을 이용한 압축공기발생기
WO2016080058A1 (fr) * 2014-11-20 2016-05-26 株式会社Ibs Pompe à diaphragme
WO2023118581A1 (fr) * 2021-12-23 2023-06-29 KNF Micro AG Tête de pompe de pompe à membrane

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US9175676B2 (en) 2009-12-08 2015-11-03 Les Chaussures Stc Inc. Fluid compression system
EP2372157B2 (fr) 2010-03-18 2016-07-13 L & P Swiss Holding AG Pompe à diaphragme pour dispositif de réglage de siège et dispositif de réglage de siège
CN103403352B (zh) * 2011-03-09 2016-03-30 Ulvac机工株式会社 泵装置
DE102011078499A1 (de) * 2011-07-01 2013-01-03 Robert Bosch Gmbh Membran zum Fördern von Medien
US10012229B2 (en) * 2013-12-19 2018-07-03 Other Lab Llc Diaphragm compressor system and method
DE102014013779A1 (de) * 2014-09-17 2016-03-17 Knf Flodos Ag Membranpumpe
DE102015205061A1 (de) * 2015-03-20 2016-09-22 Continental Teves Ag & Co. Ohg Motorpumpenaggregat mit einer Membraneinheit
EP3452721B1 (fr) * 2016-05-06 2020-04-15 Graco Minnesota Inc. Pompe à membrane modulaire à entraînement mécanique
TWI659719B (zh) * 2017-02-09 2019-05-21 瑞士商耐斯泰克公司 用於飲料製備模組之薄膜泵
DE102017104400A1 (de) 2017-03-02 2018-09-06 Qonqave Gmbh Pumpenvorrichtung zu einer Förderung zumindest eines Fördermittels
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WO2012016962A3 (fr) * 2010-08-04 2012-06-07 Gardner Denver Thomas Gmbh Pompe
WO2014174072A1 (fr) * 2013-04-26 2014-10-30 Continental Teves Ag & Co. Ohg Ensemble pompe
US9784264B2 (en) 2013-04-26 2017-10-10 Continental Teves Ag & Co. Ohg Pump assembly
KR101616964B1 (ko) 2014-06-16 2016-05-11 강소대 크랭크축을 이용한 압축공기발생기
WO2016080058A1 (fr) * 2014-11-20 2016-05-26 株式会社Ibs Pompe à diaphragme
WO2023118581A1 (fr) * 2021-12-23 2023-06-29 KNF Micro AG Tête de pompe de pompe à membrane

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CN101235813A (zh) 2008-08-06
DE102007005736A1 (de) 2008-08-14

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