EP1046816B1 - Soupape d'admission d'une pompe - Google Patents

Soupape d'admission d'une pompe Download PDF

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Publication number
EP1046816B1
EP1046816B1 EP00108472A EP00108472A EP1046816B1 EP 1046816 B1 EP1046816 B1 EP 1046816B1 EP 00108472 A EP00108472 A EP 00108472A EP 00108472 A EP00108472 A EP 00108472A EP 1046816 B1 EP1046816 B1 EP 1046816B1
Authority
EP
European Patent Office
Prior art keywords
pressure
cylinder
suction
suction valve
pressure chamber
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.)
Expired - Lifetime
Application number
EP00108472A
Other languages
German (de)
English (en)
Other versions
EP1046816A2 (fr
EP1046816A3 (fr
Inventor
Hermann Breitsamer
Franz Hani
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.)
Speck-Kolbenpumpenfabrik Otto Speck & Co KG GmbH
Original Assignee
Speck-Kolbenpumpenfabrik Otto Speck & Co KG 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
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Publication of EP1046816A2 publication Critical patent/EP1046816A2/fr
Publication of EP1046816A3 publication Critical patent/EP1046816A3/fr
Application granted granted Critical
Publication of EP1046816B1 publication Critical patent/EP1046816B1/fr
Anticipated expiration legal-status Critical
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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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons
    • F04B53/125—Reciprocating valves
    • F04B53/129—Poppet valves
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F04B39/0016—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons with valve arranged in the piston
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F04B39/0022—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons piston rods
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons
    • F04B53/125—Reciprocating valves
    • F04B53/127—Disc valves
    • F04B53/128—Annular disc valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2203/00—Non-metallic inorganic materials
    • F05C2203/08—Ceramics; Oxides
    • F05C2203/0865—Oxide ceramics
    • F05C2203/0869—Aluminium oxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/12—Polyetheretherketones, e.g. PEEK
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00—Other material characteristics; Treatment of material
    • F05C2253/12—Coating

Definitions

  • the invention relates to a pump with at least one conveyor assembly comprising a piston axially guided in a plunger, which varies with its drive remote end the volume in a pressure chamber, the suction stroke with at least one of the pressure chamber opposite side of the plunger inlet port and at Pressure stroke communicates via a pressure valve arrangement with at least one outlet opening.
  • Such pumps are for example from the US 5,658,134 , of the US 5,174,735 , of the US 5,346,373 , of the US 3,920,356 , of the US 3,809,508 and the US 3,652,188 known.
  • At least one passage opening into the pressure chamber during the suction stroke is formed in the plunger, said passage extending at least partially obliquely to the movement axis of the plunger.
  • This passage can comprise a channel opening into the pressure chamber and an antechamber upstream of the channel upstream with an enlarged free flow cross-section relative to the channel.
  • the plunger is mounted for centering in the cylinder on the piston rod at least to a small extent movable.
  • the bearing of the plunger is designed such that at least a small axial mobility of the plunger is given relative to the piston rod.
  • the plunger in the cylinder can optimally align itself in a manner ensuring trouble-free operation, in particular with regard to the sealing effect, whereby tolerances with regard to the guidance of the piston rod can be compensated.
  • the possibility of self-adjustment of the plunger in the cylinder reduces the wear of the seals used and thus increases the life of the pump with consistently good sealing properties.
  • the pressure chamber is sealed to the suction side on the one hand via the plunger.
  • the plunger is preferably provided with at least one peripheral recess in which a seal is arranged, which is formed in a particularly preferred variant as existing of Teflon Gleitdichtring.
  • a particular high-temperature resistant and impact-resistant plastic such as PEEK, could be used for the sliding seal.
  • the Gleitdichtring can by means of an elastically deformable, arranged between the bottom of the peripheral recess and the Gleitdichtring O-ring to be biased in the direction of the cylinder inner wall. In this way, an optimal sealing effect is achieved with low frictional resistance.
  • the sealing of the pressure chamber via the suction valve plate, the in the form of axial bores or obliquely to the longitudinal axis extending passages in the plunger closes existing flow connection in the pressure chamber.
  • the cylinder is made of aluminum, wherein the cylinder inner wall is formed by a suitable conversion process alumina. Teflon particles can also be incorporated in the alumina.
  • the cylinder in particular hardened steel, wherein preferably the cylinder inner wall is provided with an additional surface layer, in particular a CVD or PVD surface layer.
  • an additional surface layer in particular a CVD or PVD surface layer.
  • hardened steel of hardness 62 HRC provided with an additional CVD or PVD surface layer can be provided as the cylinder material.
  • a hardness of 2400 HV can be achieved.
  • the cylinder surface can be extremely finely polished. The wear on the cylinder wall and on the seals is significantly reduced by these measures.
  • the pressure chamber delimiting end faces of the suction valve and the pressure valve assembly at the end of the pressure stroke so approximate approached each other that the volume of the pressure chamber is negligible compared to the maximum value at the end of the suction stroke value and preferably approximately reduced to zero.
  • the minimum distance between facing end faces of the pressure valve arrangement and the Saugventilan extract is less than 1 mm and is preferably in the range of 0.1 to 0.2 mm.
  • a plurality of at least substantially identical conveying arrangements are provided, wherein the pump can be used by connecting the inlet opening of at least one conveying arrangement with the outlet opening of at least two other conveying arrangements as a multi-stage compressor.
  • the pump according to the invention thus comprises a plurality of principle independently operating conveyor arrangements whose plunger can be provided with a common drive.
  • a pressure line which is connected to a common outlet opening of two conveying arrangements, can be connected to the inlet opening of the third conveying arrangement.
  • the pump could also be operated as a three-stage or multi-stage compressor.
  • the pump according to the invention is particularly suitable for use with carbon dioxide.
  • Fig. 1 shows a portion of a pump according to an embodiment of the invention with three conveyor assemblies whose longitudinal axes 70 lie in one plane.
  • the conveyor assemblies are of identical construction and each have a piston rod 28 which are driven via a common drive for carrying out axial reciprocating movements in a respective cylinder 10.
  • a common drive unit for the conveyor arrangements is in Fig. 1 not shown.
  • a suction housing 42 having a perpendicular to the longitudinal axis 70 extending inlet channel 15, the cylinder 10 and a pressure valve body 18 of a pressure valve assembly clamped by means of screw 46.
  • the suction housing 42, the cylinder 10 and a plunger 12 define a delivery chamber 32 into which the inlet port 15 having an inlet opening 16 opens.
  • a suction line can be connected.
  • a radially projecting, circumferential collar 18a of the pressure valve body 18 is clamped between the drive-remote end face of the cylinder 10 and the pressure housing 44.
  • the drive-side end face of the cylinder 10 abuts against a shoulder 45 of the suction housing 42.
  • An outlet opening for the piston rod 28 from the delivery chamber 32 is bounded by a radially inwardly projecting collar 43 of the suction housing 42.
  • On the drive side is located on the collar 43 of the suction housing 42, a cylindrical annular portion of the centering element 34, the piston rod 28 facing inner surface with annular recesses 36 for seals 31, 96 is provided.
  • annular recesses 36 a made of Teflon Gleitdichtring 31 is arranged, which could be additionally biased for example by means of a stainless steel spring in the direction of the piston rod 28.
  • a high-temperature resistant and impact-resistant plastic such as e.g. PEEK be used for the sliding seal 31.
  • the centering element 34 bears against a shoulder 41 of the retaining element 40. By the centering element 34, the suction housing 42 is centered to the drive.
  • the plunger 12 is held at the free end of the piston rod 28 via a screw 27 whose head is formed by a head part 26, in such a way that the plugged on the screw 27 plunger 12 is movable in a small extent in the axial direction relative to the piston rod 28.
  • the plunger 12 inserted into the cylinder 10 substantially in registration can align at least to a certain extent independently of the piston rod 28 in the cylinder 10.
  • the head part 26, which is screwed tightly in the axial direction with the piston rod 28, has a pin 26b and a flange portion 26a which terminates flush with the pin 26b on the side of the head part 26 facing away from the piston rod 28 and thus forms a flat end face.
  • the pin 26b cooperates with an annular projection 12a of the plunger 12 to hold the plunger 12 on the piston rod 28.
  • the screw 27 can be rotated by means of a corresponding tool.
  • the recesses 26c are closed by means of sealing plugs, whereby the dead space is advantageously minimized.
  • the plugs for the recesses 26c are made for example of a temperature-resistant plastic.
  • annular suction valve plate 24 On the head part 26, an annular suction valve plate 24 is arranged, whose outer diameter is smaller than the inner diameter of the cylinder 10. The resulting intermediate space between the outer edge of the suction valve plate 24 and the cylinder inner wall is part of a pressure chamber 14 described in more detail elsewhere.
  • the Saugventilplatte 24 and the head part 26 are provided with each other in the radial direction overlapping flange portions 24a, 26a, wherein the Saugventilplatte 24 is slidably mounted with a ring portion 24b on the flange portion 26a of the head portion 26.
  • the plunger 12 is provided with a recess 90 in the form of a radially limited by obliquely to the longitudinal axis 70 side walls bounded annular channel.
  • a recess 90 in the form of a radially limited by obliquely to the longitudinal axis 70 side walls bounded annular channel.
  • the plunger 12 facing side of the suction valve plate 24 is cone-shaped so that they - according to the position according to Fig. 1 - During the pressure stroke, the recess 90 fills and sealingly abuts the oblique side walls, wherein for sealing annular sealing elements 92 are provided.
  • the sum of the axial heights of the flange portions 24a, 26a of the suction valve plate 24 and the head part 26 is smaller than the axial height of the protruding from the plunger 12 part of the pin 26b.
  • the suction valve plate 24 between the head part 26 and the plunger 12 is axially free to move.
  • a gap or gap 50 is present.
  • Fig. 1 shows the plunger 12 and the Saugventilan Aunt formed by the Saugventilplatte 24 and the head part 26 at the top dead center, ie at the end of the pressure stroke.
  • the suction valve plate 24 abuts on the plunger 12 and fills the recess 90 such that the axial bores 52 in the plunger 12, which open radially outside of the tapered end of the piston rod 28 into the delivery chamber 32, through the Saugventilplatte 24 are closed. There is thus no flow connection between the axial bores 52 in the plunger 12 and the annular gap between the outer edge of the suction valve plate 24 and the cylinder inner wall during the pressure stroke.
  • the suction valve assembly 24, 26 a perpendicular to the longitudinal axis 70 extending, flat end face, which is formed by the side facing away from the piston rod 28 sides of the head part 26 and the suction valve 24.
  • the conveyor assembly is designed so that at top dead center, the end face of the suction valve 24, 26 so close to the suction valve assembly 24, 26 facing end of the - closer described - pressure valve assembly 18, 20 moved up, that a very small, in Fig. 1 unrecognizable axial gap between the two end faces is present, which forms part of the minimized in this state pressure chamber 14 of the conveyor assembly.
  • the pressure chamber 14 is thus formed substantially by the annular space between the outer edge of the suction valve plate 24 and the cylinder inner wall.
  • the pressure valve body 18 is part of a pressure valve assembly, which also comprises a pressure valve element 20 which has approximately the shape of a capped cap and by a coil spring 21 against the side facing away from the pressure chamber 14 side of the pressure valve body 18 is biased.
  • the spring 21 is supported on a sleeve-shaped support member 13 which is screwed to the pressure valve body 18 and communicates via apertures in the side wall with the outlet space 23.
  • a central opening 61 is formed, the boundary surface widens in a funnel shape in the direction of the outlet space 23 according to the shape of the pressure valve element 20 and thus forms a valve seat.
  • the pressure valve assembly 18, 20 is dimensioned such that in the closed state according to Fig. 1 the suction valve assembly 24, 26 facing, formed jointly by the pressure valve body 18 and the pressure valve element 20 end face - in the below explained variant with bevel 94 only approximately - flat surface which is perpendicular to the longitudinal axis 70.
  • the end face of the pressure valve body 18 may be bevelled, as shown in FIG Fig. 1 is indicated by dashed lines 94, wherein the illustration is exaggerated for clarity. Due to the chamfer, a wedge-shaped, slightly widening in the direction of the longitudinal axis 70 annular gap between the opposite end faces of the Saugventilan extract 24, 26 and the pressure valve assembly 18, 20 is present. In this way, it is ensured that during the pressure stroke liquid flows in the direction of the longitudinal axis 70 and through the opening 61, without congestion or blocking of the piston assembly due to the liquid present between the end faces.
  • the arranged on the side facing away from the pressure chamber 14 of the pressure valve body 18 components of the pressure valve assembly are located in the pressure chamber 18 and the pressure housing 44 limited outlet space 23 to which a outlet opening 22 having radial outlet channel 25 a pressure line, not shown, is connectable.
  • the area of the cylinder 10 surrounded by the pressure housing 44 is provided with a spiral groove 48, which can be supplied via an inlet 47 with a cooling fluid, which is preferably used for water.
  • a cooling fluid which is preferably used for water.
  • the cylinder 10 is provided on its outside with cooling fins 49.
  • the seal between the suction housing 42 and centering element 34, between the suction housing 42 and cylinder 10 and between the pressure housing 44, cylinder 10 and pressure valve body 18 is effected by arranged in corresponding circumferential recesses O-rings 60th
  • the cylinder 10 is made of aluminum, the cylinder inner wall being made of alumina, which is produced by a conversion process, e.g. a hard-coat conversion, is produced on the cylinder inner wall. Furthermore, embedded in the cylinder inner wall forming alumina Teflon particles.
  • the cylinder may alternatively be made of hardened steel, e.g. hardness 62 HRC and provided on the inner wall with an additional CVD or PVD surface layer. To minimize wear, the cylinder surface is also extremely finely polished.
  • the suction valve plate 24 and the pressure valve element 20 are made of PEEK. In principle, other, in particular high-temperature-resistant and / or impact-resistant, plastic materials can be used.
  • the conveyor arrangement according to the invention is suitable for conveying fluids both in the liquid and in the gaseous state.
  • the plunger 12 moves together with the Saugventilan Aunt 24, 26 in Fig. 1 to the left, so that the axially freely movable suction valve plate 24 abuts the head part 26, that is, the gap 50 is no longer present.
  • the increasing pressure chamber 14 is filled with liquid or gaseous fluid during the suction stroke, which flow via a not shown, coupled to the inlet port 16 suction line, the inlet channel 15, the delivery chamber 32 and the plunger 12 and the Saugventilan Aunt 24, 26 can.
  • a flow connection from the pressure chamber 14 into the outlet chamber 23 through the opening 61 of the pressure valve body 18 is closed by the pressure valve element 20, which is pressed by means of the spring 21 on the pressure valve body 18 serving as a valve seat on this side.
  • the pressure valve assembly 18, 20 opens at the beginning of the pressure stroke, so that the liquid through the opening 61 of the pressure valve body 18 at the lifted off the valve seat pressure valve element 20 into the outlet space 23 and the outlet channel 25 and the outlet opening 22 can flow into the pressure line, not shown.
  • the conveyor assembly is advantageously dead space optimized, since at the end of the pressure stroke, the pressure chamber 14 only of the annular space between the outer edge of the Saugventilplatte 24 and the cylinder inner wall and of the minimum gap at "A" in Fig. 1 is formed between the flat end faces of the Saugventilan extract 24, 26 and the pressure valve assembly 18, 20.
  • the recesses 26 c are - as mentioned - following the assembly - in Fig. 1 not shown - Plug elements inserted so that the recesses 26 c do not contribute to the pressure chamber 14.
  • the dead space optimization has a very good efficiency especially when promoting gaseous media.
  • Fig. 2 illustrated embodiment of a pump according to the invention differs from that of Fig. 1 in particular by the formation of the plunger 12 and the Saugventilan Aunt formed by the Saugventilplatte 24 and a head 98. This also applies to the details described elsewhere Fig. 3 and 4 , On with the embodiment of Fig. 1 matching aspects will not be discussed further below.
  • the suction valve plate 24 is surrounded by the annular head portion 98, wherein again in the radial direction overlapping flange portions 24a, 98a are provided.
  • the head part 98 is screwed with a sleeve portion 98b on an axially remote from the drive end face of the plunger 12 ring portion 12b and axially displaceably mounted with a flange 98a on a ring portion 24b of the suction valve plate 24. With its flange portion 24a, the suction valve plate 24 bears against the inside of the ring portion 12b of the plunger 12.
  • the axial mobility of the Saugventilplatte 24 is according to the embodiment of Fig. 1 is ensured by the gap 50, which is present during the pressure stroke between the radially overlapping flange portions 24a, 98a.
  • Both end faces of the suction valve plate 24 and the plunger 12 are flat and perpendicular to the longitudinal axis 70.
  • the pressure valve body 18 may be provided with a bevel 94 indicated by the dashed lines. In the position according to Fig. 2 At the end of the compression stroke, the axial bores 52 in the plunger 12 are closed by the suction valve plate 24.
  • the suction valve plate 24 has a central opening 99 whose diameter is slightly larger than that of the head portion 26 of the screw 27, which is flush in this embodiment with the end face of the plunger 12. Into the opening 99 projects the - its closed position occupying - pressure valve element 20 into which is formed in this embodiment as a complete dome.
  • both liquid and gaseous medium can be conveyed via the delivery chamber 32, the axial bores 52 in the plunger 12, one in the state of Fig. 2 lacking clearance zwisehen the plunger 12 and the suction valve plate 24 and the opening 99 into the pressure chamber 14 to flow.
  • Fig. 2 Not shown in Fig. 2 are plug elements which are inserted after installation in the recesses 26c of the screw head portion 26 and fill the opening 99 so that during the intake stroke, although a fluid flow from the axial bores 52 through the opening 99 into the pressure chamber 14 is possible during the Druckhubs however, the pressure chamber 14 substantially by the in Fig. 2 is formed by an "A" indicated gap between the suction valve plate 24 and the pressure valve body 18. The distance between the facing end faces of these two components is at the end of the pressure stroke about 0.1 to 0.2 mm. In this way, the conveyor arrangement according to the invention of Fig. 2 advantageously space-optimized and optimally suitable for conveying gaseous media with high efficiency.
  • Fig. 3 and 4 each show a training of in Fig. 2 illustrated pump. The differences are in particular in the formation of the plunger 12 and the suction valve 24 and the Head part 98 formed Saugventilan Aunt. On with the embodiment of Fig. 2 and also from Fig. 1 matching aspects will not be discussed further below.
  • a plurality of circumferentially distributed passages are formed, each comprising an obliquely to the longitudinal axis or axis of movement 70 of the plunger 12 extending channel 52 and the channel 52 vorströmseifig vorgelagig pre-chamber 51.
  • the free flow cross-section of the pre-chambers 51 is greater than that of the straight channels 52.
  • the pre-chambers 51 each have rounded inner surfaces.
  • FIG. 2 Another difference from the embodiment of Fig. 2 is that the suction valve plate 24 surrounding head portion 98 is secured by a screw 97.
  • the plunger 12 is also provided with channels 52 and antechamber 51 existing passages.
  • the facing sides of the plunger 12 and the Saugventilplatte 24 complementary to each other are curved such that they each have an approximately spherical shape.
  • the suction valve plate 24 is concave and the plunger 12 is convexly curved, so that the plunger 12 is located with its central portion closer to the pressure valve element 20 than in the embodiment of Fig. 3 , Accordingly, the axial extent of the screw head portion 26 with respect to the embodiment of Fig. 3 increased.
  • Fig. 5a schematically shows how a pump according to the invention, the three juxtaposed, a common drive unit 80 having delivery arrangements is operated in a liquid delivery mode.
  • the two in Fig. 5a lower conveyor arrangements have only either an inlet opening 16 or an outlet opening 22 and are in the housing interior by in Fig. 5a only indicated channels 11 on the input side and output connected to each other.
  • the third, upper conveyor assembly has both its own inlet opening 16 and its own outlet opening 22.
  • the three conveying arrangements are connected to a common suction line 72 and the liquid conveyed via the suction line 72 is transported away via a common pressure line 74.
  • a common suction line 72 In the liquid conveying mode, the three conveying arrangements are connected to a common suction line 72 and the liquid conveyed via the suction line 72 is transported away via a common pressure line 74.
  • two non-interconnected suction lines 72 and pressure lines 74 may be provided.
  • the quantities of gas delivered by the two conveying arrangements of the first stage are thus jointly compressed in the second stage and removed via the pressure line 74 of the second stage forming conveyor arrangement.
  • each cylinder 10 serves to dissipate the heat generated during the compression of the gas.
  • a coolant pumped through the spiral groove 48 via the inlet 47 and one at the other end of the spiral groove 48th arranged, not shown outlet a coolant pumped through the spiral groove 48.
  • Fig. 5c shows in a common representation both the liquid delivery mode and the gas delivery mode and the arrangement of valves M1, M2, M3 and M4 in the respective lines. While in the liquid conveying mode the valves M1, M2 are closed and the valves M3, M4 are open, the gas delivery mode is characterized in that the valves M1, M2 are opened and the valves M3, M4 are closed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Compressor (AREA)
  • Reciprocating Pumps (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Eye Examination Apparatus (AREA)
  • Fluid-Pressure Circuits (AREA)
  • External Artificial Organs (AREA)

Claims (13)

  1. Pompe comprenant au moins un dispositif transporteur, qui comporte un piston plongeur (12) guidé axialement dans un cylindre (10), lequel piston modifie avec son extrémité éloignée de l'entraînement le volume dans une chambre sous pression (14), laquelle communique lors de la course d'aspiration avec au moins une ouverture d'entrée (16) placée sur le côté, opposé à la chambre sous pression (14), du piston plongeur (12) et communique lors de la course de refoulement au moyen d'un dispositif de soupape de refoulement (18, 20) avec au moins une ouverture de sortie (22),
    le piston plongeur (12) portant sur son extrémité éloignée de l'entraînement un agencement de soupape d'aspiration (24, 98), qui comporte une partie supérieure (98) reliée axialement de façon fixe à une tige de piston (28) et une plaque de soupape d'aspiration (24) librement mobile axialement entre le piston plongeur (12) et la partie supérieure (98), laquelle plaque libère, lors de la course d'aspiration en s'appliquant sur la partie supérieure (98), une liaison d'écoulement fermée lors de la course de refoulement allant de l'ouverture d'entrée (16) à la chambre sous pression (14) en passant par le piston plongeur (12), l'agencement de soupape de refoulement (18, 20) comportant un corps de soupape de refoulement (18) limitant au moins par endroits la chambre sous pression (14) et un élément de soupape de refoulement (20), qui est prétendu pendant la course d'aspiration contre le côté, opposé à la chambre sous pression (14), du corps de soupape de refoulement (18) et libère au moins une liaison fluidique de la chambre sous pression (14) à l'ouverture de sortie (22) à partir d'une pression générée pendant la course de refoulement dans la chambre sous pression (14),
    caractérisé
    en ce que l'élément de soupape de refoulement (20), de préférence en forme de calotte, dépasse, lors de la course de refoulement, du côté, tourné vers l'agencement de soupape d'aspiration (24, 98), du corps de soupape de refoulement (18) et dépasse à l'intérieur de la chambre sous pression (14), et
    en ce que la plaque de soupape d'aspiration (24) présente une ouverture (99) centrale qui forme un composant de la liaison d'écoulement allant dans la chambre sous pression (14) et dans laquelle l'élément de soupape de refoulement (20) dépasse à la fin de la course de refoulement.
  2. Pompe selon la revendication 1,
    caractérisée en ce que le piston plongeur (12) est logé de façon mobile au moins dans une faible proportion pour le centrage dans le cylindre (10) sur la tige de piston (28).
  3. Pompe selon au moins l'une des revendications précédentes, caractérisée en ce que des faces avant, délimitant la chambre sous pression (14), de l'agencement de soupape d'aspiration (24, 26 ; 24, 98) et de l'agencement de soupape de refoulement (18, 20) sont rapprochées les unes des autres sans contact à la fin de la course de refoulement de telle sorte que le volume de la chambre sous pression (14) est réduit à une valeur négligeable par rapport à la valeur maximale à la fin de la course d'aspiration et de préférence approximativement à zéro,
    et/ou en ce que la distance minimale entre des faces avant tournées les unes vers les autres, de l'agencement de soupape de refoulement (18, 20) et de l'agencement de soupape d'aspiration (24, 26 ; 24, 98) est inférieure à 1 mm et se situe de préférence dans la plage allant de 0,1 à 0,2 mm.
  4. Pompe selon au moins l'une des revendications précédentes, caractérisée en ce que la partie supérieure (98) est conçue comme élément annulaire entourant la plaque de soupape d'aspiration (24) et reliée axialement de façon fixe, en particulier pouvant être vissée avec la face avant, éloignée de l'entraînement, du piston plongeur (12).
  5. Pompe selon au moins l'une des revendications précédentes, caractérisée en ce qu'au moins un passage (51, 52) débouchant lors de la course d'aspiration dans la chambre sous pression (14) est réalisé dans le piston plongeur (12), lequel passage est agencé au moins par endroits en biais par rapport à l'axe de déplacement (70) du piston plongeur (12), et/ou en ce qu'au moins un passage (51, 52) réalisé dans le piston plongeur (12) comporte un canal (52) débouchant dans la chambre sous pression (14) et une préchambre (51) placée en amont du canal (52) côté entrée avec une section d'écoulement libre agrandie par rapport au canal (52).
  6. Pompe selon au moins l'une des revendications précédentes, caractérisée en ce que les côtés, tournés les uns vers les autres, du piston plongeur (12) et de la plaque de soupape d'aspiration (24) sont incurvés de façon complémentaire les uns par rapport aux autres et présentent en particulier un tracé au moins approximativement sphérique, le piston plongeur (12) étant incurvé de préférence de façon convexe et la plaque de soupape d'aspiration (24) étant incurvée de préférence de façon concave.
  7. Pompe selon au moins l'une des revendications précédentes, caractérisée en ce que la plaque de soupape d'aspiration (24) est conçue avec une forme annulaire et est disposée de préférence dans la direction radiale de façon très ajustée sur la partie supérieure (26),
    en particulier le diamètre extérieur de la plaque de soupape d'aspiration (24) étant inférieur au diamètre intérieur du cylindre (10),
    et/ou en ce que le côté, tourné vers le piston plongeur (12), de la plaque de soupape d'aspiration (24) est réalisé en forme de cône et s'applique lors de la course de refoulement de façon étanche sur des parois latérales, agencées en biais par rapport à l'axe longitudinal (70) du cylindre (10), d'un évidement (90) du piston plongeur (12), dans lequel débouche au moins un alésage axial (52) du piston plongeur (12),
    et/ou en ce que des côtés, tournés vers l'agencement de soupape de refoulement (18, 20) de la plaque de soupape d'aspiration (24) et de la partie supérieure (26) forment ensemble, lors de la course de refoulement, un côté avant, au moins sensiblement plan, de l'agencement de soupape d'aspiration (24, 26).
  8. Pompe selon au moins l'une des revendications précédentes, caractérisée en ce que la plaque de soupape d'aspiration (24) et la partie supérieure (26 ; 98) sont dotées de parties de bride (24a, 26a ; 24a, 98a) se chevauchant dans le sens radial.
  9. Pompe selon au moins l'une des revendications précédentes, caractérisée en ce que la chambre sous pression (14) est étanchée par rapport au côté aspiration par le piston plongeur (12),
    en particulier le piston plongeur (12) comprenant au moins un évidement périphérique (30) de préférence en forme de rainure, dans lequel est disposé un joint (31, 33) de préférence au moins en partie à base de Téflon ou de PEEK,
    en particulier au moins un joint comportant une bague d'étanchéité à glissement (31),
    et/ou en ce qu'au moins un joint est prétendu de préférence au moyen d'un joint torique (33) disposé dans l'évidement périphérique (30), élastiquement déformable, en direction de la paroi intérieure du cylindre.
  10. Pompe selon au moins l'une des revendications précédentes, caractérisée en ce que le cylindre (10) est fabriqué en aluminium, la paroi intérieure du cylindre étant de préférence à base d'oxyde d'aluminium formé en particulier par une transformation avec couche dure, ou en ce que le cylindre (10) est fabriqué à base d'acier en particulier trempé, la paroi intérieure du cylindre étant dotée de préférence d'une couche superficielle supplémentaire, en particulier d'une couche superficielle CVD ou PVD,
    et/ou des particules de Téflon sont intégrées dans la paroi intérieure du cylindre, en particulier dans l'oxyde d'aluminium formant la paroi intérieure du cylindre,
    et/ou en ce qu'au moins la plaque de soupape d'aspiration (24) de l'agencement de soupape d'aspiration est fabriquée à base d'un plastique en particulier résistant aux températures élevées et/ou résilient, de préférence en PEEK,
    et/ou en ce qu'au moins un élément de soupape de refoulement (20) de l'agencement de soupape de refoulement (18, 20) est fabriqué à base d'un plastique en particulier résistant aux températures élevées et résilient, de préférence à base de PEEK.
  11. Pompe selon au moins l'une des revendications précédentes, caractérisée en ce que la tige de piston (28) s'étend à travers un espace de transport (32) communiquant avec l'ouverture d'entrée (16) et est entourée à l'extérieur de l'espace de transport (32) d'un élément de centrage (34) de forme annulaire, dont la surface intérieure tournée vers la tige de piston (28) est dotée d'au moins un joint (38) disposé dans un évidement annulaire (36), à base de préférence au moins en partie de Téflon ou de PEEK,
    en particulier au moins un joint (38) comprenant une bague d'étanchéité à glissement,
    et/ou en ce qu'au moins un joint (38) est prétendu de préférence au moyen d'un ressort en acier en direction de la tige de piston (28),
    et/ou en ce que l'élément de centrage (34) est disposé entre un élément de retenue (40) et le cylindre (10), de préférence un carter d'aspiration (42) se raccordant côté entraînement au cylindre (10) et centré de préférence au moyen de l'élément de centrage (34),
    et/ou en ce que l'élément de centrage (34), le cylindre (10) et l'agencement de soupape de refoulement (18, 20) sont serrés entre l'élément de retenue (40) et un carter de pression (44) au moyen d'au moins un assemblage vissé (46) dans la direction axiale.
  12. Pompe selon au moins l'une des revendications précédentes,
    caractérisée en ce qu'au moins un espace réfrigérant (48) formant une partie d'un circuit réfrigérant pouvant être exploité de préférence avec de l'eau est présent au moins entre un carter de pression (44) et une zone, entourée par le carter de pression (44), du cylindre (10),
    en particulier l'espace réfrigérant étant prévu sous la forme d'au moins une rainure en spirale (48) formée sur la surface extérieure du cylindre (10).
  13. Pompe selon au moins l'une des revendications précédentes, caractérisée en ce qu'elle comporte plusieurs agencements de transport qui sont de préférence au moins pratiquement identiques et peut être utilisée par la liaison de l'ouverture d'entrée (16) d'au moins un agencement de transport avec l'ouverture de sortie (22) d'au moins un autre agencement de transport sous forme de compresseur à plusieurs niveaux, en particulier pour le transport de fluides gazeux,
    en particulier trois agencements de transport avec des axes longitudinaux (70) disposés de préférence à peu près dans un plan étant prévus, chaque ouverture d'entrée (16) étant reliée à une conduite d'aspiration (72) dans un mode de transport de liquide et chaque ouverture de sortie (22) étant reliée à une conduite de refoulement (74) et une ouverture d'entrée (16) étant reliée à deux ouvertures de sortie (22) dans un mode de transport de gaz,
    et/ou en ce qu'au moins deux agencements de transport présentent une unique ouverture d'entrée (16) commune et/ou une unique ouverture de sortie (22) commune.
EP00108472A 1999-04-22 2000-04-18 Soupape d'admission d'une pompe Expired - Lifetime EP1046816B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19918394 1999-04-22
DE19918394A DE19918394A1 (de) 1999-04-22 1999-04-22 Pumpe

Publications (3)

Publication Number Publication Date
EP1046816A2 EP1046816A2 (fr) 2000-10-25
EP1046816A3 EP1046816A3 (fr) 2001-10-10
EP1046816B1 true EP1046816B1 (fr) 2009-01-28

Family

ID=7905571

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00108472A Expired - Lifetime EP1046816B1 (fr) 1999-04-22 2000-04-18 Soupape d'admission d'une pompe

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EP (1) EP1046816B1 (fr)
AT (1) ATE422027T1 (fr)
DE (2) DE19918394A1 (fr)
DK (1) DK1046816T3 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10106873B4 (de) * 2001-01-23 2006-01-26 Brueninghaus Hydromatik Gmbh Zylindertrommel für hydrostatische Axialkolbenmaschinen
JP2003184703A (ja) * 2001-12-21 2003-07-03 Bosch Automotive Systems Corp 燃料供給ポンプ
ITMI20012824A1 (it) * 2001-12-28 2003-06-28 Nuovo Pignone Spa Materiale plastico autolubrificante per elementi di tenuta
RU2451831C2 (ru) * 2009-02-27 2012-05-27 Владимир Алексеевич Преображенский Двойной цилиндропоршневой блок высокого давления
DE102009021170A1 (de) 2009-05-13 2010-12-16 Compart Compressor Technology Gmbh Zylinder- und Kolbenstangenabdichtung eines Linearverdichters

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US3446156A (en) * 1966-11-17 1969-05-27 Cosmodyne Corp The Differential pressure poppet valve
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US5174735A (en) * 1991-04-16 1992-12-29 Tecumseh Products Company Low reexpansion valve system
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DE9314328U1 (de) * 1993-09-22 1993-12-02 Saxlund Gmbh, 29614 Soltau Schwimmende Kolbenführung in Dickstoffpumpen
US5476371A (en) * 1994-06-08 1995-12-19 Tecumseh Products Company Compressor suction valve of toroidal shape with a radial finger
US5658134A (en) * 1995-07-26 1997-08-19 J-Operating Company Compressor with suction valve in piston

Also Published As

Publication number Publication date
ATE422027T1 (de) 2009-02-15
EP1046816A2 (fr) 2000-10-25
DK1046816T3 (da) 2009-05-11
EP1046816A3 (fr) 2001-10-10
DE50015536D1 (de) 2009-03-19
DE19918394A1 (de) 2000-10-26

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