EP1046816A2 - Soupape d'admission d'une pompe - Google Patents

Soupape d'admission d'une pompe Download PDF

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Publication number
EP1046816A2
EP1046816A2 EP00108472A EP00108472A EP1046816A2 EP 1046816 A2 EP1046816 A2 EP 1046816A2 EP 00108472 A EP00108472 A EP 00108472A EP 00108472 A EP00108472 A EP 00108472A EP 1046816 A2 EP1046816 A2 EP 1046816A2
Authority
EP
European Patent Office
Prior art keywords
pressure
plunger
suction
cylinder
suction valve
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.)
Granted
Application number
EP00108472A
Other languages
German (de)
English (en)
Other versions
EP1046816A3 (fr
EP1046816B1 (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
Application filed by Speck-Kolbenpumpenfabrik Otto Speck & Co KG GmbH filed Critical Speck-Kolbenpumpenfabrik Otto Speck & Co KG GmbH
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
Expired - Lifetime 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
    • 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 delivery arrangement, which comprises a plunger axially guided in a cylinder, which with the far end of the drive varies the volume in a pressure chamber, that during the suction stroke with at least one on the opposite side of the pressure chamber Side of the plunger and during the pressure stroke via a pressure valve arrangement with at least one Exhaust port communicates.
  • Such pumps are for example from US 3,920,356, the US 3,809,508 and US 3,652,188.
  • a pump of the type mentioned in the introduction even with high pumping power and when operating at high speeds, especially with regard to Sealing of the plunger in the cylinder works trouble-free, versatile can be used and in particular also for the promotion of gaseous Condition present media can be used.
  • the plunger on its drive remote End carries a suction valve assembly that is axially fixed to a piston rod connected headboard and one between the plunger and the head part comprises axially freely movable suction valve plate, which at Suction stroke on the head part, a flow connection closed during the pressure stroke from the inlet opening over the plunger into the Releases the pressure chamber.
  • suction valve assembly according to the invention an optimal seal between the cylinder inner wall and the free end of the plunger attached to the piston rod can be achieved, the trouble-free and low wear Operation of the pump over long periods of time is permitted and in particular allows the pressure chamber opposite the inlet opening during the pressure stroke or a delivery chamber into which the inlet opening opens, too seal securely when conveying gaseous media.
  • the invention Provide the axially freely movable suction valve plate between the plunger and the headboard take care of the start of the suction stroke for releasing the flow connection from the inlet opening into the pressure chamber solely due to the inertia of the suction valve plate, which is particularly advantageous when pumping gaseous media.
  • Plunger at least one opening into the pressure chamber during the suction stroke Passage formed, which is at least partially oblique to The axis of movement of the plunger runs.
  • This passage can be one channel opening into the pressure chamber and one on the inflow side upstream antechamber with enlarged compared to the channel include free flow cross section.
  • the Plunger for centering in the cylinder on the piston rod at least movably supported to a small extent.
  • Storage is preferred of the plunger designed such that at least a small given axial mobility of the plunger relative to the piston rod is.
  • the plunger in the cylinder can in particular ensuring trouble-free operation with regard to the sealing effect Align way optimally, creating tolerances regarding the guidance of the piston rod can be compensated.
  • the possibility the self-adjustment of the plunger in the cylinder reduces the Wear of the seals used and thus increases while remaining the same good sealing properties the life of the pump.
  • the plunger is preferably with at least one peripheral recess provided, in which a seal is arranged, which in a particularly preferred variant as a sealing ring made of Teflon is trained.
  • a seal is arranged, which in a particularly preferred variant as a sealing ring made of Teflon is trained.
  • the mechanical seal can be used an elastically deformable, between the bottom of the peripheral recess and the O-ring arranged in the direction of the cylinder inner wall be biased. In this way, an optimal Sealing effect achieved with low frictional resistance.
  • the pressure chamber is sealed via the suction valve plate, which during the pressure stroke, e.g. in the form of axial bores or of passages in the plunger running obliquely to the longitudinal axis closes the existing flow connection into the pressure chamber.
  • the cylinder is made of aluminum manufactured, the cylinder inner wall made by a suitable Conversion process is made of alumina. In the alumina Teflon particles can also be embedded.
  • the cylinder inner wall with an additional Surface layer, in particular a CVD or PVD surface layer, is provided.
  • an additional Surface layer in particular a CVD or PVD surface layer
  • Hardened steel of hardness 62 HRC can be provided with an additional CVD or PVD surface layer is provided. This can a hardness of 2400 HV can be achieved.
  • the cylinder surface be extremely finely polished. The wear on the cylinder wall and these measures significantly reduce the seals.
  • the end faces of the suction valve arrangement which delimit the pressure chamber and the pressure valve arrangement at the end of the pressure stroke in such a contactless manner approximated that the volume of the pressure chamber on one negligible compared to the maximum value at the end of the suction stroke small value and preferably approximately reduced to zero.
  • the minimum distance between each other facing end faces of the pressure valve arrangement and the suction valve arrangement less than 1 mm and is preferably in the range of 0.1 to 0.2 mm.
  • the pump by providing a larger one Number of delivery arrangements the pump also as a three or more stages Compressor operated.
  • the pump according to the invention is also suitable in the gaseous state especially for use with carbon dioxide.
  • Fig. 1 shows part of a pump according to an embodiment of the invention with three conveyor arrangements, the longitudinal axes 70 in one plane lie.
  • the conveyor arrangements are identical in construction and have each have a piston rod 28 which, via a common drive Execution of axial back and forth movements in a respective cylinder 10 are driven.
  • a common drive unit for the conveyor arrangements is not shown in Fig. 1.
  • a centering element - from left to right in FIG. 1 34 an inlet channel running perpendicular to the longitudinal axis 70 15 having suction housing 42, the cylinder 10 and a pressure valve body 18 of a pressure valve arrangement by means of screw connections 46 clamped.
  • the suction housing 42, the cylinder 10 and a plunger 12 delimit a conveying space 32 into which an inlet opening 16 having inlet channel 15 opens.
  • At the inlet opening 16 is one Suction line, not shown, can be connected.
  • a radially protruding, circumferential collar 18a of the pressure valve body 18 is between the remote end of the cylinder 10 and the Pressure housing 44 clamped.
  • the drive end of the cylinder 10 lies against a shoulder 45 of the suction housing 42.
  • An exit opening for the piston rod 28 from the delivery chamber 32 is by a radial inwardly projecting collar 43 of the suction housing 42 is limited.
  • a collar is located on the collar 43 of the suction housing 42 Ring portion of the centering element 34, of which the piston rod 28 facing inner surface with ring recesses 36 for seals 31, 96 is provided.
  • One of the ring recesses 36 is made of Teflon Manufactured sliding seal 31 arranged, the additional example biased towards the piston rod 28 by means of a stainless steel spring could be. Instead of Teflon could also be a high temperature resistant and impact-resistant plastic such as PEEK for the mechanical seal 31 be used.
  • the centering element 34 is located on the drive side Shoulder 41 of the holding element 40. Through the centering element 34 centered the suction housing 42 for driving.
  • the plunger 12 is via a screw 27, the head of one Head part 26 is formed, held at the free end of the piston rod 28, in such a way that the plunger 12 inserted on the screw 27 to a small extent in the axial direction relative to the piston rod 28 is mobile. In this way, the can fit in essentially Plunger 12 inserted into cylinder 10 at least to a certain extent Align degrees independently of piston rod 28 in cylinder 10.
  • the head part firmly screwed to the piston rod 28 in the axial direction 26 has a pin 26b and a flange portion 26a which flush on the side of the head part 26 facing away from the piston rod 28 ends with the pin 26b and thus forms a flat end face.
  • the pin 26b acts with an annular projection 12a of the plunger 12 together to the plunger 12 on the piston rod 28 hold.
  • the screw 27 can be recessed 26c in the head part 26 be rotated using an appropriate tool.
  • the recesses 26c can be closed by means of plugs, which is advantageous Way the dead space is minimized.
  • the plugs for the Recesses 26c are made of a temperature-resistant material, for example Made of plastic.
  • An annular suction valve plate 24 is arranged on the head part 26, whose outer diameter is smaller than the inner diameter of the cylinder 10 is.
  • the resulting space between the outer edge the suction valve plate 24 and the cylinder inner wall is part of one another Place pressure chamber 14 described in more detail.
  • the suction valve plate 24 and the head part 26 are radial with each other Provided towards overlapping flange portions 24a, 26a, the Suction valve plate 24 with a ring portion 24b on the flange portion 26a of the head part 26 is slidably mounted.
  • the plunger 12 has a recess 90 in the form of a radial limited by side walls extending obliquely to the longitudinal axis 70 Provided ring channel.
  • Axial bores 52 open into the recess 90 of the plunger 12.
  • the side of the plunger 12 facing the Suction valve plate 24 is conical in such a way that - accordingly 1 - during the pressure stroke, the recess 90 fills and seals against their sloping side walls, whereby annular sealing elements 92 are provided for sealing.
  • the sum of the axial heights of the flange portions 24a, 26a of the suction valve plate 24 or the head part 26 is smaller than the axial height of the the plunger 12 protruding part of the pin 26b.
  • the suction valve plate 24 between the head part 26 and the plunger 12 freely movable axially. Between those overlapping in the radial direction Flange sections 24a, 26a is in the state according to FIG. 1 Gap or space 50 present.
  • Fig. 1 shows the plunger 12 and that of the suction valve plate 24 and the suction valve assembly formed at the top dead center, i.e. at the end of the print stroke.
  • the suction valve plate 24 is located on the plunger 12 and fills the recess 90 such that the axial bores 52 in the plunger 12, the radially outside of the tapered end the piston rod 28 open into the delivery chamber 32, through the suction valve plate 24 are closed. It therefore exists during the pressure stroke no flow connection between the axial bores 52 in Plunger 12 and the annular space between the Outer edge of the suction valve plate 24 and the cylinder inner wall.
  • the suction valve arrangement 24, 26 At the top dead center shown in Fig. 1, the suction valve arrangement 24, 26 a flat end face running perpendicular to the longitudinal axis 70 on that of the sides of the head part facing away from the piston rod 28 26 and the suction valve plate 24 is formed.
  • the conveyor arrangement is designed so that the top of the suction valve assembly at top dead center 24, 26 so close to that facing the suction valve arrangement 24, 26 Front side of the pressure valve arrangement - described in more detail below 18, 20 has approached that a very small, in Fig. 1 not There is a recognizable axial space between the two end faces which is part of the pressure chamber minimized in this state 14 of the conveyor assembly forms.
  • the pressure chamber 14 At top dead center is the pressure chamber 14 thus essentially through the annular space between the outer edge of the suction valve plate 24 and the cylinder inner wall educated.
  • the distance between the two indicated by an "A" in FIG facing end faces of the suction valve arrangement 24, 26 and the pressure valve arrangement 18, 20 at top dead center is about 0.1 to 0.2 mm, so that the end faces do not touch.
  • the pressure valve body 18 is part of a pressure valve assembly, which also a pressure valve element 20, which has approximately the shape of a spherical cap with cut cap and against a coil spring 21 the side of the pressure valve body pointing away from the pressure chamber 14 18 is biased.
  • the spring 21 is supported on a sleeve-shaped Support element 13, which is screwed to the pressure valve body 18 and communicates with the outlet space 23 via openings in the side wall.
  • a central opening 61 is formed, the Boundary surface in the direction of the outlet space 23 accordingly the shape of the pressure valve element 20 funnel-shaped and expanded this way forms a valve seat.
  • the pressure valve arrangement 18, 20 is dimensioned such that in the closed 1 the suction valve arrangement 24, 26 facing from the pressure valve body 18 and from the pressure valve element 20 together formed end face - in the variant explained below with bevel 94 is only approximate - flat surface that runs perpendicular to the longitudinal axis 70.
  • the end face of the pressure valve body 18 can be chamfered 1, as indicated by broken lines 94 in FIG. 1, the illustration is exaggerated for clarity.
  • the bevel is a wedge-shaped, slightly in the direction of the longitudinal axis 70 widening annular gap between the opposite End faces of the suction valve arrangement 24, 26 and the pressure valve arrangement 18, 20 present. In this way it is ensured that when Pressure stroke liquid in the direction of the longitudinal axis 70 and through the opening 61 flows without congestion or blocking the piston assembly due to the liquid present between the end faces cause.
  • the area of the cylinder 10 surrounded by the pressure housing 44 is marked with a Spiral groove 48 provided, via an inlet 47 with a cooling fluid, for which water is preferably used can be supplied.
  • a cooling fluid for which water is preferably used can be supplied.
  • the cylinder 10 is on its outside provided with cooling fins 49.
  • the seal between suction housing 42 and centering element 34, between Suction housing 42 and cylinder 10 and between pressure housing 44, Cylinder 10 and pressure valve body 18 are made by corresponding O-rings 60 arranged in circumferential recesses.
  • the plunger 12 is provided with groove-shaped circumferential recesses 30, in which mechanical seals 31 made of Teflon are arranged, instead of Teflon also a high temperature resistant one and impact-resistant plastic, for example PEEK, can be used could.
  • Teflon also a high temperature resistant one and impact-resistant plastic, for example PEEK, can be used could.
  • PEEK a high temperature resistant one and impact-resistant plastic
  • the cylinder 10 is made of aluminum produced, wherein the cylinder inner wall consists of aluminum oxide, the through a conversion process, e.g. a hard coat conversion the cylinder inner wall is generated. Furthermore, there are the cylinder inner wall forming aluminum oxide teflon particles.
  • the cylinder can alternatively also be made of hardened steel e.g. hardness 62 HRC manufactured and 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 manufactured. Basically, other, especially high temperature resistant, can also be used and / or impact-resistant, plastic materials are used become.
  • the delivery arrangement according to the invention is used to deliver fluids Suitable both in the liquid and in the gaseous state.
  • the plunger 12 moves together with the suction valve assembly 24, 26 in Fig. 1 to the left, so that the axially freely movable Suction valve plate 24 abuts the head part 26, i.e. the gap 50 no longer is available.
  • Pressure chamber 14 filled with liquid or gaseous fluid that over a suction line, not shown, coupled to the inlet opening 16, the inlet channel 15, the delivery chamber 32 and the plunger 12 and the suction valve assembly 24, 26 can flow.
  • a flow connection from the pressure chamber 14 into the outlet space 23 through the opening 61 of the pressure valve body 18 is through the pressure valve element 20 closed by means of the spring 21 on the side as a valve seat serving pressure valve body 18 is pressed.
  • the suction valve arrangement 24, 26 automatically due to the free axial mobility of the Suction valve plate 24 switched to a pressure mode in which the Suction valve plate 24 on plunger 12 filling recess 90 abuts and - as shown in Fig. 1 - the axial bores 52 in the plunger 12 closes.
  • the conveyor arrangement according to the invention is advantageously optimized for dead space, since at the end of the pressure stroke, the pressure chamber 14 only from the annular space between the outer edge of the suction valve plate 24 and the cylinder inner wall as well as the minimal Gap at "A" in Fig. 1 between the flat end faces of the suction valve assembly 24, 26 and the pressure valve arrangement 18, 20 is formed.
  • the recesses 26c are - as mentioned - after the assembly - Not shown in Fig. 1 - Plug elements, so that the Recesses 26c do not contribute to the pressure chamber 14.
  • the dead space optimization according to the invention also has in particular Conveying gaseous media results in very good efficiency.
  • Fig. 2 of an inventive Pump differs from that of FIG. 1 in particular by the formation of the plunger 12 and that of the suction valve plate 24 and a head part 98 formed suction valve assembly. This is also valid for the Fig. 3 and 4 described in more detail elsewhere Aspects corresponding to the exemplary embodiment of FIG. 1 are described in not discussed in more detail below.
  • the suction valve plate 24 is annular Surround headboard 98, again in the radial direction overlapping flange sections 24a, 98a are provided.
  • the headboard 98 is with a sleeve portion 98b on one of the drive distant End face of the plunger 12 axially projecting ring portion 12b screwed and with a flange portion 98a on a ring portion 24b of the suction valve plate 24 is axially displaceable.
  • Flange section 24a is the suction valve plate 24 on the inside of the Ring section 12b of the plunger 12.
  • the axial mobility of the suction valve plate 24 is corresponding to that Embodiment of Fig. 1 ensured by the gap 50, which during of the pressure stroke between those overlapping in the radial direction Flange sections 24a, 98a is present.
  • Both ends of the suction valve plate 24 and the plunger 12 are flat and run perpendicular to the longitudinal axis 70. Also in this Embodiment can the pressure valve body 18 with a - by the dashed Lines indicated - bevel 94. In the 2 at the end of the pressure stroke are the axial bores 52 in the plunger 12 closed by the suction valve plate 24.
  • the suction valve plate 24 has a central opening 99, the diameter of which is slightly larger than that of the head part 26 of the screw 27, in this embodiment, flush with the end face of the plunger 12 completes. This protrudes into opening 99 - its closed position engaging - pressure valve element 20, which in this embodiment is designed as a full cap.
  • Both liquid and gaseous media can be used during the suction stroke via the delivery chamber 32, the axial bores 52 in the plunger 12, a gap that does not exist in the state of FIG. 2 the plunger 12 and the suction valve plate 24 and the opening 99 flow into the pressure chamber 14.
  • Fig. 2 Not shown in Fig. 2 are plug elements that are made after assembly be inserted into the recesses 26c of the screw head part 26 and fill the opening 99 so that during the suction stroke fluid flow from the axial bores 52 through the opening 99 in the pressure chamber 14 is possible, but during the pressure stroke Pressure chamber 14 essentially by that indicated in Fig. 2 by an "A" Gap between the suction valve plate 24 and the pressure valve body 18 is formed.
  • the distance between the facing each other The end faces of these two components is approximately at the end of the pressure stroke 0.1 to 0.2 mm.
  • the conveyor arrangement according to the invention is also in this way of Fig. 2 advantageously optimized dead space and for promotion gaseous media with high efficiency ideally suited.
  • FIG. 3 and 4 each show a further development of that shown in FIG. 2 Pump.
  • the differences are particularly in the training of the plunger 12 and that of the suction valve plate 24 and the Head part 98 formed suction valve assembly.
  • Fig. 2 and also of Fig. 1 coinciding aspects will not be discussed in more detail below.
  • the plunger 12 formed in the circumferential direction arranged passages, the one at an angle to the longitudinal axis or axis of movement 70 of the plunger 12 extending channel 52 and one inflow soapy channel 52 include upstream antechamber 51.
  • the free flow cross section the antechamber 51 is larger than that of the straight channels 52.
  • the antechambers 51 each have rounded inner surfaces.
  • FIG. 2 Another difference from the embodiment of FIG. 2 is that the head part 98 surrounding the suction valve plate 24 by means of a Screw 97 is secured.
  • the plunger 12 is also included passages consisting of channels 52 and antechambers 51.
  • Fig. 5a shows schematically how a pump according to the invention, the three side by side arranged, having a common drive unit 80 Includes conveyor arrangements operated in a liquid delivery mode becomes.
  • the two lower conveyor arrangements in FIG. 5a only have either an inlet opening 16 or an outlet opening 22 on and are inside the housing by channels 11, which are only indicated in FIG. 5a connected on the input side and output side.
  • the third, upper Conveyor arrangement has both its own inlet opening 16 and its own outlet opening 22.
  • the three delivery arrangements are on a common one Suction line 72 is connected and is via the suction line 72 transported liquid transported away via a common pressure line 74.
  • a common pressure line 74 may be provided.
  • the common pressure line 74 of the two lower in Fig. 5b Conveyor arrangements to the inlet opening 16 of the upper conveyor arrangement in FIG. 5b connected.
  • the gaseous medium for example carbon dioxide, which via the to the inlet opening 16 of the lower conveyor assembly connected common suction line 72 is conveyed, is after the exit from the two lower conveyor arrangements formed first stage of the pump of the third, upper conveyor arrangement fed.
  • the third conveyor arrangement forms the second stage of the in this gas delivery mode as a compressor pump.
  • the quantities of gas delivered by the two delivery arrangements of the first stage are thus compressed together in the second stage and via the pressure line 74 of the conveyor arrangement forming the second stage transported away.
  • the one provided with a spiral groove 48 serving as a cooling space, in the flow direction front area of each cylinder 10 (see. Fig. 1-4) is used Dissipation of the heat generated during the compression of the gas. For this is via the inlet 47 and one at the other end of the spiral groove 48th arranged, not shown outlet, a coolant through the spiral groove 48 pumped.
  • the connecting lines between the funding arrangements forming the second stage and the to provide the second stage forming conveyor assembly with a cooling jacket are preferably provided.
  • 5c shows in a common representation both the liquid delivery mode as well as the gas production mode and the arrangement of Valves M1, M2, M3 and M4 in the respective lines. While in Liquid delivery mode, the valves M1, M2 closed and the valves M3, M4 are open, the gas production mode is characterized by that the valves M1, M2 are open 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)
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 true EP1046816A2 (fr) 2000-10-25
EP1046816A3 EP1046816A3 (fr) 2001-10-10
EP1046816B1 EP1046816B1 (fr) 2009-01-28

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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

Country Status (4)

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

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003056176A1 (fr) * 2001-12-28 2003-07-10 Nuovo Pignone Holding S.P.A. Matiere plastique autolubrifiante pour elements d'etancheite
EP1321672A3 (fr) * 2001-12-21 2003-12-03 Bosch Automotive Systems Corporation Pompe à carburant

Families Citing this family (3)

* 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
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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US5174735A (en) * 1991-04-16 1992-12-29 Tecumseh Products Company Low reexpansion valve system
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US2694607A (en) * 1949-07-13 1954-11-16 Int Harvester Co Connecting rod and piston assembly
US3036873A (en) * 1961-09-13 1962-05-29 Kimwood Machine Co Piston and piston rod connection
US4368755A (en) * 1978-12-20 1983-01-18 Copeland Corporation Valve assembly
US4284391A (en) * 1979-10-01 1981-08-18 Acf Industries, Inc. Crashworthy fuel pump improvement
US5106278A (en) * 1988-09-21 1992-04-21 Bristol Compressors, Inc. Refrigerant gas compressor construction
DE3901058A1 (de) * 1989-01-16 1990-07-19 Paul Hammelmann Hochdruckkolbenpumpe mit hoher saugleistung
US5174735A (en) * 1991-04-16 1992-12-29 Tecumseh Products Company Low reexpansion valve system
US5346373A (en) * 1993-06-17 1994-09-13 White Consolidated Industries, Inc. Refrigeration compressor having a spherical discharge valve
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

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EP1321672A3 (fr) * 2001-12-21 2003-12-03 Bosch Automotive Systems Corporation Pompe à carburant
WO2003056176A1 (fr) * 2001-12-28 2003-07-10 Nuovo Pignone Holding S.P.A. Matiere plastique autolubrifiante pour elements d'etancheite

Also Published As

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ATE422027T1 (de) 2009-02-15
DK1046816T3 (da) 2009-05-11
EP1046816A3 (fr) 2001-10-10
DE50015536D1 (de) 2009-03-19
EP1046816B1 (fr) 2009-01-28
DE19918394A1 (de) 2000-10-26

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