EP0346285B1 - Dispositif de clapet - Google Patents

Dispositif de clapet Download PDF

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Publication number
EP0346285B1
EP0346285B1 EP89810419A EP89810419A EP0346285B1 EP 0346285 B1 EP0346285 B1 EP 0346285B1 EP 89810419 A EP89810419 A EP 89810419A EP 89810419 A EP89810419 A EP 89810419A EP 0346285 B1 EP0346285 B1 EP 0346285B1
Authority
EP
European Patent Office
Prior art keywords
valve
lid
valve arrangement
arrangement according
diaphragm
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
EP89810419A
Other languages
German (de)
English (en)
Other versions
EP0346285A1 (fr
Inventor
Heinz Baumann
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.)
Atlas Copco Schweiz AG
Original Assignee
Gebrueder Sulzer AG
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 Gebrueder Sulzer AG filed Critical Gebrueder Sulzer AG
Publication of EP0346285A1 publication Critical patent/EP0346285A1/fr
Application granted granted Critical
Publication of EP0346285B1 publication Critical patent/EP0346285B1/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
    • 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/102—Adaptations or arrangements of distribution members the members being disc valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7904—Reciprocating valves
    • Y10T137/7922—Spring biased
    • Y10T137/7929—Spring coaxial with valve
    • Y10T137/7937—Cage-type guide for stemless valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87571—Multiple inlet with single outlet
    • Y10T137/87587—Combining by aspiration

Definitions

  • the invention relates to a valve arrangement, in particular for piston compressors, pumps or the like, with a component which contains a passage opening through which a fluid can flow and a disk-like valve body which covers the passage opening and interacts with a valve seat surrounding it and which, together with a valve seat which can be braced against it
  • the spring element is freely movable in a fluid flow-through recess of a guide part that at least partially surrounds the valve seat, said recess being designed at a distance from the valve seat that allows the valve body to be lifted off, with inwardly projecting shoulders on which the Part of the spring element facing away from the valve body rests under pretension.
  • valve body formed by a flat plate is braced against the valve seat by a coil spring.
  • This valve construction requires a relatively large, high installation space to accommodate the coil spring.
  • Valve arrangements used in reciprocating compressors are known, each having an annular or concentric slot valve plate, which together with a spring plate by a central screw or e.g. are clamped by three corresponding fastening elements distributed over the valve between a valve seat part which can be placed on the passage opening and a holding plate which can be braced against the latter, the valve seat part and the holding plate being provided with openings through which the fluid can flow.
  • These known, multi-part valve constructions each require a relatively large installation space and, in addition, a relatively large amount of work when assembling and installing the valve.
  • the invention has for its object to provide a valve arrangement of the type mentioned improved in this regard in a simplified, compact and inexpensive construction, in particular with a low overall height, which enables an embodiment with a small clearance and correspondingly small dimensions of the required installation space.
  • valve body is designed with a central local elevation on the side facing away from the valve seat, and in that the spring element is formed by a round spring plate which can be loosely braced against this elevation, the elevation being a support surface for a central supporting surface the spring plate.
  • valve body and the spring element enables a particularly flat, compact design of the valve, its installation height essentially only by the thicknesses of the valve body and the spring plate and is determined by the stroke of the valve body.
  • simple installation and removal of the spring element in particular is ensured, since the flat spring plate, when untensioned, is correspondingly easier to handle than a helical spring, for example.
  • the pistons 5 and 7 are coupled via a yoke 14 connecting their piston rods 12 and 13 to a sliding piece 15 which is mounted on a crank pin 16 of a crankshaft 17.
  • the crankshaft 17 is connected to a motor, not shown, for example an electric motor.
  • the slider 15 is guided transversely to the axis 10 between two guideways 18 formed in the yoke 14.
  • the pistons 6 and 7 are via a yoke 22 connecting their piston rods 20 and 21, respectively coupled to a second slider, not shown, mounted on the crank pin 16, which is displaceably guided transversely to the axis 11 in the yoke 22, which is offset by 90 ° relative to the yoke 14.
  • the compression space 31 of the cylinder 1 forming the first compression stage is delimited by an end plate 35 which is inserted into the cylinder head 27 and which is provided with several, for example four through openings 36 arranged offset in the circumferential direction are provided.
  • the passage openings 36, of which only one is visible in FIG. 1, are each provided with a pressure valve 37.
  • the pressure valves 37 are each arranged on the side of the end plate 35 facing away from the piston 5 in a recess 38 of a guide part, according to FIG.
  • a plurality of passage openings 42 are also formed in the piston 5, each of which is provided with a suction valve 41.
  • a connection is established between the compression space 31 and a cylinder space 43 separated from it by the piston 5, which is connected to a feed line (not shown) for the medium to be compressed, e.g. Natural gas, is connected.
  • the suction valves 41 are arranged on the side of the piston 5 facing the compression space 31, each in a recess 44 of a further guide part detachably fastened to the piston 5, as shown in the illustration of a holding plate 45.
  • the compression spaces 32 and 33 are each one on the cylinder insert 24 and 25th attached end plate 46 and 47 limited.
  • the end plates 46 and 47 each contain a central through-opening 36 provided with the pressure valve 37, for example four, provided with suction valves 41, circumferentially offset through-openings 42, of which only one is also visible in FIG. 1.
  • the recess 38 receiving the pressure valve 37 is formed in the cylinder cover 28 and 29, respectively.
  • the recesses 44 receiving the suction valves 41 are each formed in the end part of the cylinder insert 24 or 25 facing the inside of the end plate 46 or 47, which serves as a guide part for the suction valves 41.
  • the recesses 38 are each connected to the compression space 32 or 33 by a lateral opening.
  • both a passage opening 36 provided with the pressure valve 37 and a passage opening 42 provided with the suction valve 41 are formed in the cylinder cover 30, the recess 38 receiving the pressure valve 37 in a connecting nipple 50 which can be screwed into the cylinder cover 30 of a pressure line leading away from the compressor 51 is formed, while the recess 44 receiving the suction valve 41 is formed in a nipple 52 which connects the compression space 34 to a flow channel 58 formed in the cylinder cover 30.
  • the piston 5 is shown in its top dead center position, in which the compression space 31 is the smallest.
  • the gas supplied to the cylinder space 43 is sucked through the passage opening 42 with the suction valve 41 open.
  • the gas compressed to a pressure of, for example, 5 bar, with the pressure valve 37 open is passed through the passage opening 36 into a cylinder space 55 and from there via a connecting cylinder cover 27 and 28 Flow channel 56 and an annular channel 48 of the second compression stage formed by the cylinder 2 are supplied.
  • the gas sucked into the compression chamber 32 through the passage openings 42 during the suction stroke of the piston 6 is reduced to a pressure of e.g. Compressed 20 bar and supplied with the pressure valve 37 open via a flow channel 57 connecting the cylinder covers 28 and 29 and an annular channel 49 to the third compression stage formed by the cylinder 3.
  • Fig. 1 the piston 7 of the cylinder 3 is shown in the bottom dead center position, in which the compression space 33 is largest.
  • the gas sucked into the compression space 33 during the suction stroke of the piston 7 is reduced to a pressure of e.g. 60 bar compressed and fed via the flow channel 58 connecting the cylinder covers 29 and 30 and through connection channels 59 and 60 formed in the nipple 52 to the fourth compression stage formed by the cylinder 4.
  • the gas sucked into the compression space 34 during the suction stroke of the piston 8 is brought to a pressure of e.g. 180 bar compressed and supplied with the pressure valve 37 open via the pressure line 51 to a gas fuel tank, not shown, which e.g. can be designed as a fuel tank of a motor vehicle.
  • All pressure valves 37 and suction valves 41 are, apart from any different dimensions of the interacting parts, essentially the same design.
  • the pressure valve 37 contains a disk-shaped round valve body 61 and which completely covers the associated passage opening 36 a round spring plate 62, under the action of which the valve body 61 loosely rests with a flat contact surface against a valve seat 63 surrounding the passage opening 36.
  • the valve seat 63 is formed directly on the end plate 35 delimiting the compression space 31.
  • the valve body 61 is provided on the side facing away from the valve seat 63 with a central elevation 64, which can be formed, for example, by a cylindrical extension or, as shown in FIG.
  • a bearing surface 65 for a central supporting surface 66 of the spring plate 62 is formed on the elevation 64.
  • the spring plate 62 is held clamped in the recess 38 of the holding plate 40 surrounding the pressure valve 37 against the valve body 61, the recess 38 being designed with a shoulder 67 narrowing in cross section.
  • the shoulder 67 protrudes at a distance from the valve body 61 which allows the valve body 61 to be lifted off and thus forms an abutment for the edge part 71 of the spring plate 62 which can be biased against it.
  • the recess 38 can be designed with local, niche-like extensions 68 which are distributed over its circumference and which ensure a low-loss flow through the recess 38 through the gas emerging from the compression space 31 when the pressure valve 37 is open. It goes without saying that a different number of extensions, or possibly only a single corresponding connection opening, can also be provided.
  • three slots 70 are formed in the spring plate 62 over their surface in the circumferential direction, each of which, one on an annular edge portion 71 the reference point 72 lying on the spring plate 62, runs spirally essentially over the four quadrants A, B, C and D of the surface of the spring plate 62 against its central support surface 66.
  • This support surface 66 which corresponds to the contact surface 65 of the elevation 64, is determined by an imaginary circle inscribed between the inner ends 73 of the three slots 70.
  • the slots 70 are designed such that, starting from their respective reference point 72, they each have an initial section E running along the edge section 71 with a width increasing in the area of the first quadrant A towards the second quadrant B and decreasing at the beginning of the second quadrant B.
  • the course of the slots 71 is selected such that webs 74 remain between them, each of which has a width H which, starting from the edge part 71, continuously decreases slightly over the first half of its length and against the second half of its length the central support surface 66 continuously increases slightly.
  • the support surface 66 can be made relatively small without an opening, and thus, like the corresponding contact surface 65 of the elevation 64. This construction therefore results, with optimal use of the material of the spring plate 62, in a design with relatively long, favorably stressed webs 74, which allow a relatively large spring travel with a small diameter of the spring plate 62. Accordingly, a maximum deflection of the spring plate is obtained if a minimum clearance is maintained 62 achieved so that the structural dimensions of the compressor can be kept correspondingly small.
  • the valve design according to the invention is particularly suitable for small, dry-running compressors, the valve body 61 and spring plates 62 e.g. Can have diameters of about 10 to 12 mm.
  • the spring plates 62 can be made of spring steel or another material suitable for leaf springs, such as titanium or beryllium, and each have a thickness of 0.1 to 0.3 mm. It goes without saying that designs with dimensions other than those described are also possible.
  • the valve bodies 61 can be made of metal or a plastic, e.g. Polyether ether ketone (PEEK).
  • the plastic design in particular, enables a cost-effective, low-mass and low-noise valve arrangement to be achieved, which responds quickly and which guarantees operation with minimal wear and a correspondingly long service life.
  • An optimal ratio between the maximum deflection and the spring force of the spring plate 62 can be achieved in versions in which the bearing surface 65 formed on the elevation 64 and the central support surface 66 of the spring plate 62 have a diameter which is approximately 1/4 to 1/8 of the diameter of the valve body 61.
  • Modified embodiments can contain valve bodies, each of which is designed with a conical or lenticular contact surface and which cooperate with correspondingly designed valve seats.
  • An embodiment is also possible in which the valve seat is formed on an exchangeable insert.
  • the invention is not limited to use on compressors of the type described and illustrated above, but is also for other, single or multi-stage designs, as well as for other applications, e.g. suitable for pipes, breathing air compressors, compressors for low-temperature technology or compressors for compressing CO2, nitrogen and similar media.
  • the valve arrangement according to the invention is also suitable for use on pumps or lines for liquid media, e.g. Water or liquid gas, suitable.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Claims (10)

1. Dispositif à soupape, notamment pour compresseurs à piston, pompes ou similaires, comportant un composant (5, 30, 35, 46, 47) qui présente un orifice de passage (36, 42) pouvant être traversé par un fluide, et comportant un corps de soupape (61) en forme de disque qui recouvre l'orifice de passage (36, 42) et coopère avec un siège de soupape (63) entourant cet orifice et qui est placé, de manière à pouvoir se déplacer librement avec un élément à ressort pouvant être serré contre lui, dans un évidement (38 ou 44) ouvert vers l'orifice de passage (36 ou 42), traversé par le fluide, d'un élément de guidage entourant au moins partiellement le siège de soupape (63), cet évidement (38, 44) étant réalisé à une distance du siège de soupape (63) autorisant un relèvement du corps de soupape (61), avec des talons (67), faisant saillie vers l'intérieur, contre lesquels s'applique sous précontrainte la partie (71) de l'élément à ressort opposée au corps de soupape (61), caractérisé en ce que le corps de soupape (61) est réalisé, sur le côté opposé au siège de soupape (63), avec un bossage (64) local, central, et en ce que l'élément à ressort est formé par une plaque-ressort (62) ronde, pouvant être librement serrée contre ce bossage (64), le bossage (64) présentant une surface de support (65) pour une surface d'appui (66) centrale de la plaque-ressort (62).
2. Dispositif à soupape selon la revendication 1, caractérisé en ce que le siège de soupape (63), coopérant avec le corps de soupape (61), est directement formé sur le composant (5, 30, 35, 46, 47), contenant l'orifice de passage (36, 42).
3. Dispositif à soupape selon la revendication 1 ou 2, caractérisé en ce que le corps de soupape (61) est en matière plastique, par exemple en polyétheréther-cétone.
4. Dispositif à soupape selon l'une des revendications précédentes, caractérisé en ce que le bossage (64) du corps de soupape (61) a la forme d'un tronc de cône et en ce que la surface de support (65), tournée vers la plaque-ressort (62), présente un diamètre qui est compris entre 1/4 et 1/8 du diamètre du corps de soupape (61).
5. Dispositif à soupape selon l'une des revendications précédentes, caractérisé en ce que la plaque-ressort (62) est en acier à ressort et présente une épaisseur comprise entre 0,1 et 0,3 mm.
6. Dispositif à soupape selon l'une des revendications précédentes, caractérisé en ce qu'il est formé dans la plaque-ressort (62) trois fentes (70) dont chacune, partant d'un point de référence (72) sur la partie de bordure (71), s'étend en spirale, à peu près sur les quatre quadrants (A, B, C, D) de la surface de la plaque-ressort (62), vers la surface d'appui (66) centrale, celle-ci correspondant à la surface d'appui (66), restant entre les extrémités intérieures (73) des fentes (70), de la surface de support (65) formée sur le bossage (64) du corps de soupape (61).
7. Dispositif à soupape selon la revendication 6, caractérisé en ce que chacune des fentes (70), partant du point de référence (72), présente une portion initiale (E), s'étendant à peu près sur un premier quadrant (A), avec une largeur augmentant vers le deuxième quadrant (B) et diminuant au début de ce deuxième quadrant (B), et une portion centrale (F), s'étendant sur le reste du deuxième quadrant (B) et le troisième quadrant (C), avec une largeur réduite à peu près constante ainsi qu'une portion terminale (G), s'étendant sur le quatrième quadrant (D), avec une largeur augmentant vers le premier quadrant (A).
8. Dispositif à soupape selon la revendication 6 ou 7, caractérisé en ce que les fentes (70) délimitent trois cloisons (74) s'étendant depuis la partie de bordure (71) vers la surface d'appui (66) centrale, lesquelles, partant de la partie de bordure (71), présentent une largeur (H) diminuant en continu sur à peu près la première moitié de leur longueur et augmentant en continu, sur à peu près la deuxième moitié de leur longueur, vers la surface d'appui (66) centrale.
9. Dispositif à soupape selon l'une des revendications précédentes, caractérisé en ce que l'évidement (38, 44) logeant le corps de soupape (61) et la plaque-ressort (67) est pourvu, sur son pourtour, d'au moins un élargissement (68) local augmentant sa section transversale.
10. Utilisation d'un dispositif à soupape selon l'une des revendications précédentes pour un compresseur à piston alternatif, pour comprimer du gaz, par exemple du gaz naturel, à stocker comme carburant dans un véhicule automobile.
EP89810419A 1988-06-09 1989-06-05 Dispositif de clapet Expired - Lifetime EP0346285B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH2209/88 1988-06-09
CH220988 1988-06-09

Publications (2)

Publication Number Publication Date
EP0346285A1 EP0346285A1 (fr) 1989-12-13
EP0346285B1 true EP0346285B1 (fr) 1992-04-29

Family

ID=4228434

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89810419A Expired - Lifetime EP0346285B1 (fr) 1988-06-09 1989-06-05 Dispositif de clapet

Country Status (5)

Country Link
US (2) US4936327A (fr)
EP (1) EP0346285B1 (fr)
AU (1) AU618605B2 (fr)
CA (1) CA1327189C (fr)
DE (1) DE58901264D1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4200838C2 (de) * 1992-01-15 1994-12-22 Knf Neuberger Gmbh Pumpe mit vom Fördermedium gesteuerten Ventilen
WO2004022407A1 (fr) 2002-09-05 2004-03-18 Quadeltrad, Sl Plateforme roulante interne permettant de deplacer un conteneur rigide pourvu d'un support de positionnement
TR201716552T3 (tr) * 2003-03-17 2017-12-21 Arcelik As Bir kompresör.
US7617826B1 (en) 2004-02-26 2009-11-17 Ameriflo, Inc. Conserver
US8146592B2 (en) * 2004-02-26 2012-04-03 Ameriflo, Inc. Method and apparatus for regulating fluid flow or conserving fluid flow
JP4690419B2 (ja) * 2004-11-12 2011-06-01 エルジー エレクトロニクス インコーポレイティド 吐出バルブ及びこれを備えた往復動式圧縮機のバルブアセンブリ
EP2427807B1 (fr) * 2009-05-07 2020-12-23 Parker-Hannifin Corporation Ensemble soupape de régulation à contrainte axiale et alignement automatique
KR102233610B1 (ko) 2014-07-21 2021-03-30 엘지전자 주식회사 리니어 압축기
KR102240032B1 (ko) * 2014-07-21 2021-04-14 엘지전자 주식회사 리니어 압축기
DE202014009180U1 (de) 2014-11-14 2015-01-14 Technische Universität Ilmenau Druckgradientengesteuertes Lamellenventil mit einstellbarer Steifigkeit

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US1998444A (en) * 1927-12-29 1935-04-23 Sullivan Machinery Co Valve mechanism
GB427276A (en) * 1933-09-12 1935-04-18 British Thomson Houston Co Ltd Improvements in and relating to compressor valves
US2155236A (en) * 1937-09-14 1939-04-18 Westinghouse Air Brake Co Compressor unloading device
US2792790A (en) * 1950-08-07 1957-05-21 Frank R Capps Fluid pump
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US2800142A (en) * 1954-11-15 1957-07-23 A V Roe Canada Ltd Pressure regulating and check valve
US3664371A (en) * 1970-10-23 1972-05-23 Us Navy Resilient poppet valve
US3911502A (en) * 1974-08-23 1975-10-14 Us Health Composite heart valve poppet
DE2454956A1 (de) * 1974-11-20 1976-05-26 Zlof Dieter Dipl Betriebsw Mehrstufiger hubkolbenkompressor
AU516210B2 (en) * 1975-12-24 1981-05-21 Commonwealth Scientific And Industrial Research Organisation Vacuum pump
AT351327B (de) * 1976-01-26 1979-07-25 Hoerbiger Ventilwerke Ag Rueckschlagventil
US4368755A (en) * 1978-12-20 1983-01-18 Copeland Corporation Valve assembly
JPS5759238U (fr) * 1980-09-26 1982-04-07
US4469126A (en) * 1981-11-04 1984-09-04 Copeland Corporation Discharge valve assembly for refrigeration compressors
US4543989A (en) * 1981-11-04 1985-10-01 Copeland Corporation Discharge valve assembly for refrigeration compressors
GB2135430B (en) * 1983-02-22 1986-08-13 Value Company Limited Metallic Valve component

Also Published As

Publication number Publication date
US4936327A (en) 1990-06-26
AU3614389A (en) 1989-12-14
CA1327189C (fr) 1994-02-22
DE58901264D1 (de) 1992-06-04
AU618605B2 (en) 1992-01-02
US4981421A (en) 1991-01-01
EP0346285A1 (fr) 1989-12-13

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