EP0240823B1 - Compresseur à piston roulant - Google Patents

Compresseur à piston roulant Download PDF

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Publication number
EP0240823B1
EP0240823B1 EP87104228A EP87104228A EP0240823B1 EP 0240823 B1 EP0240823 B1 EP 0240823B1 EP 87104228 A EP87104228 A EP 87104228A EP 87104228 A EP87104228 A EP 87104228A EP 0240823 B1 EP0240823 B1 EP 0240823B1
Authority
EP
European Patent Office
Prior art keywords
rotary
piston compressor
compressor according
rotary piston
casing
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
EP87104228A
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German (de)
English (en)
Other versions
EP0240823A2 (fr
EP0240823A3 (en
Inventor
Hans-Peter Dipl.-Ing. Schabert
Max Dipl.-Ing. Heller
Klaus Dipl.-Ing. Zach (Fh)
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.)
Siemens AG
Original Assignee
Siemens 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 Siemens AG filed Critical Siemens AG
Publication of EP0240823A2 publication Critical patent/EP0240823A2/fr
Publication of EP0240823A3 publication Critical patent/EP0240823A3/de
Application granted granted Critical
Publication of EP0240823B1 publication Critical patent/EP0240823B1/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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
    • F04C28/125—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves with sliding valves controlled by the use of fluid other than the working fluid
    • 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
    • Y10T137/86389—Programmer or timer
    • Y10T137/86405—Repeating cycle
    • Y10T137/86421—Variable

Definitions

  • the invention relates to a rotary piston compressor according to the preamble of the main claim.
  • a rotary piston compressor with the features of the preamble of the main claim is known for example from EP-A-0 212 570.
  • a check valve is arranged, with which the back flow of compressed gas is prevented in the cylinder. It is not possible to control the compressor output with this check valve.
  • EP-A-0 175 639 discloses a vane compressor, the mechanical performance of which can be controlled by an axially adjustable rotary valve which is arranged outside the cylinder on the outlet side and rotates with the compressor shaft. In this known compressor, however, only the final pressure at the outlet is controlled. The amount of gas drawn in remains essentially the same with this compressor.
  • the invention is based on the object of specifying a rotary piston compressor, the amount of gas drawn in can be regulated continuously even at high speeds. This is particularly important for mechanically driven rotary piston compressors which are rigidly coupled to an internal combustion engine and are used to charge the internal combustion engine.
  • a rotary valve is arranged outside the cylinder in a slotted sleeve and closed with the shaft a steady, synchronized rotary movement and since the relative position of the rotary valve and sleeve can be adjusted relative to each other, a stepless regulation of the amount of gas sucked in at a fixed speed is possible.
  • rotary valve is meant a roller-shaped body, so that passages provided on its periphery alternately communicate with the slots in the sleeve, which can also be an integral part of the compressor housing. The adjustment of the relative position which serves to change the passage cross sections takes place primarily in the axial direction.
  • the rotary valve can, for example, open at a crank angle between 0 and 25 ° of the shaft carrying the cylinder and close at a crank angle of at most 360 °. This results in the maximum delivery volume of the compressor for the closing angle of 360 °, i.e. the rotary valve remains open practically all the time. At smaller closing angles, which result in a shorter filling time, the amount of gas drawn in decreases, as is also the case when the throttle valve is gradually closed in a motor vehicle. Compared to the highly lossy throttle control, the design according to the invention as a periodically intermittent fill quantity control, however, delivers a significantly better efficiency.
  • the coupling to the compressor shaft which is desired for a constant synchronized rotary movement of the rotary slide valve can advantageously take place in such a way that the rotary slide valve and the shaft are connected to one another by a toothing.
  • Gears, toothed chains or toothed belts are primarily suitable as toothed links. It can be obtained with non-circular gears periodically non-uniform rotary slide movements, which allow quick closing after a long time with a large passage cross-section. This will make the minimizes small throttling losses that still occur when regulating the filling quantity.
  • the rotary valve for changing the passage cross-section relative to the sleeve is not only adjustable in the axial direction, but is also rotatable by a smaller angle than ⁇ 90 °, for example by 80 °, because one so that the temporal change in the opening cross-section can better capture the current suction volume flow during rotation.
  • the sleeve is actuated on the end face opposite the rotary valve drive, because it does not reach the area of the actuators of the rotary valve.
  • a possibility will later be presented of having the adjustment act on the rotary slide valve and providing it on one side in a space-saving manner together with its drive.
  • the return spring e.g. the suction quantity of the rotary piston compressor is regulated to a minimum value suitable for an internal combustion engine as idling.
  • a coupling with the accelerator pedal and an idle adjustment screw can be provided.
  • the sleeve preferably being made of plastic and surrounding a rotary valve made of metal. It is particularly advantageous to install the plastic sleeve with play in the housing so that it can expand locally when a temperature peak occurs at a friction point.
  • the rotary valve can also be designed so that it has opposite openings and is flowed through diametrically.
  • the speed of the rotary valve must be half or a third of the shaft speed.
  • the invention can be implemented in such a way that a common rotary slide valve for both Piston parts are provided, the passage openings are offset in the axial circumferential direction.
  • the offset can be 90 °, for example.
  • control option by means of the rotary valve should remain available even when the internal combustion engine is cold started.
  • the internal combustion engine is still cold, not only should the cooling of the intake air occurring at part load be compensated, but additional heat should be added to it if possible.
  • This task can be solved by a switchable internal throttle bypass.
  • FIG. 3 shows a section along the rotary slide axis drive and adjustment of a rotary slide from the same side.
  • FIGS. 7 and 8 developments of the rotary valve show passage cross sections and their changes by adjusting the rotary valve and sleeve.
  • the rotary piston compressor shown in FIGS. 1 and 2 is designed in tandem, because in its housing 1, which consists of light metal casting, the shaft 2 carries two piston parts 3 and 4 offset by 180 ° a rolling piston 5.
  • the two piston parts 3 and 4 in the same design comprise cylindrical tube pieces 6 made of stainless steel with a wall thickness of, for example, 1.2 mm and a diameter of 145 mm.
  • the pipe sections 6 are held with a thin-walled shell 7 on a hub body 8 which is fastened with a ball bearing 10 on a cranked section 9 of the shaft 2, so that the piston part 3 is pressed elastically against the wall 11 of the cylinder 1.
  • the suction line of the compressor is 500 m3 / h.
  • the shaft 2 carries, outside the housing 1, a pulley 12 for a V-belt, with which the connection to an internal combustion engine, not shown, is established.
  • the toothed belt 16 establishes the connection to a rotary valve 20 which is arranged in an inlet opening 17 and which is mounted in the housing 1 as a regulating member on the suction side.
  • the rotary valve 20 projects into a pipe socket 21 formed by the housing 1 with a ball bearing 22 which carries a toothed belt pulley 23.
  • a toothed belt pulley 23 On the toothed belt pulley 23, the flange 25 of a hollow shaft 26 is fastened in a flexible manner, which projects into the pipe socket 21. There it engages with a head piece 28 at its free end, which is provided with curved teeth 29, in grooves 30 of a further hollow shaft 31, which forms the main piece of the rotary valve 20.
  • the hollow shaft 31 is made of metal, for example stainless steel. It is on the end of the housing 1 facing away from the toothed belt pulley and the V-belt pulley 12 with an inwardly projecting Provided flange 34 on which a push rod 35 engages with a ball bearing 50. With the rod 35, an axial displacement of the hollow shaft 31 relative to a sleeve 36 made of plastic can be achieved, which tightly surrounds the hollow shaft 31 of the rotary valve 20. Since both in the sleeve 36 and in the hollow shaft 31 at least partially oblique slots 37, 38 are provided, for example triangular or trapezoidal, a different passage cross section can be set depending on the angular position of the rotary valve 20 by the axial displacement of the hollow shaft 31. In this way, the suction quantity and thus the delivery rate of the rotary piston compressor can be varied within wide limits.
  • the rotary piston compressor designed in tandem has a central partition 40 between the two piston parts 3 and 4.
  • a valve 42 is arranged in the housing 1, which can be actuated by a magnet 43.
  • An internal throttle bypass is connected with the valve 42 between the two cylinder parts, which are connected to one another by a longitudinal bore 46 and transverse bores 47 and 48. With this bypass, the cold start of an internal combustion engine with a rotary piston compressor can be facilitated. As long as the bypass is kept open, there is a back and forth lossy air flow, which causes the intake air to heat up.
  • the bypass can also be arranged in such a way that it connects regions on the circumference of the cylinder 1 which are located apart from one another.
  • FIG. 3 shows another type of actuation of the rotary valve 20 in a section along the axis of the rotary valve 20.
  • the drive and adjustment act on the same side of the rotary valve.
  • a pipe section 62 is mounted on the housing 1 of the rotary piston compressor with two ball bearings 60 and 61 spaced apart from one another, which is expanded to a gear 63 on its side facing the housing 1.
  • the other end of the pipe section 62 is formed into a flange 65.
  • a counter flange is fastened with screws 66, which is designed to be flexible with respect to the axial direction by means of incisions 68 and 69.
  • the flange 67 carries a hollow shaft piece 70 pointing towards the housing 1, into which a counterpart 72 with an arch toothing 73 located at the end is inserted.
  • the curved toothing 73 in turn engages in the grooves 30 of the hollow shaft 31 of the rotary valve 20.
  • a rod 80 projects through the flange 67 and is fixed in the hollow shaft 31 with a ball bearing 81.
  • the rod 80 is used to adjust the rotary valve 20 in the longitudinal direction.
  • it is provided with a spherical actuation button 83 at the end remote from the rotary valve 20.
  • the drive of the rotary slide valve 20 and its axial adjusting device are provided at the same end and are structurally combined in a very small space.
  • two elliptical gears 85 and 86 are used to generate the non-uniform but periodic movement, which mesh with each other.
  • the gear 85 sits eccentrically, namely with its one focal point, on the hollow shaft 31 of the rotary valve 20, the gear 86 also eccentrically on an intermediate shaft 87.
  • the intermediate shaft 87 is connected to a countershaft gear 88 which meshes with a smaller countershaft gear 89.
  • the gear 89 sits on the shaft 2 of the rotary piston compressor.
  • the speed of rotation can be varied in a ratio of up to 1: 2.
  • the oval gear 85 like the oval gear 86, is not mounted in the focal point of an ellipse that determines the gear circumference, but rather in the center of the gear.
  • the maximum speed of the rotary valve 20 relates to the minimum speed like the inverse ratio of the gear radii.
  • FIG. 6 shows that a periodically non-uniform movement of the rotary valve 20 can also be achieved with a coupling square.
  • the coupling quadrangle comprises a crank 90 which is connected to the hollow shaft 31 of the rotary valve 20.
  • the crank 90 is connected by a connecting rod 91 to a second crank 92, which sits on an intermediate shaft 93 carrying the gear 88.
  • the gear 88 meshes with the counter gear 89.
  • This gear in the form of an anti-parallel crank gear, enables ratios of the minimum to the maximum rotary valve speed of approximately 1: 3.5.
  • Figure 7 shows a development of the sleeve 36 and the rotary valve 20 with e.g. 40 mm diameter in the event that the rotary valve 20 is driven at half the speed of the shaft 2.
  • Sleeve 36 and rotary valve 20 are traversed by the gas flow on the suction side. They each have two slots 37 with an offset of 180 ° on the circumference, namely the two triangular slots 37, 37a in the rotary slide valve 20 and the slots 38 and 34 in the sleeve 36.
  • the slot 38 of the sleeve 36 connected to the cylinder 1 has a similar one Triangular shape like the slots 37, 37a of the rotary valve 20. However, the triangle 38 is turned upside down.
  • the slot 39 of the sleeve 36 connected to the suction line 17, on the other hand, is rectangular.
  • the slots 37, 37a When moving the rotary valve 20 to the left by the stroke 98 of e.g. 40 mm, the slots 37, 37a come into positions 37 ', 37a'. They then overlap with the slits 38, 39 to a much greater extent, since the flow cross-sections 101, 102 with dashed lines are created. They also remain open over a large range of rotation angles.
  • the axial displacement 98 of the rotary valve 20 thus causes a strong increase in the suction power of the compressor and leads to an increase in the boost pressure in the connecting pipeline 53 to the internal combustion engine.
  • the opening area reaches its maximum value somewhat later than the theoretically approximately sinusoidal course of the volume flow in the rotary piston compressor during suction.
  • the inertia of the real air column is taken into account in the sense that the throttling losses in the free slot cross section, ie in the overlap of the passages 38 and 37, are minimized.
  • the start of the opening in time is independent of the axial position of the rotary valve 20.
  • a displacement in the circumferential direction between rotary valve 20 and its toothed belt pulley 23 must therefore be superimposed on the displacement stroke 98 (40 mm) (for example by ⁇ 85 °), so that the overall adjustment runs in the direction of arrow 96.
  • the teeth of the curved tooth intermediate piece 29 are turned to the rotary slide 20 by 45 ° to the axis.
  • the filling quantity is controlled by pushing or pulling on the opposite end (with 45 ° setting the risk of self-locking due to tooth friction is lowest).
  • the shape of the triangular or trapezoidal slot 37 is chosen so that the long slope coincides with the displacement device of the rotary valve 20.
  • the opposite side is either axially parallel, but can also deviate from it.
  • the slots 37 cover approximately 64% (2 ⁇ 32%), the webs the residual angle 36% (2 ⁇ 18%) of the hollow shaft 31 of the rotary valve.
  • the slots 37 are shortened by, for example, 20% of the original triangular width in order to be able to arrange slots 37 which are as wide as possible on the circumference of the rotary valve 20.
  • the reduction does indeed reduce the rate of change in area that can be achieved at almost full opening just before the flow is shut off; however, since the flow has already decreased considerably on its own (sine line), the throttling loss that arises as a result is modest.
  • the axial stroke of the rotary valve 20 can be e.g. 15% longer than the length of the original triangular slot. This creates a particularly large passage cross-section and low throttle losses at full load.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Rotary Pumps (AREA)

Claims (26)

  1. Compresseur à piston roulant comportant un cylindre (1), qui possède des ouvertures d'entrée et de sortie et dans lequel tourne un piston (5), qui est porté par un arbre (2) tournant en sens opposé, caractérisé par le fait que pour la commande de la quantité d'aspiration, un tiroir rotatif (20) est disposé sur le côté aspiration à l'extérieur du cylindre (1), dans un manchon (36) pourvu de fentes (37) et est raccordé à l'arbre (2) pour l'exécution d'un mouvement de rotation permanent et synchronisé, et que la position relative du tiroir rotatif (20) et du manchon (36) est réglable.
  2. Compresseur à piston roulant suivant la revendication 1, caractérisé par le fait que le tiroir rotatif (20) et l'arbre (2) sont reliés entre eux selon une liaison par complémentarité de formes, notamment par un système denté se présentant sous la forme de pignons, de chaînes dentées, de courroies dentées.
  3. Compresseur à piston roulant suivant la revendication 2, caractérisé par le fait que la liaison par complémentarité de formes déplace le tiroir rotatif (20) plus rapidement dans le sens de la fermeture que dans le sens de l'ouverture.
  4. Compresseur à piston roulant suivant la revendication 3, caractérisé par le fait que la liaison par complémentarité de formes comprend au moins un pignon non circulaire et de préférence oval (85,86).
  5. Compresseur à piston roulant suivant la revendication 4, caractérisé par le fait que la liaison par complémentarité de formes comprend deux pignons elliptiques (85,86) engrenant réciproquement.
  6. Compresseur à piston roulant suivant la revendication 3, caractérisé par le fait que la liaison par complémentarité de formes comprend un quadrilatère de couplage plan (90,91,92) comportant une transmission démultiplicatrice (88,89).
  7. Compresseur à piston roulant suivant l'une des revendications 1 à 6, caractérisé par le fait que le tiroir rotatif (20) comporte une possibilité de réglage axial permettant de modifier la section transversale de passage par rapport au manchon (36).
  8. Compresseur à piston roulant suivant l'une des revendications 1 à 7, caractérisé par le fait que le manchon (36), qui entoure le tiroir rotatif (20), est déplaçable dans la direction axiale.
  9. Compresseur à piston roulant suivant la revendication 1, caractérisé par le fait que le manchon (36) déplaçable axialement est disposé de façon à pouvoir tourner sur un angle inférieur à ±90°.
  10. Compresseur à piston roulant suivant la revendication 7, 8 ou 9, caractérisé par le fait que le manchon (36) est actionné sur la face frontale du cylindre (1), tournée à l'opposé du dispositif d'entraînement du tiroir rotatif.
  11. Compresseur à piston roulant suivant l'une des revendications 1 à 10, caractérisé par le fait que le manchon (36) ou le tiroir rotatif (20) sont soumis à l'action d'un ressort de rappel.
  12. Compresseur à piston roulant suivant l'une des revendications 1 à 11, caractérisé par le fait que le tiroir rotatif (20) est réalisé en un métal et tourne dans un manchon (36) réalisé en une matière plastique qui est renforcée par des fibres de verre et contient un adhésif formé d'un agent de lubrification, de préférence du graphite ou du sulfure de molybdène.
  13. Compresseur à piston roulant suivant la revendication 12, caractérisé par le fait que le manchon (36) est disposé dans le cylindre (1) avec un jeu diamétral égal à au moins 0,1 mm.
  14. Compresseur à piston roulant suivant la revendication 13, caractérisé par le fait qu'un élément d'étanchéité, notamment une barrette d'étanchéité, est disposé dans la fente entre le manchon (36) et le cylindre (1).
  15. Compresseur à piston roulant suivant l'une des revendications 1 à 14, caractérisé par le fait que le tiroir rotatif (20) comporte des ouvertures opposées (37) et est traversé diamétralement par un écoulement.
  16. Compresseur à piston roulant suivant la revendication 4, caractérisé par le fait que la vitesse de rotation du tiroir rotatif (20) est égale à la moitié ou au tiers de la vitesse de rotation de l'arbre.
  17. Compresseur à piston roulant suivant l'une des revendications 1 à 16, comportant deux éléments de piston décalés dans la direction circonférentielle, caractérisé par le fait qu'il est prévu un tiroir rotatif commun (20) pour les deux éléments de piston (3,4), dont les ouvertures de passage (37) sont décalées dans la direction circonférentielle.
  18. Compresseur à piston roulant suivant l'une des revendications 1 à 17, caractérisé par le fait que les fentes (37) ménagées dans le manchon (36) ainsi que dans le tiroir rotatif (20) possèdent une forme triangulaire ou trapézoïdale avec des côtés éventuellement incurvés.
  19. Compresseur à piston roulant suivant la revendication 18, caractérisé par le fait qu'un côté de la fente triangulaire ou trapézoïdale coïncide, au repos, avec le sens de déplacement du tiroir rotatif (20).
  20. Compresseur à piston roulant suivant la revendication 18 ou 19, caractérisé par le fait que les dimensions des fentes (37) possèdent, dans la direction circonférentielle, sont égales approximativement au double de celles des barrettes intercalaires.
  21. Compresseur à piston roulant suivant la revendication 18,19 ou 20, caractérisé par le fait que dans un tiroir rotatif (20) disposé sur le côté aspiration et dans le manchon (36), qui l'entoure, sont ménagées des fentes triangulaires de même taille (37), dont les pointes sont dirigées en des sens opposés, et que le chevauchement est limité à une valeur minimale appropriée pour le fonctionnement de ralenti d'un moteur à combustion interne et qui peut être modifiée en fonction de la température.
  22. Compresseur à piston roulant suivant l'une des revendications 1 à 21, caractérisé par le fait que les fentes (37) sont réalisées sous la forme d'un triangle possédant des pointes sectionnées ou arrondies.
  23. Compresseur à piston roulant suivant l'une des revendications 1 à 22, caractérisé par le fait que la course axiale de déplacement du tiroir rotatif (20) et/ou de le manchon (36) est supérieure aux dimensions axiales d'une fente triangulaire (37).
  24. Compresseur à piston roulant suivant l'une des revendications 1 à 23, caractérisé par le fait que le tiroir rotatif (20) est entraîné par un embrayage (73) à dents courbes qui sert à transmettre le mouvement de rotation et qui s'appuie coaxialement sur un poussoir (80) pour un déplacement axial (figure 3).
  25. Compresseur à piston roulant suivant l'une des revendications 1 à 24, caractérisé par le fait que les dents de l'embrayage à dents courbes (29,76) sont inclinées d'environ 45° par rapport à l'axe.
  26. Compresseur à piston roulant suivant l'une des revendications 1 à 25, caractérisé par le fait qu'il est prévu un by-pass intérieur d'étranglement (46) pouvant être branché en supplément et qui relie entre elles des zones locales situées dans le cylindre (1) et qui sont décalées sur la périphérie ou sont associées à des éléments de piston (3,4) se déplaçant en étant décalés.
EP87104228A 1986-04-04 1987-03-23 Compresseur à piston roulant Expired - Lifetime EP0240823B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863611326 DE3611326A1 (de) 1986-04-04 1986-04-04 Rollkolbenverdichter
DE3611326 1986-04-04

Publications (3)

Publication Number Publication Date
EP0240823A2 EP0240823A2 (fr) 1987-10-14
EP0240823A3 EP0240823A3 (en) 1988-09-28
EP0240823B1 true EP0240823B1 (fr) 1991-11-21

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EP87104228A Expired - Lifetime EP0240823B1 (fr) 1986-04-04 1987-03-23 Compresseur à piston roulant

Country Status (5)

Country Link
US (1) US4793779A (fr)
EP (1) EP0240823B1 (fr)
JP (1) JPS62240494A (fr)
BR (1) BR8701547A (fr)
DE (2) DE3611326A1 (fr)

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US9267504B2 (en) 2010-08-30 2016-02-23 Hicor Technologies, Inc. Compressor with liquid injection cooling
CA2809945C (fr) 2010-08-30 2018-10-16 Oscomp Systems Inc. Compresseur a refroidissement par injection de liquide

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Also Published As

Publication number Publication date
JPS62240494A (ja) 1987-10-21
US4793779A (en) 1988-12-27
EP0240823A2 (fr) 1987-10-14
BR8701547A (pt) 1988-01-26
EP0240823A3 (en) 1988-09-28
DE3611326A1 (de) 1987-10-15
DE3774604D1 (de) 1992-01-02

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