EP0608311A1 - Combinaison de commande d'admission pour systeme de compresseur - Google Patents

Combinaison de commande d'admission pour systeme de compresseur

Info

Publication number
EP0608311A1
EP0608311A1 EP92921578A EP92921578A EP0608311A1 EP 0608311 A1 EP0608311 A1 EP 0608311A1 EP 92921578 A EP92921578 A EP 92921578A EP 92921578 A EP92921578 A EP 92921578A EP 0608311 A1 EP0608311 A1 EP 0608311A1
Authority
EP
European Patent Office
Prior art keywords
compressed gas
valve
inlet
sab
compressor
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
EP92921578A
Other languages
German (de)
English (en)
Other versions
EP0608311A4 (fr
EP0608311B1 (fr
Inventor
Anthony John Kitchener
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.)
Cash Engineering Research Pty Ltd
Original Assignee
Cash Engineering Co Pty Ltd
Cash Engineering Research Pty Ltd
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 Cash Engineering Co Pty Ltd, Cash Engineering Research Pty Ltd filed Critical Cash Engineering Co Pty Ltd
Publication of EP0608311A1 publication Critical patent/EP0608311A1/fr
Publication of EP0608311A4 publication Critical patent/EP0608311A4/fr
Application granted granted Critical
Publication of EP0608311B1 publication Critical patent/EP0608311B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/026—Lubricant separation

Definitions

  • the present invention relates to improvements in compressor systems or their component parts and particularly to flooded compressor systems employing screw or similar rotating means to effect compression of the gas.
  • Systems of the aforementioned kind conventionally comprise a number of major component parts including a screw compressor unit adapted to receive air to be compressed through an inlet filter and a main throttle vaive.
  • Lubricating oil is also introduced into the screw compressor unit adjacent its inlet zone and a mixture of compressed gas and oil is discharged from this unit to be separated in a separator vessel. Oil collected in the separator vessel is returned via a filter and an oil cooler to the screw compressor unit and clean compressed air is discharged from the separator vessel.
  • the discharged compressed air normally passes through a coalescent type final filter to remove any remaining oil droplets which is commonly housed within or in communication with the main separator vessel with the attendant problems as discussed in UK Patent No. 0,121 ,999.
  • a minimum pressure vaive is supplied in the clean compressed air discharge line from the separator vessel so that the vaive remains closed until such time as gas pressure in the separator vessel exceeds a predetermined minimum level.
  • the compressed gas is discharged into a storage vessel from which it is withdrawn for the desired end use. Pressure within the storage vessel is used to control operation of the compressor unit.
  • a typical arrangement of this kind is disclosed in UK Patent No. 0,130,662.
  • One difficulty with such systems involves the physical size of the complete package which also has an adverse effect on the expense of production.
  • the number of interconnecting pipes and corresponding joints which may cause possible leakage problems, also has an adverse effect on fabrication costs.
  • incorporation of the final filter element within the separator vessel also involves significant fabrication processes which also has an adverse effect on production costs for the system.
  • the present invention aims at providing a single control valve arrangement that will act as a main throttle valve as well as a minimum pressure valve for the separator vessel; a separate final filter configuration in combination with a minimum pressure valve; and configuration including all the aforesaid features.
  • the present invention provides a final filter configuration adapted for connection to a compressor system of the type including a compressor adapted to discharge a mixture of compressed gas and liquid into a separator vessel, said compressed gas being at least partially separated from said liquid in said separator, said final filter configuration including a support member, an outer wall secured to sai support member defining an internal substantially enclosed space, a filter element located within said enclosed space having opposed axial ends and an intervening annular wall of filter material, one of said axial ends being sealingly engaged or connected with said support member and the other of said axial ends being closed to prevent gas flow therethrough from a first zone outwardly of said filter element to a second zone inwardly of said filter element, first communication means being provided to enable flow to o r from said first zone, second communication means enabling flow to or from said second zone, and inlet connection means enabling connection in use of one of said first or second communication means to said separator vessel of the compressor system.
  • reieasable connection means is provided between said outer wall and said support member to enable access to the filter means for servicing as may be required.
  • the reieasable connection means may comprise a screw or threaded connection.
  • one of said first or second communication means passes through said support member and forms a discharge passage, a minimum pressure vaive being provided in said support member controlling flow through said discharge passage.
  • the discharge passage may be arranged leading from said second inner zone but a reverse arrangement is also possible.
  • a control valve arrangement for a flooded compressor system comprising a main throttle valve adapted to close or open a main gas inlet to a compressor unit of said compressor system and a filter assembly mounted from said control vaive arrangement, said control vaive arrangement including inlet means to receive a mixture of compressed gas and oil droplets from a separator means of said compressor system and to direct said mixture into said filter assembly, and discharge means within said valve arrangement to discharge clean compressed gas after passage through a filter element within said filter assembly.
  • the present invention provides a control valve arrangement for a flooded compressor system, said control vaive arrangement comprising a main throttle valve adapted to close or open a main gas inlet to a compressor unit of said compressor system, inlet compressed gas flow means to receive compressed gas from a separator of said compressor system, and a minimum pressure valve arranged to receive said compressed gas from said inlet gas flow and to discharge said compressed gas from said control valve arrangement only after a predetermined minimum pressure of said compressed gas is achieved.
  • said control valve arrangement also includes a filter assembly as aforesaid and said inlet compressed gas flow means is arranged to receive compressed gas after passing through said filte r assembly.
  • the present invention provides a compressor system comprising a compressor having an inlet throttle valve with said compressor being adapted to discharge a mixture of compressed gas and liquid into a separator vessel, a final filter configuration arranged to receive compressed gas with entrained liquid droplets from said separator vessel and to discharge therefrom substantially clean compressed gas, and a liquid return communication means from said separator vessel to an inlet zone of said compressor, said compressor system being characterised in that said final filter configuration and said inlet throttle valve are arranged in a combined assembly.
  • pressurised gas from said final filter element is communicated through valve means in said combined assembly to the inlet zone of said compressor.
  • a minimum pressure valve is arranged in a compressed gas discharge passage of said combined assembly. It will be recognised by those skilled in the art that the minimum pressure valve might simply comprise a restricted orifice, however, normally a non-return valve would also be required.
  • a compressor system comprising a compressor having an inlet throttle valve with said compressor being adapted to discharge a mixture of compressed gas and liquid into a separator vessel, a final filter configuration arranged to receive compressed gas with entrained liquid droplets from said separator vessel and to discharge therefrom substantially clean compressed gas, and a liquid return communication means from said separator vessel to an inlet zone of said compressor, said compressor system being characterised in that said final filter configuration is arranged separate from said separator vessel and includes a minimum pressure valve in a clean compressed gas discharge passage in said configuration.
  • Figure 1 is a schematic flow diagram of a compressor system utilising a control valve arrangement according to a preferred embodiment of the present invention
  • Figure 2 is a longitudinal cross-sectional view of an embodiment of a control valve capable of use in a system similar to Figure 1 intended for stop/start operation and for mid power range compressors, typically of the order of five to ten horsepower;
  • Figure 3 is a longitudinal cross-sectionai view of the control valve of Figure 2 taken along line III-III;
  • Figure 3A is a detailed cross-sectional view of the area X shown in Figure 3;
  • Figure 4 is a cross-sectional view taken along line IV-IV of Figure 3;
  • Figure 5 is a longitudinal cross-sectional view similar to Figure 3 of a further embodiment of a control valve according to the present invention.
  • Figures 6 and 6A are cross-sectional views taken along line VI-VI of Figure 5 showing different embodiments;
  • Figure 7 is a longitudinal cross-sectional view of a still further preferred embodiment of a control valve capable of use in a system similar to Figure 1 intended for continuous operation and for mid power range compressors, typically of the order of five to ten horsepower;
  • Figure 8 is a longitudinal cross-sectional view taken along line VIII-VIII of Figure 7;
  • Figure 9 is a cross-sectional view taken along line IX-IX of Figure 8;
  • Figure 10 is a longitudinal cross-sectional view of a still further preferred embodiment intended for stop/start operation of bw powered compressors, typically of the order of up to about five horsepower;
  • Figure 11 is a longitudinal cross-sectional view taken along line Xl-XI of Figure
  • Figure 12 is a cross-sectional view along line XII-XII of Figure 11;
  • Figure 13 is a partial cross-sectional view along line C-C of Figure 12;
  • Figure 14 is a part cross-sectional view of a still further preferred embodiment intended for use with higher powered compressors;
  • Figure 15 is a detailed part cross-sectional view showing a still further alternative arrangement
  • Figure 16 is a cross-sectional view taken along lines III-III of Figure 17 showing a further alternative form of control valve arrangement in accordance with another preferred embodiment of the present inventbn;
  • Figure 17 is a cross-sectional view taken along line VII-VII of Figure 16;
  • Figure 18 is a cross-sectional view taken abng line V-V of Figure 16;
  • Figure 19 is a cross-sectional view taken abng line VI-VI of Figure 16;
  • Figure 20 is a view similar to Figure 18 showing the valve arrangement in an unbaded state.
  • Figure 21 is a view similar to Figures 18 and 20 showing the vaive arrangement in a baded state.
  • the flooded compressor system 10 comprises a screw compressor unit 11 driven by a motor M.
  • An inlet control valve arrangement 12 is provided which receives air to be compressed at 13 preferably via an inlet filter (not shown).
  • the control valve arrangement 12 includes an inlet throttle valve 14 which directs air via a line or passage 24 to the compressor unit 11. Clean compressed air is discharged abng line 15 to a receiver storage container 22.
  • a separator vessel 23 discharges a mixture of compressed air and oil via a line 16 into a separator vessel 23.
  • the compressed air (and some entrained oil droplets) is passed via a line 17 to a final filter assembly 25 (as described hereinafter) mounted from the main throttle valve 14.
  • a final filter assembly 25 (as described hereinafter) mounted from the main throttle valve 14.
  • Separated oil from the separator vessel 23 is returned to the compressor unit 11 via line 18.
  • An oil cooler and filter would normally be provided in this line or a thermal by-pass valve might be provided to bypass the cooler at certain stages of operation, if desired.
  • the clean compressed air discharged from the filter assembly 25 is directed via communication means 27 into a minimum pressure vaive (MPV) 28 forming part of the valve arrangement 12.
  • MPV minimum pressure vaive
  • the minimum pressure valve 28 remains cbsed until a minimum pressure achieved within separator vessel 23 is reached and thereafter the minimum pressure valve opens. With the minimum pressure valve 28 open, compressed air is directed via communication means 15 into the receiver 22 and this pressure is also directed onto a pressure switch (PS) 30 via a communicatbn means 31.
  • PS pressure switch
  • the pressure switch 30 acts to keep the discharged compressed air between predetermined upper and lower pressure limits, for example between six (6) and seven (7) bars. When the upper limit is reached, the pressure switch 30 opens to direct pressure via communication means 32 on to a vent vaive (VV) 33 which acts to vent excess pressure by connecting line 64 with a vent line 34.
  • VV vent vaive
  • the pressure of the compressed gas in line 34 may be communicated via communication means 35 back into the inlet throttle valve 14 which acts to close the throttle valve and inject pressurised air into the inlet of the compressor unit 11.
  • a non-return valve might be provided in line 35.
  • FIG. 1 illustrate various sectional views of preferred forms of control valve arrangements 12.
  • the arrangement comprises a filter assembly 25 mounted to a support member 37.
  • the member 37 comprising two plates or blocks 38 and 39 in which various passages and valve elements are located as described hereinafter.
  • a diaphragm member 68 separates the plates or blocks 38 and 39 which also acts as a sealing gasket therebetween.
  • the filter assembly 25 includes an outer shell 46 which is cup shaped and configured to withstand the gas pressures for which the system is designed.
  • the shell 46 is permanently or reieasably secured in a seating manner by any suitable means to the block 38 to define an enclosed space 80.
  • An annular coalescent type filter element 81 is provided within the space 80 having annular walls of filter material through which compressed gas is adapted to pass.
  • One end of the element 81 is fully cbsed by an end cap 82 and a second annular end 87 of the element 81 is sealed against the block 38 using a sealing gasket or the like 83.
  • a spring 94 urges the element 81 into sealing engagement.
  • any other form of sealing could be used (permanent or reieasable) such that an outer space 84 and an inner space 85 is created from the e ⁇ cbsed space 80 such that gas can only flow between the inner and outer spaces through the filter material 86.
  • the shell or housing 46 is bolted or otherwise secured to block 38 to seal the housing 46 to the block in a manner enabling removal thereof for servicing the filter element 81 as may be desired.
  • the bolts may be empbyed to secure the housing 46 and the blocks 38, 39 together.
  • the housing 46 may include a screw thread arrangement at its mouth to enable it to be secured to the block 38.
  • compressed gas and entrained liquid droplets is received via line 17 by an inlet connection 88 leading to a semi circular manifold 89 in the block 38.
  • This gas and liquid fbws into the space 84 and through the filter material 86 to remove the liquid droplets therefrom.
  • Clean compressed gas is then removed from the inner space 85 via an extension tube 90 and an outlet passage 91 within the block 38.
  • the minimum pressure valve 28 is located in this discharge passage 91.
  • the valve 28 is cbsed by a piston member 53 being urged by a spring 54 against a valve seat around passage 91.
  • the piston 53 moves against the force of the spring 54 and pressurised gas flows into a passage 55 (see Figures 4 or 6) and thereafter into the discharge line 1 5.
  • the passage 55 is communicated through a passage 92 in block 38 to the pressure switch 30.
  • the pressure switch 30 opens at a bwer predetermined pressure (e.g. six bars) and cbses at an upper predetermined pressure (e.g. seven bars).
  • the vent valve 33 opens passage 64 from the discharge passage 91 to vent the pressurised gas.
  • the main throttle valve 14 comprises a valve member 67 supported by the diaphragm 68 to move upwardly and downwardly.
  • a spring member 98 is provided to urge the member 67, however, it should be appreciated that the spring member 98 is not essential.
  • a reduced diameter conduit 69 communicates the chamber 66 above the member 67 to the inlet zone 70 leading via line or passage 24 to the compressor unit 11.
  • the valve member 67 rests on a valve seat 71 surrounding the inlet zone 70 so that this communication zone is cbsed. I n consequence, vacuum conditions are rapidly built up in the zone 70 which is communicated to the chamber 66 above the diaphragm.
  • a conduit 26 communicating with the base of the inner zone 85 of the filter assembly 25 is provided to drain oil collected in this base back into the inlet of the compressor unit 11.
  • a valve device 98 may be provided in the passage 25.
  • a simple construction may be used, however, both have the disadvantage that the relatively small openings may become blocked in use.
  • large passage dimensions can be maintained by using a labyrinth restrictor device 100 comprising a plurality of plates 101 each with a flow opening
  • FIGS. 3 to 4 of the accompanying drawings show an embodiment intended for stop/start operation.
  • the pressure switch 30 senses same and stops the motor M driving the compressor.
  • the motor M is re-started to drive the compressor 11.
  • the spring 99 acts to seat the member 67 so as to close the inlet zone 70.
  • the diaphragm 68 also moves downwardly to force its loose support ring 105 downwardly so that a downward force acts on the valve stem 107 of a poppet valve 106 to open this valve.
  • pressurised gas is led from the clean gas inner zone 85 via passage 108 through the vaive 106 into the zone 72 and ultimately to atmosphere via the inlet 13.
  • FIGS 5, 6 and 6A illustrate further alternative embodiments.
  • this pressure is, as discussed above, vented via the vent valve 33 and some of this pressurised air is applied to the chamber 66 via the passage 35 and also some of this air is introduced into the inlet passage 24 via the conduit 69.
  • the pressure in the chamber 66 causes the valve member 67 to close thereby preventing entry of atmospheric air from valve inlet 13 into the compressor inlet 70 and at the same time pressurised air is injected into the compressor inlet 70 to prevent the compressor compressing what air remained in the inlet over high imposed compression ratios.
  • pressurised air is injected into the compressor inlet 70 to prevent the compressor compressing what air remained in the inlet over high imposed compression ratios.
  • Figure 6A illustrates a further alternative where the pressure switch 30 and air vent valve 33 are formed as valves functioning in the block 38 rather than as separate attached devices as depicted in Figure 6.
  • the pressure switch 30 and air vent valve 33 are formed as valves functioning in the block 38 rather than as separate attached devices as depicted in Figure 6.
  • this pressure is sufficient to lift the piston 109 against the spring 110 and this pressure is communicated via passage 111 to the top of the minimum pressure vaive 28 to ctose this valve and simultaneously via passage 1 1 2 to the top of the piston 113 in the vent valve 33.
  • Figures 7 to 9 of the accompanying drawings show a further alternative similar to Figures 2 to 4 but in this case adapted for continuous operation.
  • Reference numerals used in the preceding discussion identify the same features in Figures 7 to 9.
  • Figures 10 to 13 illustrate a simplified control arrangement intended for use on low horsepower compressor systems (typically up to five horsepower) operated on a start/stop basis. Again, reference numerals used in the preceding discussbn identify similar features in this embodiment.
  • the member 67 is urged by the spring 99 against the associated valve seat thereby closing the inlet zone 70. Vacuum conditions are rapidly created in the zone 70 which is communicated along passage 69 to the region 66 above the diaphragm 68.
  • a simple minimum pressure valve 28 is built into the block 38 beneath the clean compressed air pipe 90, the valve 28 comprising a valve member 120 urged by a spring 121 against the base of the pipe 90.
  • the valve member 120 moves against the spring 121 to allow discharge of the compressed gas along the pipe 90, past the valve member 120 to the- discharge passage 55 and line 15.
  • the pressure in the discharge pipe 90, when the valve member 120 is open is also communicated via a passage 122 to a pressure switch
  • the pressure switch 30 When the pressure reaches an upper predetermined level, the pressure switch 30 is activated to stop the motor M driving the compressor unit. Pressure from the filte r inner zone 85 is communicated via the pipe 90 and an opening 123 to the region 66 above the diaphragm 68. As a result, the valve member 67 immediately seats to close the inlet zone 70 and this elevated pressure is applied to an elastomeric cup diaphragm
  • FIG. 13 illustrates a simple oil purge line 129 which passes through a labyrinth type restrictor device 130 (similar to that shown in Figure 3A) to pass oil collected in the base region of the inner filter zone 85 into the region 66 and from there via passage 69 into the inlet zone 70 for the compressor 11.
  • FIGS 14 and 15 illustrate still further embodiments adapted for use in relation to higher powered compressors, for example 30 horsepower compressors.
  • features not illustrated may be as disclosed in any of the previously discussed embodiments.
  • a pair of poppet type valves 130 and 131 are employed, mounted in the block 39, with their valve stems 132, 133 being moved downwardly by movement of the free diaphragm support ring 105 downwardly under action from the diaphragm 68, when the valve member 67 is seated to close the inlet zone 70.
  • the valve 130 is open and the compressed gas is discharged via the passage 108 through the region 72 to the intake 13.
  • valve 131 might be further modified to both allow injectbn of pressurised air into the zone 70 when the valve member 67 cbses and to permit a continuous purging of oil from the base of the inner filter zone 85 abng the same passage, thereby minimising fabrication costs.
  • passage 134 provides both the means for communicated pressurised air but also the oil drain or purge line.
  • the vaive stem 133 in this case is modified to have a narrow bore passage 136 continuously open to drain oil into the inlet zone 70.
  • the arrangement comprises a filter assembly 25 mounted to a valve housing 37.
  • the valve housing 37 comprises a plurality of plates or blocks 38, 39, 40, 41 and 42 in which varbus passages and valve elements are located as described hereinafter. At least the upper plates or bbcks are separated by gasket members 43, 44 and 45 which also may include holes, passages or the like as required and as described hereinafter.
  • the filter assembly 25 includes an outer shell 46 which has an annular coalescent type filter element located therein.
  • a central passage 47 is provided that communicates to an inner zone within the filter element and has a connection means 48 in the form of an outer screw thread that enables the filter assembly 25 to be screwed down onto the top face of the plate 38 so that the rim of the housing 46 is sealed against sealing surfaces on the plate 38.
  • a connection means 48 in the form of an outer screw thread that enables the filter assembly 25 to be screwed down onto the top face of the plate 38 so that the rim of the housing 46 is sealed against sealing surfaces on the plate 38.
  • an outer space is provided between the shell 46 and the filter element and the inner one is located within the filter element itself.
  • a distributbn plate within the neck of the shell 46 enables gas flow to be directed to the outer space and this gas flow is received from line 17 to a connection zone 49 in the block 39 (see Figure 17). Clean compressed air discharged from the passage 47 of filter assembly 25 is directed into a passage 50 formed in the block 39, gasket 44 and plate 40.
  • this compressed air from passage 50 is directed into a transverse passage 51 formed in the block 41 and thereafter through a vertical passage 52 formed through the gaskets 45, 44 and plate 40 into the base of the minimum pressure valve 28.
  • the valve 28 is cbsed by a piston member 53 being urged by a spring 54 against a valve seat around passage 52.
  • the piston 53 lights against the force of the spring 54 and pressurised air flows into chamber 55.
  • a transverse passage 56 through block 39 communicates this chamber 55 to a discharge connection 57 enabling connection of the minimum pressure valve 28 via line 15 to the receiver 22 (see Figure 19).
  • the vent vaive 33 comprises a spool valve element having an upper piston 60 connected to and of greater diameter than a lower piston 61 with a spring 62 urging the bwer piston 61 to seal against a vaive seat in chamber 63.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Compressor (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)

Abstract

Système de commande de compresseur noyé comprenant un compresseur noyé (11), une soupape d'étranglement d'admission (14) ainsi qu'un filtre final (25) monté séparé d'un récipient séparateur (23) dans lequel la soupape d'étranglement d'admission (14) et le filtre final (25) forment un ensemble combiné, le filtre final (25) comprenant également une soupape de pression minimale (28) régulant la décharge de gaz comprimé propre provenant du filtre final (25), ayant pour effet de réduire le nombre de raccords de tuyaux dans le système.
EP92921578A 1991-10-14 1992-10-14 Combinaison de commande d'admission pour systeme de compresseur Expired - Lifetime EP0608311B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AU8876/91 1991-10-14
AUPK887691 1991-10-14
PCT/AU1992/000547 WO1993008404A1 (fr) 1991-10-14 1992-10-14 Combinaison de commande d'admission pour systeme de compresseur

Publications (3)

Publication Number Publication Date
EP0608311A1 true EP0608311A1 (fr) 1994-08-03
EP0608311A4 EP0608311A4 (fr) 1995-08-02
EP0608311B1 EP0608311B1 (fr) 1997-11-26

Family

ID=3775745

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92921578A Expired - Lifetime EP0608311B1 (fr) 1991-10-14 1992-10-14 Combinaison de commande d'admission pour systeme de compresseur

Country Status (7)

Country Link
EP (1) EP0608311B1 (fr)
JP (1) JPH07500167A (fr)
AT (1) ATE160617T1 (fr)
AU (1) AU668110B2 (fr)
DE (1) DE69223325T2 (fr)
ES (1) ES2112333T3 (fr)
WO (1) WO1993008404A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1292941B1 (it) * 1997-01-28 1999-02-11 Virgilio Mietto Distributore monoblocco per la regolazione automatica della pressione dell'aria in un serbatoio
IT1298378B1 (it) * 1997-12-19 2000-01-05 Chiara Perazzo Filtro disoleatore, con associata valvola di minima pressione per impianti erogatori di aria compressa.

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1134224A (en) * 1965-05-03 1968-11-20 Hymatic Eng Co Ltd Improvements relating to compressors
SE359159B (fr) * 1971-12-23 1973-08-20 Stal Refrigeration Ab
DE2821321A1 (de) * 1978-05-16 1979-11-22 Ruediger Dr Ing Klein Vorrichtung zur erzeugung von druckluft
US5142056A (en) * 1989-05-23 1992-08-25 Abbott Laboratories Retroviral protease inhibiting compounds
JPS5754157A (en) * 1980-09-19 1982-03-31 Nippon Kayaku Co Ltd L-argininal derivative and its preparation
DE3146535A1 (de) * 1981-11-24 1983-06-01 Isartaler Schraubenkompressoren GmbH, 8192 Geretsried "steuerungsvorrichtung fuer einen verdichter"
DE3149245A1 (de) * 1981-12-11 1983-06-16 Isartaler Schraubenkompressoren GmbH, 8192 Geretsried "verdichteranlage"
AU563570B2 (en) * 1983-04-08 1987-07-16 Cash Engineering Research Pty Ltd Compressor inlet valve
DE3445400A1 (de) * 1984-12-13 1986-06-19 Blitz M. Schneider Werkzeug- und Maschinenfabrik GmbH, 7715 Bräunlingen Oelabscheider
JPH075634B2 (ja) * 1987-10-30 1995-01-25 日東紡績株式会社 トリペプチド類及びこれを含有する抗プラスミン剤
IL89900A0 (en) * 1988-04-12 1989-12-15 Merck & Co Inc Hiv protease inhibitors useful for the treatment of aids and pharmaceutical compositions containing them
EP0361341A3 (fr) * 1988-09-28 1991-07-03 Miles Inc. Agents thérapeutiques contre le SIDA basés sur des inhibiteurs des protéases du HIV
JP2701932B2 (ja) * 1989-04-10 1998-01-21 サントリー株式会社 タンパク質分解酵素阻害剤
GB8909836D0 (en) * 1989-04-28 1989-06-14 Boots Co Plc Therapeutic agent

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
No further relevant documents disclosed *
See also references of WO9308404A1 *

Also Published As

Publication number Publication date
DE69223325D1 (de) 1998-01-08
WO1993008404A1 (fr) 1993-04-29
EP0608311A4 (fr) 1995-08-02
ATE160617T1 (de) 1997-12-15
JPH07500167A (ja) 1995-01-05
DE69223325T2 (de) 1998-04-16
AU2790792A (en) 1993-05-21
AU668110B2 (en) 1996-04-26
ES2112333T3 (es) 1998-04-01
EP0608311B1 (fr) 1997-11-26

Similar Documents

Publication Publication Date Title
US5803715A (en) Inlet control combination for a compressor system
US6640792B2 (en) Air/oil coalescer with an improved centrifugally assisted drainage
US6478019B2 (en) Flat low profile diesel engine crankcase ventilation filter
US5643446A (en) Fuel filter and priming pump
EP0631803A1 (fr) Combinaison de filtres à flux principal et flux secondaire avec buse à venture
US4362475A (en) Compressor inlet valve
US4768542A (en) Drain valve
CA2240781A1 (fr) Soupape de retenue multi-etagee
AU8515698A (en) Valve assembly for gas cylinder and pressure reducing valve used therefor
US4322290A (en) Filter assembly
US6167908B1 (en) Valve assembly for an apparatus under pressure
CA1091167A (fr) Filtre a cycles alternes de filtrage et de regeneration
EP0117785B1 (fr) Valve de retenue à vide
CA2484022A1 (fr) Siege de soupape pour robinet de chasse a piston
AU2790792A (en) Inlet control combination for a compressor system
US8365764B2 (en) Minimum pressure valve
US4408967A (en) Piston cylinder and head for compressors
EP0234801A2 (fr) Vanne de commande pour un fluide
EP0907537B1 (fr) Purgeur
US4124008A (en) Integrated fuel supply system for an internal combustion engine including filter, valve, and pump
MXPA04008953A (es) Valvula para filtro de fluido.
KR20190028115A (ko) 압축공기필터용 탄댐 오토드레인 장치
GB2206673A (en) Drain valve assembly
SU1375801A1 (ru) Пусковой газлифтный клапан
EP1092105A1 (fr) Valve de purge automatique

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19940321

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FR GB GR IE IT LI LU MC NL SE

A4 Supplementary search report drawn up and despatched

Effective date: 19950620

AK Designated contracting states

Kind code of ref document: A4

Designated state(s): AT BE CH DE DK ES FR GB GR IE IT LI LU MC NL SE

17Q First examination report despatched

Effective date: 19960410

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: CASH ENGINEERING RESEARCH PTY. LTD.

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE DK ES FR GB GR IE IT LI LU MC NL SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19971126

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19971126

Ref country code: DK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19971126

Ref country code: CH

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19971126

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19971126

REF Corresponds to:

Ref document number: 160617

Country of ref document: AT

Date of ref document: 19971215

Kind code of ref document: T

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REF Corresponds to:

Ref document number: 69223325

Country of ref document: DE

Date of ref document: 19980108

ITF It: translation for a ep patent filed
ET Fr: translation filed
REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2112333

Country of ref document: ES

Kind code of ref document: T3

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19981014

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19981014

26N No opposition filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990430

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20001003

Year of fee payment: 9

Ref country code: ES

Payment date: 20001003

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20001006

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20001016

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20001030

Year of fee payment: 9

Ref country code: BE

Payment date: 20001030

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20011014

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20011015

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20011015

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20011031

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20011124

Year of fee payment: 10

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

BERE Be: lapsed

Owner name: CASH ENGINEERING RESEARCH PTY. LTD

Effective date: 20011031

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020501

EUG Se: european patent has lapsed

Ref document number: 92921578.8

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20011014

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020628

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 20020501

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030501

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20021113

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20051014