EP0576415A1 - Soupape de contrôle de l'aspiration - Google Patents

Soupape de contrôle de l'aspiration Download PDF

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Publication number
EP0576415A1
EP0576415A1 EP19930890096 EP93890096A EP0576415A1 EP 0576415 A1 EP0576415 A1 EP 0576415A1 EP 19930890096 EP19930890096 EP 19930890096 EP 93890096 A EP93890096 A EP 93890096A EP 0576415 A1 EP0576415 A1 EP 0576415A1
Authority
EP
European Patent Office
Prior art keywords
seat
intake
control valve
closure body
screw 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
EP19930890096
Other languages
German (de)
English (en)
Other versions
EP0576415B1 (fr
Inventor
Friedrich Dr. Dipl.-Ing. Bauer
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.)
Hoerbiger Ventilwerke GmbH and Co KG
Original Assignee
Hoerbiger Ventilwerke GmbH and Co KG
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 Hoerbiger Ventilwerke GmbH and Co KG filed Critical Hoerbiger Ventilwerke GmbH and Co KG
Publication of EP0576415A1 publication Critical patent/EP0576415A1/fr
Application granted granted Critical
Publication of EP0576415B1 publication Critical patent/EP0576415B1/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
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S137/00—Fluid handling
    • Y10S137/907—Vacuum-actuated 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
    • Y10T137/7758—Pilot or servo controlled
    • Y10T137/7762—Fluid pressure type
    • Y10T137/7769—Single acting fluid servo
    • Y10T137/777—Spring biased

Definitions

  • the invention relates to an intake control valve for a screw compressor, in particular for a screw compressor with oil injection, which is installed in the intake line of the screw compressor and has a closure body which alternately releases or closes the intake line and with an actuating piston or an actuating diaphragm which can be displaced in a cylinder, which can be acted upon by a pressure medium, is in the drive connection in the opening direction of the intake line.
  • Intake control valves of this type are known in various designs.
  • the simple designs for screw compressors are "normally open", i.e. When the screw compressor is depressurized, the intake control valve releases the passage cross-section of the intake line.
  • the screw compressor starts up with the intake control valve open, which means that the drive motor is immediately loaded by the full compression work. Only when a sufficient operating pressure has been built up can the intake control valve be closed completely or partially to reduce the delivery rate.
  • This embodiment thus has the disadvantage that the drive motor is heavily loaded and is also overloaded when the vehicle is started frequently in the time unit.
  • the spring force holding this closed must be overcome in this known embodiment to open the suction control valve, which is usually done by a differential piston.
  • the piston area of the differential piston must be correspondingly large, because the force exerted by it must overcome on the one hand the spring force acting on the intake control valve and on the other hand the gas pressure acting on the intake control valve due to the built-up operating pressure in the closing direction, in addition to this also the increase in spring force due to the spring stiffness .
  • a suction control device of this type is known from DE-OS 29 44 053.
  • the pressure that builds up overcomes the spring force and opens the suction line.
  • the change in the flow cross-section for regulating the delivery rate is carried out with the aid of a further control piston, which is acted upon by a control pressure, for example the network pressure, and loads the closure body in the direction of the spring force, so that the operating pressure present on the opposite side of the closure body is overcome.
  • a control pressure for example the network pressure
  • the invention has for its object to simplify the structure of the known intake control valves and still improve them so that they can be operated with little effort without impairing the function.
  • the suction control valve designed as a double seat valve is provided with a suction seat which the closure body closes in the suction direction and a backflow seat which the closure body closes against the suction direction, and in that the closure body is one between the two seats has an intermediate position defined by an end position of the control piston or the control membrane, in which at least approximately the largest flow cross-section is released through the intake control valve and from which it can be freely adjusted as a check valve against the backflow seat.
  • the design of the intake control valve as a double-seat valve with a defined intermediate position results in a surprisingly simple structure and also an advantageous actuation.
  • the suction control valve according to the invention is closed by the suction-side vacuum when the screw compressor starts up and, after an operating pressure has built up, is opened by the pressure medium acting on the actuating piston or the actuating diaphragm into the intermediate position between the two seats.
  • the closure body of the intake control valve is raised to about half the stroke between its two seats and releases the full intake cross-section in this position.
  • the actuating piston or the actuating diaphragm only has to overcome the weak spring force of its or its return spring and the suction force.
  • the closing body of the intake control valve which then acts as a check valve, is pressed by the pressure medium onto the backflow seat, which it closes, regardless of the position of the actuating piston or the actuating membrane.
  • the vacuum sucks the closure body over its entire stroke onto the suction seat and closes it, so that the suction control valve then performs the "normally closed” function. This prevents overloading the drive motor.
  • the closure body is loaded by a weak spring supported on the housing, which acts on it in the direction of the backflow seat.
  • this spring supports the closing movement of the closure body in the direction of the backflow seat and ensures its rapid, full sealing, so that a backflow of pressure medium and oil mist carried into the suction line is reliably avoided.
  • a duct with a small cross section bypassing the suction seat can be provided.
  • this channel has the effect that, when the suction control valve is closed, that is to say during the start-up phase of the screw compressor, the pressure build-up is not too slow and the screw compressor is lubricated by the oil injection in good time.
  • the suction seat of the suction control valve can also be made leaky.
  • the actuating piston can be arranged in an actuating cylinder which is fastened approximately in the axis of the valve housing of the intake control valve and around which the pumped medium flows. It is a space-saving arrangement of the actuating cylinder with simple, straightforward power transmission to the closure piece of the intake control valve.
  • FIG. 1 and 2 each show a longitudinal section through an embodiment of an intake control valve according to the invention.
  • Both embodiments consist of a hollow valve housing 1 or. 1 ', which is connected with a connection opening 2 to the inlet of a screw compressor, not shown.
  • a flange 3 with fastening holes 4 for flange screws is provided for this purpose.
  • the valve housing 1 has a flow channel 5, to which the suction line 6 connects at the other housing end.
  • a return flow seat 7 is formed and at some distance from it the valve housing 1 has an inwardly projecting collar 8, which forms a suction seat 9 opposite the return flow seat 7.
  • an actuating cylinder 10 is arranged inside the valve housing 1, which can be designed as a cast part, in which an actuating piston 11 can be displaced against the force of a return spring 12.
  • the open end of the actuating cylinder 10 is closed by a screw cap 13, via which a control connection 14 opens into the actuating cylinder 10.
  • the actuating piston 11 is guided out of the actuating cylinder 10 with a rod 15, on the free end of which an extension 16 provided with a bore a plate-shaped closure body 17 is slidably mounted.
  • a weak helical spring 18 is supported on the housing of the actuating cylinder 10 and loads the closure body 17 against the backflow seat 7.
  • the closure body 17 has a seal 19, which brings about a tight closure of the backflow seat 7.
  • a channel 20 is provided in the collar 8, which bypasses the suction seat 9 of the suction control valve and thus represents a leak in the suction seat 9.
  • the intake control valve is designed as a corner valve and an actuating membrane, which is designated 11 ′, is provided for the adjustment of the closure body 17.
  • the housing 1 ' is connected at one end to the suction line 6 as in the embodiment according to FIG. 1, but the flow channel 5 opens out on the side of the housing 1' and is connected there in a manner not shown to the inlet of a screw compressor.
  • the membrane 11 ' is clamped in a pressure chamber 10', which is provided with a control connection 14, and acts on a membrane plate 11 '', which is loaded by the return spring 12.
  • the rod 15 is attached to the membrane plate 11 ′′, on which the hollow extension 16 of the closure body 17 is placed.
  • the closure body 17 is therefore largely freely displaceable relative to the actuating membrane 11 ', with only a driving connection between the rod 15 and the closure body 17 in the opening direction of the suction seat 9, etc. to an intermediate position between the intake seat 9 and the return flow seat 7.
  • this intermediate position which is caused by the stop of part of the actuating piston 11 on the actuating cylinder 10 (FIG. 1) or the diaphragm plate 11 ′′ on the valve housing 1 ′ (FIG. 2) is precisely defined, the flow cross-section through the intake control valve is fully open and largest.
  • the rod 15 is designed in coordination with the piston 11 or the membrane 11 'that adjusts it so that it can only adjust the closure body 17 to the intermediate position between the suction seat 9 and the backflow seat 7.
  • the closure body 17 can therefore not be pressed against the backflow seat 7 even at high operating pressure by the control piston 11 or the control membrane 11 '. This is closed by the closure body 17 only as a freely adjustable check valve as soon as the delivery of the screw compressor stops, etc. by the force exerted on it by the compressed medium with the support of the spring 18.
  • the medium delivered by the screw compressor, not shown, is drawn in in the direction of arrow 21 through the flow channel 5 of the intake control valve.
  • the closure body 17 of the intake control valve is in the intermediate position shown in the two drawing figures approximately in the middle between the return flow seat 7 and the intake seat 9, whereby it releases the full flow cross-section through the flow-through channel 5.
  • the helical spring 18 immediately presses the closure body 17 against the backflow seat 7, which is completely sealed by means of the seal 19. As a result, backflow of compressed medium into the intake line 6 and in particular the escape of oil injected to lubricate the compressor is avoided.
  • the coil spring 18 also causes the backflow seat 7 to remain closed even if the screw compressor is later depressurized.
  • the actuating piston 11 or the actuating membrane 11 ' is under the action of the return spring 12 in the lower end position, in which the rod 15 is retracted as far as possible into the actuating cylinder 10 or into the pressure chamber 10'.
  • the resulting negative pressure causes the closure body 17 to be detached from the backflow seat 7 and to be moved until it contacts the suction seat 9. This movement is not hindered by the relatively short rod 15 drawn back into the interior of the actuating cylinder 10 or the pressure chamber 10 '.
  • the intake control valve performs its "normally closed" function.
  • the medium conveyed by the screw compressor is sucked in through the small channel 20, which can be calibrated, so that the compressor is brought to the operating pressure in the desired slow manner, for example by inflating a pressure container connected to the screw compressor.
  • the control connection 14 is pressurized via a two-point controller and thus the actuating piston 11 or the actuating membrane 11 'is pressurized, whereupon the rod 15 lifts the closure body 17 from the suction seat 9 and brings it into the intermediate position shown in the drawing.
  • the size of the pressure of the medium supplied through the control connection 14 it is also possible to lift the closure body 17 more or less from the suction seat 9 and thus to continuously regulate the amount of medium sucked in by the screw compressor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
EP19930890096 1992-06-02 1993-05-12 Soupape de contrÔle de l'aspiration Expired - Lifetime EP0576415B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT1137/92 1992-06-02
AT0113792A AT402542B (de) 1992-06-02 1992-06-02 Ansaugregelventil

Publications (2)

Publication Number Publication Date
EP0576415A1 true EP0576415A1 (fr) 1993-12-29
EP0576415B1 EP0576415B1 (fr) 1996-03-13

Family

ID=3507401

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19930890096 Expired - Lifetime EP0576415B1 (fr) 1992-06-02 1993-05-12 Soupape de contrÔle de l'aspiration

Country Status (5)

Country Link
US (1) US5411375A (fr)
EP (1) EP0576415B1 (fr)
AT (1) AT402542B (fr)
DE (1) DE59301852D1 (fr)
FI (1) FI105413B (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101705941B (zh) * 2009-11-16 2011-10-05 南通市红星空压机配件制造有限公司 螺杆式空压机进气阀

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT403948B (de) * 1994-07-29 1998-06-25 Hoerbiger Ventilwerke Ag Ansaugregelventil für rotationsverdichter
DE19625565C2 (de) * 1996-06-26 1998-07-23 Bosch Gmbh Robert Kraftstoff-Förderpumpe für eine Kraftstoff-Einspritzpumpe für Brennkraftmaschinen
US5899435A (en) * 1996-09-13 1999-05-04 Westinghouse Air Brake Co. Molded rubber valve seal for use in predetermined type valves, such as, a check valve in a regenerative desiccant air dryer
CA2301415A1 (fr) * 1999-04-19 2000-10-19 Capstone Turbine Corporation Moteur/generatrice a aimant permanent pour compresseur/turbine a ecoulement helicoidal
US6309185B1 (en) * 1999-10-06 2001-10-30 Der-Fan Shen Flow regulator for water pump
IT1307507B1 (it) * 1999-10-21 2001-11-06 Virgilio Mietto Regolatore automatico di aspirazione dell'aria in un serbatoio.
JP4411753B2 (ja) * 2000-06-30 2010-02-10 株式会社日立プラントテクノロジー オイルフリースクリュー圧縮機
US6439261B1 (en) * 2000-12-22 2002-08-27 Carrier Corporation Pressure responsive oil flow regulating supply valve
US6666656B2 (en) 2001-10-12 2003-12-23 Hans-Georg G. Pressel Compressor apparatus
CN1320282C (zh) * 2001-12-17 2007-06-06 乐金电子(天津)电器有限公司 带有防止噪音装置的涡旋式压缩机
EP1616098A4 (fr) * 2003-04-22 2011-04-27 Conrader R Co Compresseur d'air a mecanisme de regulation d'entree d'air et mecanisme de regulation d'entree automatique
ITBO20030781A1 (it) * 2003-12-23 2005-06-24 Hoerbiger Italiana S P A Assieme di valvola di aspirazione per gruppi compressori a vite
JP4656044B2 (ja) * 2006-11-10 2011-03-23 株式会社豊田自動織機 圧縮機の吸入絞り弁
US8162068B2 (en) * 2008-06-13 2012-04-24 Vanair Manufacturing, Inc. Pilot valve, method of using, and fluid system equipped therewith
US9915373B2 (en) * 2011-07-08 2018-03-13 Fmc Technologies, Inc. Electronically controlled pressure relief valve
DE102011084811B3 (de) * 2011-10-19 2012-12-27 Kaeser Kompressoren Ag Gaseinlassventil für einen Kompressor, Kompressor mit einem derartigen Gaseinlassventil sowie Verfahren zum Betreiben eines Kompressors mit einem derartigen Gaseinlassventil
US9915265B2 (en) 2014-12-31 2018-03-13 Ingersoll-Rand Company Compressor system with variable lubricant injection orifice
CN105889051B (zh) 2015-02-16 2019-11-15 创科（澳门离岸商业服务）有限公司 用于空气压缩机的进气口控制
US11204022B2 (en) 2018-08-14 2021-12-21 Milwaukee Electric Tool Corporation Air compressor
CN109209873B (zh) * 2018-09-06 2020-07-07 辰溪县宏兴新材料科技有限公司 一种空压机用进气阀
BE1029442B1 (nl) * 2021-05-27 2023-01-09 Atlas Copco Airpower Nv Element voor het samenpersen van een gas en werkwijze voor het regelen van dergelijk element

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4708599A (en) * 1984-05-25 1987-11-24 Hitachi, Ltd. Rotary compressor apparatus
US4826134A (en) * 1987-09-14 1989-05-02 Chapman Walter R Intake valve for air compressors and the like
EP0391064A1 (fr) * 1989-04-03 1990-10-10 Dresser Industries, Inc. Soupape d'entrée pour un compresseur à vide

Family Cites Families (6)

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Publication number Priority date Publication date Assignee Title
US862867A (en) * 1906-03-28 1907-08-06 Lewis Watson Eggleston Pneumatic pumping apparatus.
GB587917A (en) * 1944-11-30 1947-05-08 Adams Ltd L Improvements in or relating to pressure operated control valves
US2961147A (en) * 1958-04-07 1960-11-22 Westinghouse Air Brake Co Control system for fluid compressors
US3982561A (en) * 1975-07-17 1976-09-28 Telford Smith, Inc. Combination surge relief and back flow prevention valve
ATE35442T1 (de) * 1983-04-08 1988-07-15 Cash Eng Co Pty Ltd Steuersystem fuer verdichter.
JPS59208196A (ja) * 1983-05-11 1984-11-26 Tokico Ltd スクロ−ル式圧縮機

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4708599A (en) * 1984-05-25 1987-11-24 Hitachi, Ltd. Rotary compressor apparatus
US4826134A (en) * 1987-09-14 1989-05-02 Chapman Walter R Intake valve for air compressors and the like
EP0391064A1 (fr) * 1989-04-03 1990-10-10 Dresser Industries, Inc. Soupape d'entrée pour un compresseur à vide

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101705941B (zh) * 2009-11-16 2011-10-05 南通市红星空压机配件制造有限公司 螺杆式空压机进气阀

Also Published As

Publication number Publication date
FI105413B (fi) 2000-08-15
ATA113792A (de) 1996-10-15
DE59301852D1 (de) 1996-04-18
EP0576415B1 (fr) 1996-03-13
AT402542B (de) 1997-06-25
US5411375A (en) 1995-05-02
FI932498A0 (fi) 1993-06-01
FI932498A (fi) 1993-12-03

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