US3260444A - Compressor control system - Google Patents

Compressor control system Download PDF

Info

Publication number
US3260444A
US3260444A US355658A US35565864A US3260444A US 3260444 A US3260444 A US 3260444A US 355658 A US355658 A US 355658A US 35565864 A US35565864 A US 35565864A US 3260444 A US3260444 A US 3260444A
Authority
US
United States
Prior art keywords
compressor
gas
inlet
pump
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US355658A
Other languages
English (en)
Inventor
Raymond F Williams
Arvid L Nelson
Raymond B Millard
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.)
Gardner Denver Inc
Original Assignee
Gardner Denver Inc
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 Gardner Denver Inc filed Critical Gardner Denver Inc
Priority to US355658A priority Critical patent/US3260444A/en
Priority to GB2428/65A priority patent/GB1087751A/en
Priority to BE659409D priority patent/BE659409A/xx
Priority to FR4905A priority patent/FR1429488A/fr
Priority to SE2269/65A priority patent/SE316261B/xx
Priority to DE1965G0043198 priority patent/DE1503540A1/de
Application granted granted Critical
Publication of US3260444A publication Critical patent/US3260444A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • 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
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
    • F04C29/0014—Injection of a fluid in the working chamber for sealing, cooling and lubricating with control systems for the injection of the fluid

Definitions

  • This invention generally concerns control means for rotary gas compressors and more particularly concerns an improved unloading system for compressors of the aforesaid type whereby the present cost of running a compressor unloaded may be substantially reduced.
  • positive displacement gas compressors of the various rotary types are unloaded by closing the compressor inlet opening thereby shutting off the flow of gas into the compression chambers of the compressor.
  • the efficiency of this method for reducing unloaded power consumption and attendant operating costs is inherently low due to cyclic expansion and recompression of trapped gas remaining inside the compressor system after closure of the inlet port.
  • the trapped gas inside the compressor system exhibits a pressure gradient increasing from inlet pressure to discharge pressure and such a gradient in pressure causes the trapped gas to circulate from the compressor discharge back toward the compressor inlet through internal leakage paths within the compressor.
  • the principal object of this invention is to provide means for unloading a positive displacement rotary compressor so that the power consumed'during unloaded operation can be reduced sufficiently to render such compressors superior, or at least competitive, in this regard to reciprocating piston compressors.
  • this invention contemplates the provision of an improved compressor control system, effective upon compressor output demand being met, for reducing, or ideally eliminating, the pressure gradient between the inlet and the discharge of a rotary com-pressor thereby eliminating or substantially reducing the power consumed by recompression of internally circulating gas.
  • Another object is to eliminate or reduce the aforementioned pressure gradient by evacuating trapped gas from the interior of the compressor.
  • Another object is to effect evacuation of the compressor as aforesaid by means of a pump device which is driven by the compressor prime mover.
  • Yet another object is to evacuate the compressor as 3,25%,4441 Patented July I2, 1966 aforesaid by a pump device which normally functions during loaded operation to supply liquid under pressure to the interior of the compressor to seal and cool the same.
  • Still another object is to provide a compressor unloading system of the aforedescribed type which is characterized by efficiency and economy of operation and by simplicity and low cost of construction.
  • FIG. 1 is a schematic illustration of a gas compressing system embodying the present invention
  • FIG. 2 is an enlarged fragmentary view of the motorcompressor unit shown in FIG. 1 having a portion of the casing broken away;
  • FIG. 3 is a view taken along lines 33 of FIG. 2;
  • FIG. 4 is an enlarged View of a check valve shown in FIG. 1 having a portion of the valve housing broken away;
  • FIG. 5 is an enlarged sectional view of a pilot valve shown in FIG. 1;
  • FIG. 6 is an enlarged sectional view of a control valve shown in FIG. 1;
  • FIG. 7 is a view similar to FIG. 6 of another control valve shown in FIG. 1;
  • FIG. 8 is an enlarged sectional view of a choke device shown in FIG. 1.
  • FIG. 1 of the drawings illustrates a gas compressor control system which, in accordance with this invention, is adapted to load and unload a motor-compressor unit 10 which comprises a screw type rotary compressor 12 driven by an electric motor 14.
  • the illustrative com-pressor 12 comprises a stationary housing, indicated in its entirety'by numeral 16, and a pair of complementary, meshing rotors 18 and 20 which are rotatively journalled within the housing.
  • the pluralpart housing 16 comprises a central cylinder or casing 22 which is closed at opposite ends by removable end walls or heads 24 and 26.
  • the casing and the heads are provided with abutting flanges and suitable fasteners for securing the parts in place; and, a gear pump 96 is removably secured to the head 26.
  • the central casing member 22 is provided with intersecting parallel bores 28 and 30 which are in open communication with an inlet port 32, opening substantially radially through casing 22 and the inlet-end head 24, and with a discharge port 34- opening substantially axially through the head 26 to a gas discharge pipe 36.
  • the base portion 22a of casing 22 is provided with certain cavities and passage-ways, to be hereinafter described, and is closed by a removable base cover plate 38.
  • the compressor operating means comprise complementary helically threaded rotors 18 and 20 which are rotatively journalled in the parallel bores 28 and 30.
  • Rotor 18 has four generally convex lobes and is commonly denominated the main rotor; and, rotor 20 has six generally concave grooves and is commonly denominated the gate rotor.
  • the rotors are provided with reduced diameter shaft extensions 40 and 42 which are formed integrally and coaxially with the helical body portions of the respective rotors.
  • the extending rotor shafts 40 and 42 are rotatively journalled at their opposite ends by antifriction bearing assemblies mounted in the heads 24 and 26.
  • a bearing assembly 44 is mounted in the inlet head 24 to support and journal the inlet end of the main rotor shaft 40; and, a bearing assembly 46 is mounted in the discharge head 26 to support and journal the discharge end of the main rotor shaft in a similar manner.
  • the main rotor shaft 40 extends through the inlet head 24 into driving engagement with the drive shaft 48 of the electric motor 14.
  • the cooperating rotors are synchronized or timed to provide interrotor clearance by means of suitable gearing 50 mounted on the inlet ends of the rotor shafts 40 and 42.
  • a plurality of compression chambers are for-med by the mating main rotor lobes and gate rotor grooves as the rotors 18 and 20 rotate in opposite directions and in approximate contact with the walls of the casing bores 28 and 30.
  • the compression chambers sequentially open to their full volume and fill with gas while in communication with the inlet port 32.
  • the volume of gas contained in the compression chambers is progressively reduced by the shortening of the length of each chamber from its inlet end to its discharge end; and, with a decrease in volume, the internal pressure in each chamber is progressively raised from inlet pressure to discharge pressure.
  • the compression chambers are axially displaced toward the discharge port 34 and are sequentially brought into gas-delivering registration with the discharge port.
  • the discharge gas is conducted from the compressor discharge port 34 to a receiver tank 52 by means of the discharge pipe 36, the latter having a check valve 54 therein to prevent the backward fiow of receiver gas to the compressor when the compressor is unloaded or is stopped.
  • the check valve 54 is conventionally constructed and generally comprises a twopart housing 56; a plural port seat 58, and closure members 60 which are biased to a seated or closed condition by springs 62. It will be understood that the bias of the springs 62 is overcome by the pressure of the compressor discharge gas operating on the closure members 60.
  • gas is drawn into the interior of the compressor housing 16 through a gas filtering device 64 and an inlet valve assembly 66; and, the gas is thereafter compressed and discharged to the receiver tank 52 in the manner hereinbefore described.
  • the flow of gas into the inlet port 32 of compressor 12 may be interrupted by the inlet valve 66 when the gas pressure in the receiver tank 52 reaches a rated value.
  • a pressure sensitive pilot valve 68 is connected between a final delivery pipe 70 and the inlet valve 66; and, upon receiver pressure having reached rated value, a pilot valve closure member 72 will be unseated against the adjustable bias of a spring 74 thereby permitting pilot gas to flow from the delivery pipe 70 through a control line 76 communicating between the pilot valve outlet 78 and a piston chamber 80 of inlet valve 66.
  • a fluid-actuated piston member 82 and an attached closure member 84 of the inlet valve 66 are urged to the position shown in FIG.
  • valve seat 86 when the compressor 12 is running loaded; however, when pilot gas is communicated to the piston chamber 80 as aforedescribed, the piston 82 and valve closure member 84 will be forcibly shifted to seat the latter on valve seat 86 thereby placing the inlet valve 66 in a closed condition.
  • a suitable liquid medium may be supplied under pressure to a gallery 88 relieved in the casing base 22a for injection into the interior of the housing 16 through a plurality of spaced apertures 90 for the purpose of sealing clearances between the meshing rotors and between the rotors and the housing 16 and for removing the heat of compression generated during loaded operation.
  • the selected liquid medium has good lubricating properties, it may be desirable to employ the sealing and cooling liquid for lubricating certain moving parts of the compressor.
  • oil is employed and, as shown by FIG. 2, the discharge end of gallery 88 communicates with the aforementioned bearing assembly 46 by means of a passageway 92 defined in the casing base 22a and the discharge head 26.
  • oil from gallery 88 is supplied to the main rotor bearing assembly 44 through a passageway 94 defined in the casing base 22a and the inlet head 24.
  • the lubricating system for the gate rotor bearing assemblies is substantially identical in structure and operation to that described above in connection with the main rotor bearing assemblies 44 and 46. If the sealing and cooling liquid should comprise water, for example, it would, of course, be desirable to provide a separate lubricating system.
  • a positive displacement gear pump 96 of conventional construction and suitable capacity is drivably connected directly to the discharge end of the main rotor shaft 40 and is provided with an inlet 96a and an outlet 96b.
  • the gear pump 96 draws separated oil from the bottom or sump portion of tank 52 through a pipe 98, a radiator type heat exchanger 100, a pipe 102, a pump inlet valve 104, a pipe 106 and pump inlet 96a.
  • the oil pump discharge is communicated to the gallery 88 through pump outlet 96b, a pipe 108, a pump discharge valve 110 and a pipe 112.
  • the controlling functions and construction of valves 104 and 110 will be hereinafter more fully described.
  • an object of this invention is to reduce or eliminate such recirculation and recompression created by the undesirable gas pressure gradient between the inlet and discharge of compressor 12 by evacuating the trapped gas from the interior of the compressor housing and discharge pipe 36.
  • a pumping device is employed for this purpose; and, by means of a novel arrangement of valves and pipes, the aforedescribed oil circulating pump 72 is advantageously connectable in circuit with the compressor discharge opening 34 to evacuate gas and oil from the interior of the compressor 12.
  • this aspect of the invention is accomplished by means of the aforementioned pump control valves 104 and 110.
  • Control valve 104 is operable to connect the pump inlet 96a and pipe 106 interchangeably to pipe 102 leading to tank 52 or to a pipe 113 which joins with the discharge pipe 36 at a point between the compressor discharge port 34 and the check valve 54.
  • pipe 106 is in communication with pipe 102 by means of valve chambers 114 and 116 which are in open communication through a port 118 in an internal wall 120.
  • Another port 122 opening from chamber 114 is closed by a valve closure member 124 which seats on an internal wall 126 under the bias of a spring 128.
  • the closure member 124 is shiftable by an attached valve-actuating piston 130 to close port 118 and to open port 122 thereby communicating pipes 106 and 113 through chamber 114, port 122 and a chamber 132.
  • Control valve 110 is operable to connect the pump outlet 96b and pipe 108 interchangeably to pipe 112 leading to the gallery 88 or to a pipe 134 leading to the gas receiver-oil sump tank 52.
  • pipe 108 With the compressor running loaded, pipe 108 is in communication with pipe 112 by means of valve chambers 138 and 140 which are in open communication through a port 142 in an internal wall 114. Another port 146 opening from chamber 138 is closed by a valve closure member 148 which seats on an internal wall 150 under the bias of a spring 152. In a manner to be described, the closure member 148 is shiftable by an attached valve-actuating piston 154 to close port 142 and to open port 146 thereby communicating pipes 108 and 134 through chamber 138, port 146 and a chamber 156.
  • control valve-chambers 132 and 156 comprise cylinders for pistons 130 and 154, respectively; and, the outlet 78 of pilot valve 68 is connected to these cylinders by branches of a control line 158 which communicates with control line 76.
  • the inlet valve 66 and the pump control valves 104 and 110 will be in the condition shown in the drawings.
  • the closure member 84 of the inlet valve 66 will be open thereby permitting the rotors 18 and 20 to draw gas into the housing 16 and to compress the gas to a final discharge pressure which may conveniently be assumed to be 100 p.s.i.g.
  • the discharge gas enters the receiver tank 52 through pipe 36 and check valve 54, and, after entrained oil is separated therefrom, the gas is delivered through the pipe 70 to any desired gas supply system.
  • the oil pump 96 is driven by the main rotor shaft 40 and has its inlet 96a connected to the bottom sump portion of tank 52 by means of pipe 106, control valve 104, pipe 102, oil cooler 100, and pipe 98.
  • the pump outlet 96b is connected to the gallery 88 by pipe 108, control valve 110 and pipe 112; and, by this means oil is supplied under pump discharge pressure to the rotor bearings and to the compression chambers of the compressor. 'When the demand for receiver gas decreases for one reason or another, the gas pressure in tank 52 and delivery pipe 70 willincrease to rated output pressure of 100 p.s.i.g. making it possible to unload the compressor to reduce the power consumed by the motor 14.
  • the illustrative electric motor 14 is of the constant speed type and that the compressor 12 is operated at constant speed to meet a fluctuating demand.
  • An increase in receiver pressure will be sensed by the pilot valve 68; and, when receiver pressure reaches 100 p.s.i.g. or above, valve-actuating gas will be passed by the pilot valve and communicated simultaneously to the inlet valve 66 and to the pump control valves 104 and 110.
  • the trapped gas within the housing 16 would conventionally be subjected to a pressure gradient ranging from approximately 100 p.s.i.g. at the compressor discharge to approximately zero p.s.i.g. or less at the compressor inlet.
  • Such a pressure difierential of approximately 100 pounds would be suflicient to cause the trapped gas to flow back from compressor discharge toward compressor inlet through internal clearances between the rotors 18 and 20, between the walls of bores 28 and 30 and the rotors, and between the ends of the rotors and the housing end walls 24 and 26
  • this leakage gas flows toward the compressor inlet to points of diminishing pressure, it expands and again fills the compression chambers toward the low pressure end of the rotor screws.
  • the expanded gas is then recompressed to discharge pressure.
  • the pressure gradient between the opposite ends of the compressor 12 causes trapped gas to circulate internally and to be cyclically compressed and expanded with a consequent waste of the power expended in recompressing the trapped gas.
  • the aforedescribed oil pump 96 is employed to draw gas from the compressor discharge port 34 to reduce substantially or to eliminate the undesirable pressure gradient within the compressor housing.
  • pilot valve 68 opens to actuate inlet valve 66
  • pilot gas is simultaneously supplied to pump control valves 104 and through lines 76 and 158.
  • the piston member of valve 104 will be shifted downwardly against the bias of spring 128 to open port 122 and to close port 118.
  • This valving action etfectively disconnects the pump inlet 96a from the sump portion of tank 52 and connects the pump inlet 96a to the discharge port 34 of the compressor housing 16 by means of the pipe 113 and the discharge pipe 36.
  • the pilot valve closure member 72 When the demand for receiver gas again increases and the delivery pressure within tank 52 and delivery pipe 70 decreases below the minimum rated delivery pressure, the pilot valve closure member 72 will seat, thereby interrupting the supply of pilot gas to the inlet valve 66 and the control valves 104 and 110 and causing the piston chambers of these valves to be vented to atmosphere through a passage 164 in the spring adjusting member 166 of the pilot valve 68.
  • the valve 66 will then open to admit gas to the housing 16 thereby restoring the compressor 12 to its loaded condition; and, simultaneously, the control valves 104 and 110 will disconnect th pump 96 from the compressor discharge port 34.
  • valves 104 and 110 connects the pump 96 between the housing 16 and the tank 52 to effect evacuation of trapped gas from the interior of the compressor.
  • the pump 96 should remove all trapped gas from the housing 16 and discharge pipe 36 and should create a vacuum therein so that the rotors 18 and 20 perform no work in compressing trapped gas; however, the degree to which this ideal may be achieved is limited in practice by the efliciency of the pump 96.
  • the pressure at the discharge of a compressor having a rated discharge pressure of 100 p.s.i.g. has been reduced to approximately 1.5 p.s.i .g.
  • a gas compressor having inlet and discharge openings; closure means for said inlet opening; pump means 8 connectable with the interior of said compressor for removing gas trapped therein upon closure of said inlet opening; a gas receiver; a source of liquid; and control means for said pump means operable to connect the same interchangeably between said source of liquid and the interior of said compressor and between the interior of said compressor and said gas receiver.
  • control means comprises first fluid conducting means operable to connect the inlet of said pump interchangeably to said source of liquid and to said compressor discharge opening; and second fluid conducting means operable to connect the outlet of said pump interchangeably to the interior of the compressor and to said gas receiver.
  • first and second fluid conducting means include fluidactuated valves having valve actuating members responsive to changes in pressure in said gas receiver.
  • conduit means includes a choke for restricting fluid flow therethrough.

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)
US355658A 1964-03-30 1964-03-30 Compressor control system Expired - Lifetime US3260444A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US355658A US3260444A (en) 1964-03-30 1964-03-30 Compressor control system
GB2428/65A GB1087751A (en) 1964-03-30 1965-01-20 Control system for a positive displacement rotary compressor
BE659409D BE659409A (ko) 1964-03-30 1965-02-08
FR4905A FR1429488A (fr) 1964-03-30 1965-02-09 Système de commande d'un compresseur
SE2269/65A SE316261B (ko) 1964-03-30 1965-02-22
DE1965G0043198 DE1503540A1 (de) 1964-03-30 1965-03-27 Gaskompressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US355658A US3260444A (en) 1964-03-30 1964-03-30 Compressor control system

Publications (1)

Publication Number Publication Date
US3260444A true US3260444A (en) 1966-07-12

Family

ID=23398292

Family Applications (1)

Application Number Title Priority Date Filing Date
US355658A Expired - Lifetime US3260444A (en) 1964-03-30 1964-03-30 Compressor control system

Country Status (6)

Country Link
US (1) US3260444A (ko)
BE (1) BE659409A (ko)
DE (1) DE1503540A1 (ko)
FR (1) FR1429488A (ko)
GB (1) GB1087751A (ko)
SE (1) SE316261B (ko)

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3506376A (en) * 1966-11-10 1970-04-14 Peugeot Method and apparatus for regulating a compressed gas producer
US3582233A (en) * 1969-04-24 1971-06-01 Worthington Corp Rotary compressor control system
DE2446378A1 (de) * 1973-11-26 1975-05-28 Hokuetsu Kogyo Co Oelgekuehlter umlaufverdichter
US3961862A (en) * 1975-04-24 1976-06-08 Gardner-Denver Company Compressor control system
US4035114A (en) * 1974-09-02 1977-07-12 Hokuetsu Kogyo Co., Ltd. Method for reducing power consumption in a liquid-cooled rotary compressor by treating the liquid
US4052135A (en) * 1976-05-11 1977-10-04 Gardner-Denver Company Control system for helical screw compressor
US4173440A (en) * 1977-06-17 1979-11-06 Compagnie Industrielle Des Telecommunications Cit-Alcatel Method and device for lubricating compressors
US4326839A (en) * 1979-12-06 1982-04-27 Tecumseh Products Company Cylinder unloading mechanism for refrigeration compressor
EP0184329A1 (en) * 1984-11-19 1986-06-11 The Hydrovane Compressor Company Limited Positive displacement air compressors
US5171130A (en) * 1990-08-31 1992-12-15 Kabushiki Kaisha Kobe Seiko Sho Oil-cooled compressor and method of operating same
US5388967A (en) * 1993-03-10 1995-02-14 Sullair Corporation Compressor start control and air inlet valve therefor
US5456582A (en) * 1993-12-23 1995-10-10 Sullair Corporation Compressor inlet valve with improved response time
US5667367A (en) * 1994-04-08 1997-09-16 Kabushiki Kaisha Kobe Seiko Sho Air compressor
US6039551A (en) * 1996-06-07 2000-03-21 Matsushita Electric Industrial Co., Ltd. Gear pump for use in an electrically-operated sealed compressor
US6283716B1 (en) 1997-10-28 2001-09-04 Coltec Industries Inc. Multistage blowdown valve for a compressor system
US6474953B2 (en) * 2000-02-22 2002-11-05 Atlas Copco Airpower, Naamloze Vennootschap Compressor control system and method for controlling the same
US20050186095A1 (en) * 2004-02-25 2005-08-25 Zinsmeyer Thomas M. Lubrication system for compressor
CN105201789A (zh) * 2015-11-03 2015-12-30 干平 一种气动阀及变内压比调节装置
EP3014153A1 (de) * 2013-06-28 2016-05-04 GEA AWP GmbH Rückschlagventil-filter-baugruppe
CN110793161A (zh) * 2019-11-01 2020-02-14 青岛海信日立空调***有限公司 一种风冷模块机组
CN113562469A (zh) * 2021-07-15 2021-10-29 合肥科狮机械科技有限公司 一种自控节能型气力输送站
US11204029B2 (en) * 2018-11-14 2021-12-21 Quincy Compressor Llc Loadless start valve for a compressor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3210790A1 (de) * 1982-03-24 1983-10-06 Bauer Kompressoren Druckmittelbetaetigtes steuerbares absperrventil

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1948907A (en) * 1931-04-18 1934-02-27 Egli Eugen Compressor
US2739758A (en) * 1955-03-23 1956-03-27 Jaeger Machine Co Rotary compressor
US2787411A (en) * 1952-04-28 1957-04-02 Joy Mfg Co Compressor unloading mechanism
US2977039A (en) * 1958-07-10 1961-03-28 Joy Mfg Co Control circuit
US2997227A (en) * 1958-12-17 1961-08-22 Bendix Westinghouse Automotive Unloader for rotary compressors
US3199770A (en) * 1963-07-30 1965-08-10 Westinghouse Air Brake Co Lubricating oil pressure control apparatus for unloading compressors

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1948907A (en) * 1931-04-18 1934-02-27 Egli Eugen Compressor
US2787411A (en) * 1952-04-28 1957-04-02 Joy Mfg Co Compressor unloading mechanism
US2739758A (en) * 1955-03-23 1956-03-27 Jaeger Machine Co Rotary compressor
US2977039A (en) * 1958-07-10 1961-03-28 Joy Mfg Co Control circuit
US2997227A (en) * 1958-12-17 1961-08-22 Bendix Westinghouse Automotive Unloader for rotary compressors
US3199770A (en) * 1963-07-30 1965-08-10 Westinghouse Air Brake Co Lubricating oil pressure control apparatus for unloading compressors

Cited By (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3506376A (en) * 1966-11-10 1970-04-14 Peugeot Method and apparatus for regulating a compressed gas producer
US3582233A (en) * 1969-04-24 1971-06-01 Worthington Corp Rotary compressor control system
DE2446378A1 (de) * 1973-11-26 1975-05-28 Hokuetsu Kogyo Co Oelgekuehlter umlaufverdichter
US3936249A (en) * 1973-11-26 1976-02-03 Hokuetsu Kogyo Co., Ltd. Rotary compressor of oil cooling type with appropriate oil discharge circuit
US4035114A (en) * 1974-09-02 1977-07-12 Hokuetsu Kogyo Co., Ltd. Method for reducing power consumption in a liquid-cooled rotary compressor by treating the liquid
US3961862A (en) * 1975-04-24 1976-06-08 Gardner-Denver Company Compressor control system
US4052135A (en) * 1976-05-11 1977-10-04 Gardner-Denver Company Control system for helical screw compressor
US4173440A (en) * 1977-06-17 1979-11-06 Compagnie Industrielle Des Telecommunications Cit-Alcatel Method and device for lubricating compressors
US4326839A (en) * 1979-12-06 1982-04-27 Tecumseh Products Company Cylinder unloading mechanism for refrigeration compressor
EP0184329A1 (en) * 1984-11-19 1986-06-11 The Hydrovane Compressor Company Limited Positive displacement air compressors
US5171130A (en) * 1990-08-31 1992-12-15 Kabushiki Kaisha Kobe Seiko Sho Oil-cooled compressor and method of operating same
US5388967A (en) * 1993-03-10 1995-02-14 Sullair Corporation Compressor start control and air inlet valve therefor
US5456582A (en) * 1993-12-23 1995-10-10 Sullair Corporation Compressor inlet valve with improved response time
US5667367A (en) * 1994-04-08 1997-09-16 Kabushiki Kaisha Kobe Seiko Sho Air compressor
US6227828B1 (en) 1996-06-07 2001-05-08 Matsushita Electric Industrial Co., Ltd. Gear pump for use in an electrically-operated sealed compressor
US6116877A (en) * 1996-06-07 2000-09-12 Matsushita Electric Industrial Co., Ltd. Gear pump for use in an electrically-operated sealed compressor
US6039551A (en) * 1996-06-07 2000-03-21 Matsushita Electric Industrial Co., Ltd. Gear pump for use in an electrically-operated sealed compressor
CN1085790C (zh) * 1996-06-07 2002-05-29 松下电器产业株式会社 电动式密封压缩机中使用的齿轮泵
US6283716B1 (en) 1997-10-28 2001-09-04 Coltec Industries Inc. Multistage blowdown valve for a compressor system
US6371731B2 (en) 1997-10-28 2002-04-16 Coltec Industries Inc Multistage blowdown valve for a compressor system
US6478546B2 (en) 1997-10-28 2002-11-12 Coltec Industries Inc. Multistage blowdown valve for a compressor system
US6474953B2 (en) * 2000-02-22 2002-11-05 Atlas Copco Airpower, Naamloze Vennootschap Compressor control system and method for controlling the same
US7553142B2 (en) * 2004-02-25 2009-06-30 Carrier Corporation Lubrication system for compressor
US20050186095A1 (en) * 2004-02-25 2005-08-25 Zinsmeyer Thomas M. Lubrication system for compressor
EP3014153A1 (de) * 2013-06-28 2016-05-04 GEA AWP GmbH Rückschlagventil-filter-baugruppe
US20160290521A1 (en) * 2013-06-28 2016-10-06 GEA AWP GmbH Non-return valve/filter unit
CN105201789A (zh) * 2015-11-03 2015-12-30 干平 一种气动阀及变内压比调节装置
CN105201789B (zh) * 2015-11-03 2017-05-03 干平 一种变内压比调节装置
US11204029B2 (en) * 2018-11-14 2021-12-21 Quincy Compressor Llc Loadless start valve for a compressor
CN110793161A (zh) * 2019-11-01 2020-02-14 青岛海信日立空调***有限公司 一种风冷模块机组
CN110793161B (zh) * 2019-11-01 2021-06-08 青岛海信日立空调***有限公司 一种风冷模块机组
CN113562469A (zh) * 2021-07-15 2021-10-29 合肥科狮机械科技有限公司 一种自控节能型气力输送站
CN113562469B (zh) * 2021-07-15 2024-05-10 合肥科狮机械科技有限公司 一种自控节能型气力输送站

Also Published As

Publication number Publication date
SE316261B (ko) 1969-10-20
BE659409A (ko) 1965-05-28
GB1087751A (en) 1967-10-18
DE1503540A1 (de) 1970-07-02
FR1429488A (fr) 1966-02-25

Similar Documents

Publication Publication Date Title
US3260444A (en) Compressor control system
US3961862A (en) Compressor control system
US2492075A (en) Vacuum pump
RU1771514C (ru) Первичный двухступенчатый роторный насос
US3788776A (en) Compressor unloading control
US3848422A (en) Refrigeration plants
JPS5930919B2 (ja) 液冷式回転圧縮機の液量及び気体容量調整装置
KR20040110098A (ko) 복수의 압축기
JPS62502836A (ja) 冷凍設備および回転式容積型機械
US4035114A (en) Method for reducing power consumption in a liquid-cooled rotary compressor by treating the liquid
US1818767A (en) Rotary blower and pump
US3451614A (en) Capacity control means for rotary compressors
US7165949B2 (en) Cavitation noise reduction system for a rotary screw vacuum pump
JPH02275089A (ja) スクリュ式真空ポンプ
US3438570A (en) Two stage vacuum pump
US4123203A (en) Multistage helical screw compressor with liquid injection
JP2002310079A (ja) 水潤滑式スクリュー圧縮機
KR100186875B1 (ko) 회전베인형 유체압기기
US3250459A (en) Gear-rotor motor-compressor
WO2022088813A1 (zh) 压缩机、双压缩机串联热泵机组及其控制方法
CN112594153B (zh) 一种节能气体无油压缩机及其多级压缩结构
US3131855A (en) Art of conserving lubricant in gas compressors
JPH08543Y2 (ja) 油冷式スクリュ圧縮機
US2509377A (en) Compressor
JPH0953583A (ja) 油冷式スクリュ二段圧縮機