US20070065302A1 - System and method for operating a compressor - Google Patents

System and method for operating a compressor Download PDF

Info

Publication number
US20070065302A1
US20070065302A1 US11/230,204 US23020405A US2007065302A1 US 20070065302 A1 US20070065302 A1 US 20070065302A1 US 23020405 A US23020405 A US 23020405A US 2007065302 A1 US2007065302 A1 US 2007065302A1
Authority
US
United States
Prior art keywords
compressor
inlet
valve
fluid
inlet 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.)
Abandoned
Application number
US11/230,204
Other languages
English (en)
Inventor
Michael Schmitz
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.)
General Electric Co
Original Assignee
General Electric Co
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 General Electric Co filed Critical General Electric Co
Priority to US11/230,204 priority Critical patent/US20070065302A1/en
Assigned to GENERAL ELECTRIC COMPANY reassignment GENERAL ELECTRIC COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SCHMITZ, MICHAEL BERNHARD
Priority to JP2008532259A priority patent/JP2009509098A/ja
Priority to PCT/US2006/034849 priority patent/WO2007035268A1/en
Priority to EP06803112A priority patent/EP1934506A1/en
Priority to CA002623174A priority patent/CA2623174A1/en
Priority to CNA2006800422810A priority patent/CN101305229A/zh
Publication of US20070065302A1 publication Critical patent/US20070065302A1/en
Abandoned 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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/08—Actuation of distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing

Definitions

  • the invention relates generally to a reciprocating compressor and, more specifically, to a system and method for controlling a valve closing time of a compressor inlet valve.
  • a compressor is typically used to boost pressure of a working fluid by receiving power from an electric machine or a turbine, and applying a compressive force to the working fluid.
  • the working fluid may be air, refrigerant, or the like.
  • Compressors are typically classified as positive displacement compressors, dynamic compressors or turbo compressors, depending on the method they employ for compression.
  • Positive displacement compressors are typically used to boost pressure of the working fluid by reduction in volume, and may be further classified into categories of reciprocating compressors and rotary compressors.
  • Reciprocating compressors typically compress the working fluid via a piston reciprocating inside a cylinder.
  • Rotary compressors typically compress the working fluid via a roller revolving inside a cylinder having an eccentricity.
  • the compressors use a hydraulic actuation mechanism to control the opening and closing of the inlet valve during partial load conditions.
  • the pressure control of the hydraulic actuation mechanism is controlled via electromagnetic valves. Thereby, mass flow of fluid through the compressor is reduced and the performance of the compressor is enhanced.
  • Such hydraulic actuation mechanisms may employ high pressure pipes and in addition electrical connections to each inlet valve. Moreover, such hydraulic systems do not facilitate flexibility in the controlled opening and closing of inlet valve during partial load conditions.
  • An improved system and method for controlling valve timing of compressor inlet valves to achieve flexibility in partial load operation of the compressor is desirable.
  • a compressor in accordance with one aspect of the present embodiment, includes an inlet adapted to intake a fluid at an inlet pressure and an inlet valve coupled to the inlet.
  • the inlet valve is adapted to control intake of the fluid at the inlet pressure through the inlet.
  • the compressor further includes a cam adapted to control a valve closing time of the inlet valve during a compression stroke of the compressor to pressurize the fluid.
  • an outlet adapted to discharge pressurized fluid subsequent to the compression stroke.
  • a compressor in accordance with another aspect of the present embodiment, includes an inlet adapted to intake a fluid at an inlet pressure and an inlet valve coupled to the inlet.
  • the inlet valve is adapted to control intake of the fluid at the inlet pressure through the inlet.
  • the compressor further includes at least one blocking solenoid adapted to control a valve closing time of the inlet valve during a compression stroke of the compressor, the at least one blocking solenoid being further adapted to maintain the inlet valve at least one stop point during the compression stroke of the compressor.
  • a method of operating a compressor includes supplying a fluid at the inlet pressure via an inlet. The method further includes actuating a cam to control a valve closing time of an inlet valve coupled to the inlet during the compression stroke of the compressor.
  • a method of operating a compressor includes supplying a fluid at an inlet pressure via an inlet; and actuating at least one blocking solenoid to control valve closing time of an inlet valve coupled to the inlet during a compression stroke of the compressor.
  • FIG. 1 is a diagrammatical representation of a reciprocating compressor having valve closing control features in accordance with an exemplary aspect of the present embodiment
  • FIG. 2 is a detailed diagrammatical representation of a reciprocating compressor having valve closing control features in accordance with an exemplary aspect of the present embodiment
  • FIG. 3 is a diagrammatical representation of a reciprocating compressor having a cam adapted to control valve closing time of an inlet valve in accordance with an exemplary aspect of the present embodiment
  • FIG. 4 is a graph representing variation of pressure versus volume during a full load cycle operation of a reciprocating compressor in accordance with an exemplary aspect of the present embodiment
  • FIG. 5 is a graph representing variation of pressure versus volume during a partial load cycle operation of a reciprocating compressor in accordance with an exemplary aspect of the present embodiment
  • FIG. 6 is a diagrammatical representation of a reciprocating compressor having a plurality of blocking solenoids adapted to control valve closing time of an inlet valve in accordance with an exemplary aspect of the present embodiment
  • FIGS. 7 and 8 are flow charts illustrating exemplary processes of operating a compressor in accordance with certain exemplary aspects of the present embodiment.
  • a compressor 10 includes a piston 38 slidably inserted inside a cylinder 42 .
  • a suction valve assembly 46 is provided for opening and closing a suction hole 11 mounted at a front side of the piston 38 .
  • the suction valve assembly is adapted to control intake of fluid through the suction hole 11 .
  • the compressor 10 further includes an electromechanical valve mechanism 52 adapted to control a valve closing time of an inlet valve (not shown) during a compression stroke of the compressor 10 to pressurize the fluid.
  • a control unit 54 may be coupled to the electro-mechanical valve actuation mechanism 52 and configured to control the operation of the valve actuation mechanism 52 .
  • the reciprocating compressor 10 may be used for domestic and industrial purposes.
  • the compressor 10 is typically driven by an electric motor, steam or gas turbine, combustion engine, or the like.
  • the compressor 10 may be used to compress air, hydrogen, methane, butane, or other liquids or gases.
  • the reciprocating compressor 10 includes a suction pipe or inlet 12 and a discharge pipe or outlet 14 coupled to a casing 16 .
  • the suction pipe 12 is configured to receive a fluid at an inlet pressure and the discharge pipe 14 is configured to discharge a compressed fluid.
  • the inlet pressure of the fluid may be ambient pressure or any other appropriate pressure as known to those skilled in the art.
  • a reciprocating motor 18 is disposed inside the casing 16 for generating a reciprocation force.
  • a compressing unit 20 is also located inside the casing 16 and configured to compress the fluid by receiving the reciprocation force generated from the reciprocating motor 18 .
  • a plurality of frames 22 , 24 , and 26 are provided for supporting the reciprocating motor 18 and the compressing unit 20 .
  • the reciprocating motor 18 includes an outer stator 28 having a cylindrical shape and an inner stator 30 disposed along an inner circumferential surface of the outer stator 28 .
  • a coil 32 is wound within the outer stator 28 .
  • a magnet 34 is reciprocatably disposed in the air gap between the outer stator 28 and the inner stator 30 .
  • the magnet 34 is fixed to an outer circumferential surface of a magnet holder 36 .
  • the magnet holder 36 is coupled to the piston 38 of the reciprocating compressor 10 .
  • a first resonant spring 39 is disposed between one side surface of the magnet holder 36 and the frame 22 and a second resonant spring 40 is disposed between another side surface of the magnet holder 36 and the frame 24 , to induce a resonant movement of the piston 38 .
  • the piston 38 is slidably inserted inside the cylinder 42 forming a compression chamber 44 .
  • the suction valve assembly 46 is provided for opening and closing a suction hole mounted at a front side of the piston 38 .
  • a discharge valve assembly 48 is mounted at a front side of the cylinder 42 for discharging the compressed fluid when a pressure inside the compression chamber 44 is greater than a preset pressure.
  • a fluid suction passage 50 is formed along a longitudinal direction in the piston 38 .
  • the magnet 34 When the reciprocating motor 18 is operated, the magnet 34 is linearly reciprocated and thereby the piston 38 coupled to the magnet is linearly reciprocated to compress the fluid.
  • the inlet valve of the suction valve assembly 46 When the piston 38 is retreated, the inlet valve of the suction valve assembly 46 is opened by a differential pressure between the fluid introduced into the suction passage 50 of the piston 38 and the compression chamber 44 of the cylinder 42 .
  • the piston 38 When the piston 38 is advanced, the inlet valve is closed and thereby fluid inside the compression chamber 44 is compressed.
  • a discharge valve (not shown) of the discharge valve assembly 48 is opened and thereby the compressed fluid is discharged through the discharge pipe 14 .
  • the inlet valve is closed due to differential pressure between the fluid introduced into the suction passage 50 of the piston 38 and the compression chamber 44 of the cylinder 42 .
  • the electro-mechanical valve actuation mechanism 52 is employed to control the closing of the inlet valve during the compression stroke of the compressor 10 at no-load or partial load operating conditions.
  • the electro-mechanical valve actuation mechanism 52 enables to control the closing time of the inlet valve during the compression stroke independent of crank motion of the compressor 10 .
  • Various exemplary embodiments of the electro-mechanical valve actuation mechanism 52 are explained in greater detail with respect to subsequent figures.
  • the control unit 54 may be coupled to the electro-mechanical valve actuation mechanism 52 and configured to control the operation of the valve actuation mechanism 52 .
  • the control unit 54 includes an electronic logic controller that is programmable by a user.
  • the control unit 54 may control the valve actuation mechanism 52 based on the load condition of the compressor.
  • the electromechanical valve actuation mechanism 52 includes a cam 68 adapted to be electrically driven by a rotary drive unit 70 such as an electrical motor or a rotational solenoid.
  • the cam 68 may be stopped and held in any arbitrary position within the predetermined limits to control the closing of the inlet valve 55 during the compression stroke.
  • FIG. 3 additionally shows further optional exemplary aspects for electromechanical valve actuation mechanism 52 which are described in more detail below.
  • the inlet valve 55 of the suction valve assembly 46 is provided for opening and closing the suction hole mounted at the front side of the piston.
  • the inlet valve 55 includes a valve plate 56 , two plates ( 58 , 60 ) mutually coupled via a plurality of springs 62 .
  • the plurality of springs 62 is provided to bias the plate 58 against the valve plate 56 .
  • the valve plate 56 includes a plurality of holes 64 and inlet openings 66 .
  • the electromechanical valve actuation mechanism 52 includes the cam 68 adapted to be electrically driven by the rotary drive unit 70 such as an electrical motor or a rotational solenoid.
  • the drive unit 70 is operable at constant speed or variable speed.
  • the rotary drive unit 70 may be rotated 90 degrees in an anticlockwise direction to close the inlet valve 55 . In certain other embodiments, the rotary drive unit 70 may be rotated 90 degrees in a clockwise direction to close the inlet valve 55 .
  • the cam 68 drives a pushing rod (unloader) 72 adapted to follow the motion of the inlet valve 55 and hold the inlet valve 55 at an open position.
  • the pushing rod 72 includes two plate portions ( 76 , 79 ), a rod portion 74 extending between the plate portions ( 76 , 79 ), and a plurality of projections 78 extending from the plate portion 76 .
  • the projections 78 penetrate through the holes 64 formed in the valve plate 56 to disengage the plate 58 from the valve plate 56 . Fluid is then sucked through the inlet openings of the valve plate 56 .
  • the compressor may include a plurality of inlet valves 55 adapted to control the intake of fluid into the compressor 10 .
  • the electro-mechanical valve actuation mechanism 52 may include one cam and one drive unit per valve, in order to operate each valve separately and ensure flexibility. For example, depending on the load condition of the compressor, it may be required to vary the closing time of one set of valves from the closing time of the other set valves during compression stroke of the compressor.
  • the cam 68 is adapted to hold the valve 55 in the open position without the requirement of any external force or energy. The cam 68 may be stopped and held in any arbitrary position within the predetermined limits to control the closing of the inlet valve 55 during the compression stroke.
  • the inlet valve 55 is operable in two modes. During no-load condition or partial load condition, a peak portion 80 of the cam 68 contacts the pushing rod 72 and the inlet valve 55 is fully opened. During full load condition, the cam 68 is disengaged from the pushing rod 72 and the inlet valve 55 is in free floating condition, enabling the inlet valve 55 to be opened and closed due to differential pressure.
  • the control unit 54 may further include a database 82 , an algorithm 84 , and a data analysis block 86 .
  • the database 82 may be configured to store predefined information about the compressor 10 .
  • the database 82 may store information relating to crank angle, compressor speed, compressor load, intake fluid pressure, compressed fluid pressure, type of fluid, or the like.
  • the database 82 may also include instruction sets, maps, lookup tables, variables, or the like. Such maps, lookup tables, instruction sets, are operative to correlate characteristics of the valve closing time to specified compressor operation parameters such as compressor speed, crank angle, compressor pressure, compressor load, type of fluid, or the like.
  • the database 82 may be configured to store actual sensed/detected information pertaining to the compressor 10 .
  • the algorithm 84 may facilitate the processing of sensed information pertaining to the compressor 10 .
  • the data analysis block 86 may include a variety of circuitry types, such as a microprocessor, a programmable logic controller, a logic module or the like.
  • the data analysis block 86 in combination with the algorithm 84 may be used to perform the various computational operations relating to determination of closing time of the inlet valves 55 , predetermined time period for controlling closing time of the inlet valves 55 , degree of rotation of the rotary drive unit 70 , power required to drive the valve actuation mechanism 52 , or a combination thereof. Any of the above mentioned parameters may be selectively and/or dynamically adapted or altered relative to time.
  • FIG. 4 a graph representing variation of cylinder pressure versus cylinder volume during a full load cycle operation of the reciprocating compressor is illustrated.
  • Dashed lines 61 , 63 represents top dead center position and bottom dead center position respectively of the piston.
  • Operating point 65 represents piston positioned at the top dead center and the discharge valve held in closed position.
  • the piston is moved to the bottom dead center and is represented by the curve 67 .
  • Pressure is reduced and the volume is increased in the cylinder during intake stroke.
  • Operating point 69 represents opening of the inlet valve during intake stroke of the piston and supply of fluid into the cylinder.
  • the inlet valve is opened by a differential pressure between the fluid introduced into the suction passage of the piston and the compression chamber of the cylinder.
  • the inlet valve is closed as represented by the operating point 71 .
  • FIG. 5 a graph representing variation of cylinder pressure versus cylinder volume during a partial load cycle operation of the reciprocating compressor is illustrated.
  • dashed lines 61 , 63 represent top dead center position and bottom dead center position respectively of the piston.
  • Operating point 65 represents piston positioned at the top dead center and the discharge valve held in closed position.
  • the piston is moved to the bottom dead center and is represented by the curve 67 .
  • Pressure is reduced and the volume is increased in the cylinder during intake stroke.
  • Operating point 69 represents opening of the inlet valve during intake stroke of the piston and supply of fluid into the cylinder. The inlet valve is maintained in free-floating condition during intake stroke.
  • the inlet valve When the piston reaches the bottom dead center position, the inlet valve is further maintained in the open position using the electro-mechanical valve actuation mechanism as described previously.
  • the piston During compression stroke, the piston is moved from the bottom dead center to the top dead center and is represented by the curve 73 . Fluid inside the cylinder is compressed. Therefore, pressure is increased and the volume is reduced in the cylinder during compression stroke. Since the inlet valve is maintained open for a predetermined period during compression stroke, reverse fluid flow may occur through the inlet of the compressor.
  • Operating point 77 represents closing of the inlet valve during the compressor stroke of the piston.
  • the electro-mechanical valve actuation mechanism is released to close the inlet valve. In the illustrated embodiment, the closing of the inlet valve is delayed using the electro-mechanical valve actuation mechanism.
  • Operating point 75 represents opening of the discharge valve during compression stroke of the piston and discharge of compressed fluid.
  • the discharge valve is closed.
  • mass flow through the compressor is reduced during partial load condition. For example, during 50% load condition of the compressor, 50% of mass flow is delivered through the compressor.
  • the usage of electro-mechanical mechanism further facilitates to reduce power consumption for maintaining the inlet valve open during compression stroke.
  • the electromechanical valve actuation mechanism 52 includes a plurality of blocking solenoids ( 88 , 90 ) adapted to be actuated by the control unit 54 .
  • the blocking solenoid 88 maintains the inlet valve in an open position for a predetermined time period during compression stroke.
  • FIG. 6 additionally shows further optional exemplary aspects for electromechanical valve actuation mechanism 52 which are described in more detail below.
  • a drive unit 92 such as a spring or a pusher solenoid, drives the pushing rod (unloader) 72 adapted to follow the motion of the inlet valve 55 and hold the inlet valve 55 at an open position.
  • the pushing rod 72 is driven by the drive unit 92 , the projections 78 penetrate through the holes 64 formed in the valve plate 56 to disengage the plate 58 from the valve plate 56 and fluid is sucked through the inlet openings of the valve plate 56 .
  • the inlet valve is opened due to the differential pressure between the fluid introduced into the suction passage 50 of the piston 38 and the compression chamber 44 of the cylinder 42 .
  • the control unit 54 electrically actuates the blocking solenoid 88 adapted to drive a blocking rod 98 so that the blocking rod 98 engages a bore 100 formed in the pushing rod 72 .
  • the blocking solenoid 88 is configured to hold the pushing rod 72 at a first stop-point position 102 . In this manner, the blocking solenoid 88 maintains the inlet valve in an open position for a predetermined time period during compression stroke.
  • the blocking rod 98 is disengaged from the bore 100 of the pushing rod 72 by releasing the current supplied to the blocking solenoid 88 .
  • the pushing rod 72 and the pusher solenoid 92 are actuated in an opposite direction relative to the intake stroke, due to the differential pressure causing the inlet valve to close.
  • the control unit 54 electrically actuates the blocking solenoid 90 adapted to drive a blocking rod 104 so that the blocking rod 104 engages a bore 106 formed in the pushing rod 72 .
  • the blocking solenoid 90 is configured to hold the pushing rod 72 at a second stop-point position 108 . In this manner, the blocking solenoid 90 maintains the inlet valve in an open position for a predetermined time period during compression stroke.
  • the blocking rod 104 is disengaged from the bore 106 of the pushing rod 72 by releasing the current supplied to the blocking solenoid 90 .
  • the pushing rod 72 and the pusher solenoid 92 are actuated in an opposite directions relative to the intake stroke, due to the differential pressure causing the inlet valve to close.
  • valve actuation mechanism 52 may include multiple blocking solenoids configured to hold the pushing rod 72 at a plurality of stop points during the compression stroke.
  • One type of blocking solenoid may be used for variety of compressor applications.
  • FIG. 7 is a flow chart illustrating a method of operating the compressor 10 in accordance with an exemplary embodiment of the present embodiment.
  • the method includes sucking fluid via the suction pipe 12 during intake stroke as represented by step 110 .
  • the electromechanical valve actuation mechanism 52 enables to control the closing time of the inlet valve 55 during the compression stroke independent of the crank motion of the compressor 10 .
  • Operation of the rotary drive unit 70 such as the electrical motor or rotational solenoid is controlled via the control unit 54 based on the load condition of the compressor as represented by step 112 .
  • the cam 68 is driven by the rotary drive unit 70 as represented by step 114 .
  • the cam 68 drives the pushing rod 72 in such a way that the plurality of projections 78 of the pushing rod 72 penetrate through the holes 64 formed in the valve plate 56 as represented by step 116 .
  • the fluid is sucked through the inlet openings 66 formed in the valve plate 56 .
  • the inlet valve 55 is opened due to differential pressure between the fluid introduced at inlet pressure into the suction passage of the piston 38 and compression chamber 44 of the cylinder 42 .
  • the cam 68 is stopped in the predetermined position to control the closing time of the valve 55 during compression stroke of the compressor 10 as represented by step 118 .
  • the peak portion of the cam 68 is engaged with the pushing rod 72 to hold the inlet valve in the fully open position.
  • the cam 68 is further actuated by the drive unit 70 to release the cam 68 from the pushing rod 72 such that the inlet valve 55 is closed due to differential pressure acting in an opposite relative to the intake stroke.
  • fluid inside the compression chamber 44 of the cylinder 42 is compressed.
  • the compressed fluid is discharged via the discharge pipe 14 as represented by step 120 .
  • FIG. 8 this figure illustrates another embodiment of the method of operating the compressor 10 in accordance with an exemplary embodiment of the present embodiment.
  • the method includes sucking fluid via the suction pipe 12 during intake stroke as represented by step 122 .
  • the electromechanical valve actuation mechanism 52 enables to control the closing time of the inlet valve 55 during the compression stroke independent of the crank motion of the compressor.
  • the drive unit 92 such as the spring or the pusher solenoid drives the pushing rod 72 (unloader) as represented by step 124 .
  • the pushing rod 72 follows the motion of the inlet valve 55 and facilitates to hold the inlet valve 55 at an open position.
  • the projections 78 of the pushing rod 72 penetrates through the holes 64 formed in the valve plate 56 to enable suction of fluid through the inlet openings 66 formed in the valve plate 56 .
  • the control unit 54 actuates the blocking solenoid as represented by step 126 .
  • the blocking solenoid actuates the blocking rod as represented by step 128 .
  • the blocking rod engages a bore formed in the pushing rod 72 at a stop point as represented by step 130 .
  • the blocking solenoid facilitates to hold the inlet valve 55 at the open position for a predetermined time period during the compression stroke, thereby enabling to control the valve closing time of the inlet valve 55 during the compression stroke as represented by step 132 .
  • the blocking solenoid is further actuated by the drive unit 92 to release the blocking rod from the pushing rod 72 such that the inlet valve 55 is closed due to differential pressure acting in an opposite relative to the intake stroke.
  • fluid inside the compression chamber 44 of the cylinder 42 is compressed.
  • the compressed fluid is discharged via the discharge pipe 14 as represented by step 134 .
US11/230,204 2005-09-19 2005-09-19 System and method for operating a compressor Abandoned US20070065302A1 (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US11/230,204 US20070065302A1 (en) 2005-09-19 2005-09-19 System and method for operating a compressor
JP2008532259A JP2009509098A (ja) 2005-09-19 2006-09-11 圧縮機を作動させるためのシステム及び方法
PCT/US2006/034849 WO2007035268A1 (en) 2005-09-19 2006-09-11 System and method for operating a compressor
EP06803112A EP1934506A1 (en) 2005-09-19 2006-09-11 System and method for operating a compressor
CA002623174A CA2623174A1 (en) 2005-09-19 2006-09-11 System and method for operating a compressor
CNA2006800422810A CN101305229A (zh) 2005-09-19 2006-09-11 运行压缩机的系统和方法

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US11/230,204 US20070065302A1 (en) 2005-09-19 2005-09-19 System and method for operating a compressor

Publications (1)

Publication Number Publication Date
US20070065302A1 true US20070065302A1 (en) 2007-03-22

Family

ID=37507604

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/230,204 Abandoned US20070065302A1 (en) 2005-09-19 2005-09-19 System and method for operating a compressor

Country Status (6)

Country Link
US (1) US20070065302A1 (ja)
EP (1) EP1934506A1 (ja)
JP (1) JP2009509098A (ja)
CN (1) CN101305229A (ja)
CA (1) CA2623174A1 (ja)
WO (1) WO2007035268A1 (ja)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080279705A1 (en) * 2007-05-11 2008-11-13 Toshimichi Wago Externally Assisted Valve for a Positive Displacement Pump
US20100140519A1 (en) * 2008-12-04 2010-06-10 General Electric Company Electromagnetic actuators
US20100166571A1 (en) * 2006-06-09 2010-07-01 Peter Van Den Wyngaert Device for regulating the operating pressure of an oil-injected compressor installation
US20100183448A1 (en) * 2007-05-11 2010-07-22 Edward Leugemors Methods of use for a positive displacement pump having an externally assisted valve
KR20150029625A (ko) * 2012-05-02 2015-03-18 누보 피그노네 에스알엘 캠 작동식 밸브, 왕복동 압축기의 개방 시간 조정 및 방법
WO2018075034A1 (en) * 2016-10-19 2018-04-26 Halliburton Energy Services, Inc. Controlled stop for a pump
EP2511526B1 (de) * 2011-04-14 2019-08-21 Hoerbiger Wien GmbH Hubkolbenverdichter mit Fördermengenregelung
US10514029B2 (en) 2015-02-16 2019-12-24 Tti (Macao Commercial Offshore) Limited Air inlet control for air compressor
US10947967B1 (en) * 2020-03-11 2021-03-16 Halliburton Energy Services, Inc. Discharge valve disabler and pressure pulse generator therefrom
US11204022B2 (en) 2018-08-14 2021-12-21 Milwaukee Electric Tool Corporation Air compressor
US20220090594A1 (en) * 2020-09-18 2022-03-24 Caterpillar Inc. Hydraulic fracturing pump control system

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BR102014007259A2 (pt) * 2014-03-26 2015-12-08 Whirlpool Sa compressor alternativo provido de arranjo de válvulas de sucção

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2160860A (en) * 1936-02-20 1939-06-06 Schramm Inc Compressor
US2595369A (en) * 1947-07-15 1952-05-06 Schramm Inc Governing mechanism for enginedriven compressors
US2667299A (en) * 1950-04-14 1954-01-26 Schramm Inc Compressor inlet valve actuating mechanism
US3738116A (en) * 1971-10-01 1973-06-12 Dunham Bush Inc Compressor unloader indicator and refrigeration system controlled thereby
US4353682A (en) * 1980-09-22 1982-10-12 The Trane Company Reciprocating gas compressor having suction shut-off unloading means
US5718569A (en) * 1996-01-11 1998-02-17 Abbott Laboratories Dual plunger cassette pump
US5842354A (en) * 1996-04-03 1998-12-01 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Climate controller for automobiles
US6053472A (en) * 1998-10-16 2000-04-25 Eaton Corporation Rotary solenoid operated proportional flow control valve
US20050028797A1 (en) * 2003-08-08 2005-02-10 Janssen John M. Dual mode EGR valve
US20050175482A1 (en) * 2004-01-06 2005-08-11 Lg Electronics Inc. Linear compressor with external vibration-absorbing structure
US7331767B2 (en) * 2002-09-19 2008-02-19 Hoerbiger Kompressortechnik Services Gmbh Method of stepless capacity control of a reciprocating piston compressor and piston compressor with such control

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB190929016A (en) * 1908-12-11 1910-07-21 David Erastus Haire Improvements in Fluid Compressors.
JP3944413B2 (ja) * 2002-05-24 2007-07-11 株式会社日立製作所 高圧燃料供給ポンプ
US7153106B2 (en) * 2003-01-16 2006-12-26 R. Conrader Company Air compressor unit inlet control

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2160860A (en) * 1936-02-20 1939-06-06 Schramm Inc Compressor
US2595369A (en) * 1947-07-15 1952-05-06 Schramm Inc Governing mechanism for enginedriven compressors
US2667299A (en) * 1950-04-14 1954-01-26 Schramm Inc Compressor inlet valve actuating mechanism
US3738116A (en) * 1971-10-01 1973-06-12 Dunham Bush Inc Compressor unloader indicator and refrigeration system controlled thereby
US4353682A (en) * 1980-09-22 1982-10-12 The Trane Company Reciprocating gas compressor having suction shut-off unloading means
US5718569A (en) * 1996-01-11 1998-02-17 Abbott Laboratories Dual plunger cassette pump
US5842354A (en) * 1996-04-03 1998-12-01 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Climate controller for automobiles
US6053472A (en) * 1998-10-16 2000-04-25 Eaton Corporation Rotary solenoid operated proportional flow control valve
US7331767B2 (en) * 2002-09-19 2008-02-19 Hoerbiger Kompressortechnik Services Gmbh Method of stepless capacity control of a reciprocating piston compressor and piston compressor with such control
US20050028797A1 (en) * 2003-08-08 2005-02-10 Janssen John M. Dual mode EGR valve
US20050175482A1 (en) * 2004-01-06 2005-08-11 Lg Electronics Inc. Linear compressor with external vibration-absorbing structure

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100166571A1 (en) * 2006-06-09 2010-07-01 Peter Van Den Wyngaert Device for regulating the operating pressure of an oil-injected compressor installation
US8360738B2 (en) * 2006-06-09 2013-01-29 Atlas Copco Airpower, Naamloze Vennootschap Device for regulating the operating pressure of an oil-injected compressor installation
US20080279705A1 (en) * 2007-05-11 2008-11-13 Toshimichi Wago Externally Assisted Valve for a Positive Displacement Pump
US20100183448A1 (en) * 2007-05-11 2010-07-22 Edward Leugemors Methods of use for a positive displacement pump having an externally assisted valve
US8366408B2 (en) * 2007-05-11 2013-02-05 Schlumberger Technology Corporation Externally assisted valve for a positive displacement pump
US8506262B2 (en) 2007-05-11 2013-08-13 Schlumberger Technology Corporation Methods of use for a positive displacement pump having an externally assisted valve
US20100140519A1 (en) * 2008-12-04 2010-06-10 General Electric Company Electromagnetic actuators
EP2511526B1 (de) * 2011-04-14 2019-08-21 Hoerbiger Wien GmbH Hubkolbenverdichter mit Fördermengenregelung
US20150139826A1 (en) * 2012-05-02 2015-05-21 Nuovo Pignone Srl Adjusting Opening Times of a Cam Actuated Valve, Reciprocating Compressor and Method
JP2015516041A (ja) * 2012-05-02 2015-06-04 ヌオーヴォ ピニォーネ ソチエタ レスポンサビリタ リミタータＮｕｏｖｏ Ｐｉｇｎｏｎｅ Ｓ．Ｒ．Ｌ． 往復動圧縮機およびカム機構
US10253760B2 (en) * 2012-05-02 2019-04-09 Nuovo Pignone Srl Adjusting opening times of a cam actuated valve, reciprocating compressor and method
KR20150029625A (ko) * 2012-05-02 2015-03-18 누보 피그노네 에스알엘 캠 작동식 밸브, 왕복동 압축기의 개방 시간 조정 및 방법
KR102085322B1 (ko) * 2012-05-02 2020-03-05 누보 피그노네 에스알엘 캠 작동식 밸브, 왕복동 압축기의 개방 시간 조정 및 방법
US10514029B2 (en) 2015-02-16 2019-12-24 Tti (Macao Commercial Offshore) Limited Air inlet control for air compressor
WO2018075034A1 (en) * 2016-10-19 2018-04-26 Halliburton Energy Services, Inc. Controlled stop for a pump
US11415123B2 (en) 2016-10-19 2022-08-16 Halliburton Energy Services. Inc. Controlled stop for a pump
US11204022B2 (en) 2018-08-14 2021-12-21 Milwaukee Electric Tool Corporation Air compressor
US10947967B1 (en) * 2020-03-11 2021-03-16 Halliburton Energy Services, Inc. Discharge valve disabler and pressure pulse generator therefrom
US20220090594A1 (en) * 2020-09-18 2022-03-24 Caterpillar Inc. Hydraulic fracturing pump control system

Also Published As

Publication number Publication date
CN101305229A (zh) 2008-11-12
CA2623174A1 (en) 2007-03-29
WO2007035268A1 (en) 2007-03-29
EP1934506A1 (en) 2008-06-25
JP2009509098A (ja) 2009-03-05

Similar Documents

Publication Publication Date Title
US20070065302A1 (en) System and method for operating a compressor
CA2686373C (en) Electromagnetic actuators
KR20070075908A (ko) 리니어 압축기의 오일 공급 장치
WO2017096999A1 (zh) 压缩机及减小压缩机泄漏和磨损的控制方法
JP6109301B2 (ja) 多気筒回転圧縮機及びこの多気筒回転圧縮機を備えた蒸気圧縮式冷凍サイクル装置
KR20040022320A (ko) 왕복동식 압축기의 가스 압축장치
JP3490557B2 (ja) 容量可変圧縮機の容量制御装置
KR0122396Y1 (ko) 왕복동식 압축기
WO2006025620A1 (en) Linear compressor
EP2010786B1 (en) Hermetic compressor
JP2013057284A (ja) 密閉型圧縮機
KR102547594B1 (ko) 가변 용량 사판식 압축기
KR100660689B1 (ko) 리니어 압축기
US20080213108A1 (en) Linear Compressor
JP2010090705A (ja) 冷媒圧縮機
KR101753406B1 (ko) 용량 가변형 압축기
KR20060074966A (ko) 리니어 압축기의 제어방법
WO2002025110A1 (en) Valve assembly in hermetic compressor
KR20040097740A (ko) 로터리 압축기
JP2002031058A (ja) 往復式冷媒圧縮機
KR100464078B1 (ko) 토출 밸브
JP2006022719A (ja) オイルレスリニア圧縮機
JP2007132262A (ja) 圧縮機
KR20060025110A (ko) 리니어 압축기
JP2012197768A (ja) 密閉型圧縮機

Legal Events

Date Code Title Description
AS Assignment

Owner name: GENERAL ELECTRIC COMPANY, NEW YORK

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:SCHMITZ, MICHAEL BERNHARD;REEL/FRAME:017016/0277

Effective date: 20050916

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION