US3859814A - Variable capacity rotary screw compressor - Google Patents

Variable capacity rotary screw compressor Download PDF

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Publication number
US3859814A
US3859814A US403195A US40319573A US3859814A US 3859814 A US3859814 A US 3859814A US 403195 A US403195 A US 403195A US 40319573 A US40319573 A US 40319573A US 3859814 A US3859814 A US 3859814A
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United States
Prior art keywords
rotors
pressure vapor
vapor
high pressure
low pressure
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
US403195A
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English (en)
Inventor
Whitney I Grant
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.)
Copeland Industrial LP
Original Assignee
Vilter Manufacturing LLC
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 Vilter Manufacturing LLC filed Critical Vilter Manufacturing LLC
Priority to US403195A priority Critical patent/US3859814A/en
Priority to SE7411972A priority patent/SE7411972L/xx
Priority to CA210,022A priority patent/CA988730A/en
Priority to FR7433031A priority patent/FR2246754B1/fr
Priority to GB4380174A priority patent/GB1444308A/en
Priority to DE19742447116 priority patent/DE2447116A1/de
Priority to JP11428474A priority patent/JPS554239B2/ja
Application granted granted Critical
Publication of US3859814A publication Critical patent/US3859814A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of screw type

Definitions

  • ABSTRACT A variable capacity rotary screw compressor for a refrigeration system which includes a high pressure condenser, a subcooler, a main evaporator and an intermediate evaporator, the compressor including a primary inlet connected to receive low pressure vapor from the main evaporator, a secondary or intermediate inlet connected to receive high pressure vapor from the subcooler and/r intermediate evaporator, and a high pressure discharge port connected to the condenser, the compressor including a pair of oppositely rotating constant mesh helical lobe rotors and a slide valve to vary the capacity of the compressor by changing the points of admission of the low pressure vapor and the high pressure vapor to the rotors of the compressor, the points of admission of low pressure vapor and high pressure vapor being maintained in
  • the slide valve for the primary suction inlet is moved to change the capacity of the compressor from a maximum to a minimum producing a continuing change in the pressure of the intermediate vapor.
  • the intermediate vapor pressure will be virtually at the same pressure level as the primary vapor pressure from the main evaporator. This continually changing intermediate vapor pressure level reduces the effect of the multiple suction arrangement such that maximum efficiency occurs only at maximum load conditions. There is virtually no in-' crease in efficiency at minimum capacity because the pressures at the primary and secondary inlets are the same. Since the intermediate vapor pressure is continually varying in this type of a compressor, it is not suitable for use with intermediate evaporators.
  • variable capacity screw compressor of the present invention provides for the admission of secondary vapor at high pressure throughout the full stroke of the slide valve.
  • the point of injection of the secondary high pressure vapor is maintained constant with respect to the point where the vapor begins to compress in the rotors.
  • the secondary high pressure vapor is always introduced into the rotors at a fixed distance from the start of compression in the rotors.
  • a relatively constant or fixed pressure relationship is maintained between the main evaporator suction inlet and the intermediate evaporator pressure level. Since the pressure relation between the primary and secondary gas is maintained constant, the compressor can be used with an intermediate evaporator and still obtain the advantages of desuperheating and subcooling.
  • FIG. 1 is a schematic view of a refrigeration system of the two suction pressure level type connected to a multiple suction screw compressor which has been partly broken away to show the slide valve of the present invention
  • FIG. 2 is an elevation view of the multiple suction screw compressor partly broken away to show the slide valve in the minimum capacity position
  • FIG. 3 is a section view taken on line 3-3 of FIG. 2 showing the slide valve.
  • the multiple suction screw compressor of the present invention as shown in FIG. 1 is connected to a refrigeration system 11 which generally includes a condenser 12, a subcooler 14, a main evaporator 16 and an intermediate evaporator 18.
  • the condenser 12 is connected to the discharge outlet 20 of the compressor 10 by a high pressure discharge conduit 22.
  • High pressureliquid from the condenser 12 is conducted to the subcooler 14 through a high pressure liquid conduit 24.
  • the cooled liquid from the subcooler 14 is conducted to the main evaporator l6-through a conduit 26.
  • the main evaporator 16 is connected to the low pressure vapor inlet port 28 in the compressor 10 through a conduit 30.
  • the level of liquid refrigerant in the subcooler I4 is maintained at a predetermined level by a liquid level control 38 connected to the high pressure liquid conduit 24 through conduits and 36.
  • High pressure gas or vapor from the subcooler I4 is conducted to a fixed secondary or intermediate high pressure vapor inlet port 32 in the compressor 10 through a conduit 40.
  • Additional high pressure gas or vapor is provided by means of the intermediate evaporator 18.
  • the evaporator 18 is connected across the subcooler 14 by conduits 36 and 42.
  • The-high pressure vapor from the subcooler 14 and intermediate evaporator 18 is drawn into the compressor through conduit 40.
  • the evaporators 16 and 18 are conventional and can be of the shell and tube brine cooler type in which brine is introduced into and taken out of the evaporators through conduits 15, 17 and 19, 21, respectively.
  • the intermediate evaporator 18 provides vapor at a higher pressure than the main evaporator 16. This difference in pressure should normally be at least 15 psi,
  • Control valves 41 can be provided in each of the evaporators 16 and 18 to control the flow of refrigerant to these evaporators. The control valves function to reduce the pressure of the liquid to the required evaporator pressure as is generally understood.
  • variable capacity compressor 10 of the invention generally includes a housing 45 having a pair of oppositely rotating constant mesh helcial lobe rotors 44 and 46 positioned within bores 43 and 47 within the housing 45.
  • the rotors 44 and 46 cooperate to provide a pumping and compressing action in a known manner.
  • the rotors define lobe chambers which close off low pressure vapor from chamber 48 provided at the end of the rotors. These lobe chambers become progressively smaller to compress the low pressure gas or vapor trapped therein.
  • the compressor 10 includes a discharge port 20 for discharging high pressure refrigerant which has been compressed between the rotors to the condenser 12 through the conduit22.
  • the condenser 12 is conventional and functions to receive the high-pressure vapor from the compressor discharge port 20.
  • the compressor 10 is driven by means of'an electric motor 50 which is connected directly to the rotors 44 and 46 by a drive shaft 52.
  • the fixed intermediate pressure inlet port 32 is connected to the lobe chambers between the rotors'44 and 46 by means of slide valve 54.
  • the slide valve 54 is positioned for axial movement in a bore 56 provided in the housing 45 in a parallel relation to the rotor lobes 44 and 46 and is connected to chamber 48 through opening 49.
  • the slide valve 54 forms a movable wall for a portion of the wall of the bores 43 and 47 in the housing 45 and is axially movable in the bore 56 from the maximum capacity position shown in FIG. 1 to a minimum capacity position shown in FIG. 2.
  • the mass of the valve 54 can be reduced by providing a recess 55 in each end of the valve which terminate at a center section 57.
  • the slide valve 54 is biased to the minimum capacity position by means of a spring 74.
  • the spring 74 is mounted on a guide rod 75 which extends into the recess 55 on one end of the valve 54.
  • the spring 74 is seated on a fixed plate 77 and bears against the center section 57 of the valve.
  • the point of admission of low pressure vapor into the cavity or chamber between the rotors is determined by the position of the face or end 62 of the slide valve 54.
  • a portion of the bores 43 and 47 for rotors 44 and 46 will be opened to the bore 56.
  • the rotor lobes therefore cannot close until the lobes pass the end 62 of the slide valve 54.
  • the stroke of the compressor at the minimum capacity position will be equal to the distance from the end 62 of the valve 54 to the discharge end 59 of the rotors 44 and 46.
  • Means are provided in the slide valve 54 for connecting the fixed intermediate. inlet port 32 with the cavities formed in the rotors 44 and 46.
  • Such means is in the form of an arcuate slot 58 provided in the side wall of the valve 54 and a passage 60 which extends through the center section 57 of the valve from the slot 58 to the cavity in the rotors.
  • the location of the point of introduction of the high pressure vapor'through the passage 60 into the rotors is preferably at the beginning of the compression of the vapor trapped in the cavity of the rotors at suction inlet cut-off.
  • This high pressure vapor is introduced in the cavity between the rotors at a point after the low pressure vapor cut-off and preferably prior to the point where any appreciable compression has taken place in the compressor.
  • the distance of the passage 60 from the face 62 of the slide valve should be equal to or slightly greater than the length of the cavity or chamber closedby the rotors 44 and 46 at suction inlet cut-off.
  • the position of the slide valve 54 in the bore 56 is controlled by means of a piston 64 which is axially slideable in a bore 66 in housing 45.
  • the piston 64 includes a face 72 and is connected to the valve 56 by means of flanges 65.
  • the bore 66 is closed by an end plate 68 to form a chamber 70 for receiving pressure liquid through a port 71.
  • Means are provided to control the amount of movement of the piston 64 in the form of an adjustable pin 79 secured to a plate 68.
  • the slide valve 54 can be controlled by the admission of pressure liquid from any source such as oil pump 80 into chamber 70 through passage 71.
  • a schematic circuit is shown for the control liquid which is controlled by means of a high pressure oil solenoid valve 82 provided in the oil line 73 between the oil pump 80 and the chamber 70.
  • the build up of pressure liquid in the chamber 70 will move the slide valve toward the maximum capacity position against the bias of spring 74.
  • Pressure is relieved in the chamber 70 by means of an oil drain solenoid 84 provided in a discharge line 86 connected to the port 76. Opening of the oil drain solenoid 84 will relieve the pressure in the chamber allowing the spring 74 to move the slide valve towards the minimum capacity position.
  • the slide valve 54 can be positioned anywhere between the maximum capacity position and the minimum capacity position by the proper control of the solenoids and 84.
  • thc stroke will now be equal to the full length-of the rotors since the end 62 of the valve 54 is located at the inlet end of the rotors.
  • the secondary vapor will be admitted at a fixed distance from the end 62 of the'valve 54.
  • Means are provided for guiding the slide valve 54 in the housing in order to maintain the alignment of the crest edge 88 of the slide valve 54 between the rotors 44 and 46.
  • Such means is in the form of a pin 90 provided in a groove 92 in housing 45 which is axially aligned with the slot 58.
  • the pin 90 includes a reduced diameter center section 93 and a piston head 94 at each end of the center section 93.
  • the piston heads 94 have outer diameters substantially equal to the diameter of the grooves 92 and slot 58.
  • Fluid communication is provided through the guide pin 90 by means of an open passage 96 and transverse ports 98. Fluid entering the groove 92 around the center section 93 will flow through ports 98 into passage 96 and out into groove 58.
  • the slide valve 54 in the maximum capacity position shown in F IG 1 provides for the admission of high pressure vapor at a fixed distance from the low pressure vapor inlet chamber 48 This distance is equal to the length of the compression chamber immediately after low pressure suction cut-off and preferably at the beginning of compression before the pressure builds up in the chambers.
  • the slide valve 54 is in the minimum capacity position as seen in FIG. 2, the low pressure suction inlet will be at a point corresponding to the face 62 of the slide valve 54.
  • the end face 62 of the slide valve 54 will determine the point of low pressure suction inlet cut off.
  • a refrigeration system including a high pressure condenser, a subcooler for receiving condensed refrigerant from the condenser, a main evaporator for receiving liquid from said subcooler, said subcooler forming some high pressure refrigerant vapor, and a variable capacity multiple inlet compressor having a pair of oppositely rotating constant mesh rotors defining chambers having a primary inlet cut off and which rotors cooperate to provide a pumping and compressing action, a primary inlet for receiving low pressure vapor from said main evaporator, a secondary inlet for receiving high pressure vapor from said subcooler, and a discharge port for discharging high pressure vapor to said condenser, the improvement comprising: a slide valve mounted for movement relative to said rotors, said valve including low pressure vapor cut-off means for controlling the point of cut-off of admission of low pressure vapor to said rotors and the begining of said compression action, and passage means for providing fluid communication between said secondary inlet and said rotor

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary-Type Compressors (AREA)
US403195A 1973-10-03 1973-10-03 Variable capacity rotary screw compressor Expired - Lifetime US3859814A (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
US403195A US3859814A (en) 1973-10-03 1973-10-03 Variable capacity rotary screw compressor
SE7411972A SE7411972L (enrdf_load_stackoverflow) 1973-10-03 1974-09-24
CA210,022A CA988730A (en) 1973-10-03 1974-09-25 Variable capacity rotary screw compressor
FR7433031A FR2246754B1 (enrdf_load_stackoverflow) 1973-10-03 1974-10-01
GB4380174A GB1444308A (en) 1973-10-03 1974-10-01 Variable capacity rotary screw compressor
DE19742447116 DE2447116A1 (de) 1973-10-03 1974-10-02 Kuehlsystem
JP11428474A JPS554239B2 (enrdf_load_stackoverflow) 1973-10-03 1974-10-03

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US403195A US3859814A (en) 1973-10-03 1973-10-03 Variable capacity rotary screw compressor

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US51354274A Division 1974-10-10 1974-10-10

Publications (1)

Publication Number Publication Date
US3859814A true US3859814A (en) 1975-01-14

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ID=23594831

Family Applications (1)

Application Number Title Priority Date Filing Date
US403195A Expired - Lifetime US3859814A (en) 1973-10-03 1973-10-03 Variable capacity rotary screw compressor

Country Status (7)

Country Link
US (1) US3859814A (enrdf_load_stackoverflow)
JP (1) JPS554239B2 (enrdf_load_stackoverflow)
CA (1) CA988730A (enrdf_load_stackoverflow)
DE (1) DE2447116A1 (enrdf_load_stackoverflow)
FR (1) FR2246754B1 (enrdf_load_stackoverflow)
GB (1) GB1444308A (enrdf_load_stackoverflow)
SE (1) SE7411972L (enrdf_load_stackoverflow)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4058988A (en) * 1976-01-29 1977-11-22 Dunham-Bush, Inc. Heat pump system with high efficiency reversible helical screw rotary compressor
US4197719A (en) * 1976-01-29 1980-04-15 Dunham-Bush, Inc. Tri-level multi-cylinder reciprocating compressor heat pump system
US4342199A (en) * 1980-10-03 1982-08-03 Dunham-Bush, Inc. Screw compressor slide valve engine RPM tracking system
WO1986006798A1 (en) * 1985-05-09 1986-11-20 Svenska Rotor Maskiner Ab Refrigeration plant and rotary positive displacement machine
US5167130A (en) * 1992-03-19 1992-12-01 Morris Jr William F Screw compressor system for reverse cycle defrost having relief regulator valve and economizer port
US5878810A (en) * 1990-11-28 1999-03-09 Kabushiki Kaisha Toshiba Air-conditioning apparatus
US20070134122A1 (en) * 2005-12-09 2007-06-14 Chin-Tang Wang Hydraulic pump
WO2008112568A3 (en) * 2007-03-09 2008-12-24 Johnson Controls Tech Co Compressor with multiple inlets
CN103411338A (zh) * 2013-08-26 2013-11-27 天津商业大学 带两级经济器的螺杆压缩机制冷循环系统
JPWO2016084176A1 (ja) * 2014-11-26 2017-04-27 三菱電機株式会社 スクリュー圧縮機および冷凍サイクル装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS54163416A (en) * 1978-06-14 1979-12-26 Hitachi Ltd Screw compressor

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3568466A (en) * 1968-05-06 1971-03-09 Stal Refrigeration Ab Refrigeration system with multi-stage throttling
US3795117A (en) * 1972-09-01 1974-03-05 Dunham Bush Inc Injection cooling of screw compressors

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1212015A (en) * 1967-05-03 1970-11-11 Svenksa Rotor Maskiner Aktiebo Improvements in and relating to meshing screw-rotor compressors
US3577742A (en) * 1969-06-13 1971-05-04 Vilter Manufacturing Corp Refrigeration system having a screw compressor with an auxiliary high pressure suction inlet

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3568466A (en) * 1968-05-06 1971-03-09 Stal Refrigeration Ab Refrigeration system with multi-stage throttling
US3795117A (en) * 1972-09-01 1974-03-05 Dunham Bush Inc Injection cooling of screw compressors

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4058988A (en) * 1976-01-29 1977-11-22 Dunham-Bush, Inc. Heat pump system with high efficiency reversible helical screw rotary compressor
US4197719A (en) * 1976-01-29 1980-04-15 Dunham-Bush, Inc. Tri-level multi-cylinder reciprocating compressor heat pump system
US4342199A (en) * 1980-10-03 1982-08-03 Dunham-Bush, Inc. Screw compressor slide valve engine RPM tracking system
WO1986006798A1 (en) * 1985-05-09 1986-11-20 Svenska Rotor Maskiner Ab Refrigeration plant and rotary positive displacement machine
US4748831A (en) * 1985-05-09 1988-06-07 Svenska Rotor Maskiner Ab Refrigeration plant and rotary positive displacement machine
US5878810A (en) * 1990-11-28 1999-03-09 Kabushiki Kaisha Toshiba Air-conditioning apparatus
US5167130A (en) * 1992-03-19 1992-12-01 Morris Jr William F Screw compressor system for reverse cycle defrost having relief regulator valve and economizer port
US20070134122A1 (en) * 2005-12-09 2007-06-14 Chin-Tang Wang Hydraulic pump
WO2008112568A3 (en) * 2007-03-09 2008-12-24 Johnson Controls Tech Co Compressor with multiple inlets
CN103411338A (zh) * 2013-08-26 2013-11-27 天津商业大学 带两级经济器的螺杆压缩机制冷循环系统
JPWO2016084176A1 (ja) * 2014-11-26 2017-04-27 三菱電機株式会社 スクリュー圧縮機および冷凍サイクル装置
EP3225848A4 (en) * 2014-11-26 2018-10-17 Mitsubishi Electric Corporation Screw compressor and refrigeration cycle device

Also Published As

Publication number Publication date
FR2246754A1 (enrdf_load_stackoverflow) 1975-05-02
FR2246754B1 (enrdf_load_stackoverflow) 1979-02-16
GB1444308A (en) 1976-07-28
JPS554239B2 (enrdf_load_stackoverflow) 1980-01-29
SE7411972L (enrdf_load_stackoverflow) 1975-04-04
JPS5061710A (enrdf_load_stackoverflow) 1975-05-27
CA988730A (en) 1976-05-11
DE2447116A1 (de) 1975-04-10

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