WO2010035592A1 - スクリュー圧縮機 - Google Patents

スクリュー圧縮機 Download PDF

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Publication number
WO2010035592A1
WO2010035592A1 PCT/JP2009/064444 JP2009064444W WO2010035592A1 WO 2010035592 A1 WO2010035592 A1 WO 2010035592A1 JP 2009064444 W JP2009064444 W JP 2009064444W WO 2010035592 A1 WO2010035592 A1 WO 2010035592A1
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WO
WIPO (PCT)
Prior art keywords
discharge
bypass passage
casing
screw
chamber
Prior art date
Application number
PCT/JP2009/064444
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English (en)
French (fr)
Japanese (ja)
Inventor
龍一郎 米本
昌幸 浦新
Original Assignee
日立アプライアンス株式会社
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 日立アプライアンス株式会社 filed Critical 日立アプライアンス株式会社
Priority to EP09816009A priority Critical patent/EP2343457A1/en
Priority to CN2009801379258A priority patent/CN102165197A/zh
Publication of WO2010035592A1 publication Critical patent/WO2010035592A1/ja

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • 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
    • F04C28/26—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 using bypass channels
    • 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
    • F04C28/28—Safety arrangements; Monitoring

Definitions

  • the present invention relates to a screw compressor used for refrigeration and air conditioning, and is particularly suitable for a screw compressor whose capacity is controlled.
  • Patent Document 1 A conventional screw compressor is described in Patent Document 1. This screw compressor reduces the abnormal load on the screw rotor and the bearing member that supports it by bypassing the compressed gas to the discharge side by operating the relief valve provided on the slide valve when the discharge pressure rises abnormally Like to do.
  • IPLV period coefficient of performance
  • An object of the present invention is to obtain a screw compressor capable of preventing over-compression with a simple structure.
  • Another object of the present invention is to obtain a screw compressor capable of improving the period performance coefficient by improving the efficiency in the operating range of the low load region.
  • the present invention forms a compression chamber by a pair of screw rotors including a male rotor and a female rotor, and a casing that houses the pair of screw rotors, and the casing includes a compressed gas.
  • the casing In the screw compressor in which the discharge port for discharging the gas and the discharge chamber into which the compressed gas discharged from the discharge port flows are formed, the casing on both the male rotor side and the female rotor side in the vicinity of the discharge port.
  • a bypass passage that connects the compression chamber and the discharge chamber is provided, and a valve that opens and closes the bypass passage is provided.
  • valve for opening and closing the bypass passage may be configured to open when the pressure in the compression chamber communicating with the bypass passage is higher than the pressure in the discharge chamber.
  • bypass passage may be formed at a position communicating with the compression chamber within a set volume ratio of 1.5 to 3.0, preferably 1.5 to 2.7.
  • the present invention is particularly effective when applied to a configuration in which the screw rotor is driven by an electric motor capable of controlling the number of revolutions by an inverter.
  • a pair of screw rotors including a male rotor and a female rotor, and a casing that houses the pair of screw rotors form a compression chamber, and discharge that discharges compressed gas to the casing.
  • the compression chamber and the discharge chamber are respectively connected to the casings on both sides of the discharge port.
  • a bypass passage is provided, and a valve for opening and closing the bypass passage is provided.
  • Still another feature of the present invention is that a pair of screw rotors including a male rotor and a female rotor, a main casing that houses the pair of screw rotors, a discharge casing provided on a discharge side of the main casing, and the screw rotor
  • a motor casing containing an electric motor for driving the motor, a discharge port provided in at least one of the main casing and the discharge casing, a compression chamber formed by the pair of screw rotors and the main casing, and the discharge casing
  • a discharge chamber into which compressed gas discharged from the discharge port flows is provided in the discharge casing in the vicinity of the discharge port, and communicates the compression chamber and the discharge chamber.
  • a bypass passage and the compression communicating with the bypass passage Pressure is closed when less than the pressure of the discharge chamber is to provided a valve for opening and closing the bypass passage is configured to open when high.
  • bypass passage may be provided on both the male rotor side and the female rotor side of the discharge port formed in the casing.
  • both the male rotor side and female rotor side casings in the vicinity of the discharge port are provided with bypass passages that connect the compression chamber and the discharge chamber, respectively, and valves that open and close the bypass passage
  • valve that opens and closes the bypass passage is configured to open when the pressure in the compression chamber communicating with the bypass passage is higher than the pressure in the discharge chamber, so that overcompression can be prevented. Since the efficiency in the driving range of the area can be improved, the period coefficient of performance can be improved.
  • FIG. 2 is a cross-sectional view taken along line AA of the screw compressor shown in FIG. 1 and showing a screw rotor rotation position when a bypass passage provided in a discharge casing is opened or just after being opened.
  • FIG. 2 is a cross-sectional view taken along line AA of the screw compressor shown in FIG. 1 and shows a screw rotor rotation position when a bypass passage is fully opened or immediately after that.
  • FIG. 2 is a cross-sectional view taken along line AA of the screw compressor shown in FIG.
  • FIG. 5 is a cross-sectional view taken along line BB in FIG. 4.
  • FIG. 4 is a view showing a modification of the embodiment shown in FIGS. 3A to 3C and corresponding to FIGS. 3A to 3C.
  • FIG. 4 shows another modification of the embodiment shown in FIGS. 3A to 3C and corresponds to FIGS. 3A to 3C.
  • FIG. 4 is a view showing still another modified example of the embodiment shown in FIGS.
  • FIG. 4 is a view showing still another modified example of the embodiment shown in FIGS. 3A to 3C, and showing the vicinity of the discharge port in FIGS. 3A to 3C in an enlarged manner.
  • FIG. 4 is a view showing still another modified example of the embodiment shown in FIGS. 3A to 3C, and showing the vicinity of the discharge port in FIGS. 3A to 3C in an enlarged manner.
  • FIG. 4 is a view showing still another modified example of the embodiment shown in FIGS. 3A to 3C, and showing the vicinity of the discharge port in FIGS. 3A to 3C in an enlarged manner.
  • FIG. 4 is a view showing still another modified example of the embodiment shown in FIGS. 3A to 3C, and showing the vicinity of the discharge port in FIGS. 3A to 3C in an enlarged manner.
  • FIG. 8B is a view in which a leaf spring type valve and a valve presser are respectively provided in the bypass passage provided in the vicinity of the discharge port portion shown in FIG.
  • FIG. 10 is a cross-sectional view taken along line DD of the valve portion shown in FIG. 9.
  • FIG. 5 is a diagram showing another embodiment of the example shown in FIG. 4 and corresponding to FIG. 4.
  • FIG. 12 is a cross-sectional view of the vicinity of the valve portion as viewed from the direction of arrows CC in FIG. 11.
  • FIG. 13 shows another example of the example shown in FIGS. 11 and 12, and is a cross-sectional view of a portion corresponding to FIG.
  • FIG. 13 is a cross-sectional view of a portion corresponding to FIG. 12, showing still another example of the example shown in FIGS.
  • FIG. 15 is a cross-sectional view of the vicinity of the valve portion viewed from the direction of arrows EE in FIG. 14.
  • FIG. 15 is a sectional view of a portion corresponding to FIG. 12 or FIG. 14, showing still another example of the example shown in FIG. 11 and FIG. 12.
  • FIG. 1 is a longitudinal sectional view of a screw compressor showing Example 1 of the present invention.
  • the screw compressor shown in FIG. 1 is roughly divided into a compressor unit 17 and a motor unit 18.
  • the gas to be compressed (for example, the refrigerant flowing through the refrigeration cycle) is sucked from a suction port 20 formed in the motor casing 16 on the motor unit 18 side, and the stator 3 and the rotor 4 constituting the motor (drive motor) 22
  • the air is compressed from the suction port 9 by a compressor unit 17 including a pair of screw rotors (male rotor 2 and female rotor 2A).
  • the compressed gas is discharged from the discharge port 10 and the discharge radial port 44 to the discharge chamber 12 and then flows into the oil separator 80 to separate the oil from the compressed gas, and from the discharge port 19 to the outside of the compressor. It is designed to be discharged.
  • the compressor unit 17 includes a main casing 1 that encloses the screw rotors 2 and 2A and accommodates the roller bearing 6, a discharge casing 21 that forms the discharge chamber 12 and accommodates the roller bearing 7 and the ball bearing 8. ing.
  • the main casing 1 is also formed with a suction port 9, a discharge port 10 and a discharge radial port 44.
  • the suction port 20 and the suction port 9 form a suction flow path to the screw rotors 2 and 2A.
  • the discharge port 10, the discharge radial port 44, and the discharge chamber 12 form a discharge passage from the screw rotors 2 and 2A.
  • the screw rotor 2 includes a pair of male rotor 2 and female rotor 2A (see FIGS.
  • a compression chamber is formed by the meshed portion of the cylindrical bore and the male rotor 2 and female rotor 2A.
  • the shaft portions provided on both sides of the male rotor 2 are supported by a roller bearing 6 provided in the main casing 1, and a roller bearing 7 and a ball bearing 8 provided in the discharge casing 21.
  • the motor unit 18 includes a motor casing 16, a stator 3, a rotor 4, and the like.
  • the motor unit 18 is configured to transmit the driving force to the male rotor 2 of the compressor unit 17.
  • the stator 3 is mounted on a motor casing 16, and the rotor 4 is fixed to a shaft portion provided on the inner peripheral side of the stator 3 and on the motor portion side of the male rotor 2. With this configuration, the driving force of the motor 22 is transmitted to the male rotor 2, and the female rotor 2 ⁇ / b> A is driven by the male rotor 2.
  • the capacity adjustment with respect to the load is performed by inputting a signal from an intake pressure sensor (not shown) and a signal from a discharge pressure sensor (not shown) to a control device (not shown), and an inverter ( The number of revolutions of the motor 22 is controlled by an unillustrated) to adjust the discharge amount.
  • a bypass passage (the male bypass passage 50 shown in FIGS. 3A to 3C and the bypass passage communicating the discharge chamber 21 with the discharge casing 21 forming the compression chamber).
  • a valve 110 for opening and closing the bypass passage, and the pressure in the compression chamber is adjusted by the bypass passages 50 and 51 and the valve 110.
  • FIG. 2 is a diagram showing the relationship between the volume V and the pressure P in an arbitrary compression chamber of the screw rotor 2, 2A shown in FIG.
  • LP represents the suction pressure
  • HP2 represents the discharge pressure during full load operation
  • HP1 represents the discharge pressure during unload operation.
  • the operation cycle is a1-b1-c1-d1.
  • the operation cycle when the bypass passages 50 and 51 that connect the compression chamber and the discharge chamber and the valve 110 are not provided is a1-b1-g3.
  • -F1-d1 and e1-b1-g3 is an overcompressed area where it was compressed unnecessarily.
  • the operation cycle can be set to a1-e1-f1-d1, and therefore, unnecessary overcompression can be prevented.
  • n Polytropic index determined for each refrigerant VT: Suction volume (maximum rotor volume) It is.
  • the bypass passages 50 and 51 may be provided so as to communicate with the compression chamber at the rotation angle.
  • 3A to 3C are cross-sectional views (discharge port portion) taken along line AA of the screw compressor shown in FIG.
  • the male compression chamber 30a is formed by the male casing bore 40a and the male rotor 2
  • the female compression chamber 30b is formed by the female casing bore 40b and the female rotor 2A.
  • the male compression chamber 30a and the female compression chamber 30b are also communicated with each other.
  • FIG. 3A shows the screw rotor rotation position when the bypass passage 50 provided in the discharge casing 21 is opened or just after it is opened.
  • the male bypass passage 50 may be provided so as to be in contact with the reverse surface tangent 120 of the male rotor 2 at the determined rotation angle.
  • the female bypass passage 51 may be provided so as to be in contact with the reverse surface tangent 123 of the female rotor at the determined rotation angle.
  • the size of the holes of the bypass passages 50 and 51 is set to be equal to or smaller than the minimum tooth thickness of the male rotor and the female rotor so that adjacent compression chambers do not communicate with each other.
  • FIG. 3B shows the screw rotor rotation position when the bypass passages 50 and 51 are fully opened or just after that.
  • the compressed gas continues to be bypassed to the discharge chamber 12 by the over-compressed gas from the bypass passages 50 and 51 until the discharge from the male discharge port 42 and the female discharge port 43 is started. .
  • FIG. 3C shows the screw rotor rotation position when the gas to be compressed in the compression chambers 30a and 30b starts to be discharged from the male side discharge port 42 and the female side discharge port 43 provided in the discharge casing 21 to the discharge chamber 12. .
  • FIG. 4 is a cross-sectional view of the valve 110 provided in the male bypass passage 50 of the screw compressor shown in FIG. Since the pressure of the discharge chamber 12 acts through the discharge passage 100 in the valve passage 115 shown in the figure, when the pressure in the bypass passage 50 becomes higher than the pressure in the valve passage 115, the valve 110 is pushed up by the pressure difference. The compressed gas in the compression chamber 30a is discharged to the discharge chamber 12 through the valve passage 115.
  • the female bypass passage 51 is configured in the same manner.
  • FIG. 5 is a cross-sectional view taken along line BB in FIG.
  • a spring force is always applied to the valve 110 by a spring 112 in a direction to close the valve 110.
  • the valve 110 is opened, The over-compressed gas in the compression chamber 30 a flows out into the discharge chamber 12.
  • 111 is an oil hole
  • 113 is a flange that holds the valve 110, and this flange 113 is attached to the discharge casing 21 via a screw 114.
  • FIGS. 6A to 6B show a modification of the embodiment shown in FIGS. 3A to 3B and correspond to FIGS. 3A to 3C.
  • the male-side bypass passage 50 is first opened to bypass and discharge the overcompressed gas in the compression chamber 30a to the discharge chamber, and the female-side bypass hole 51 is opened after a delay. The compressed gas is discharged into the discharge chamber.
  • FIG. 6A by setting the male-side bypass passage 50 and the female-side bypass passage 51 at positions that overlap and open by a certain interval, it is possible to prevent over-compression continuously over a wide range. it can.
  • the bypass passages 50 and 51 are installed so as to be shifted so that the opening sections do not overlap, and the bypass passage may be set in this way.
  • FIGS. 7A to 7B show still another modification of the embodiment shown in FIGS. 3A to 3C, and are enlarged views showing the vicinity of the discharge port 10 in FIGS. 3A to 3C.
  • the bypass passage 50 when the bypass passage 50 is installed only on the male side, and the tooth thickness of the female rotor is thin and the female bypass passage cannot be installed large, the bypass passage is provided only on the male side. It is good to make it.
  • a bypass passage and a valve are not required on the female side, and the cost can be reduced.
  • the bypass passage 51 may be provided only on the female side without providing the bypass passage on the male side.
  • it is also effective to provide bypass passages on the male side and the female side, respectively, and to make the opening area of the male side bypass passage larger than the opening area of the female side bypass passage.
  • FIGS. 3A to 3C show still another modification of the embodiment shown in FIGS. 3A to 3C, and are enlarged views of the vicinity of the discharge port 10 in FIGS. 3A to 3C.
  • the bypass passages 50 and 51 provided in the discharge casing are elongated holes. By configuring in this way, a sufficiently large bypass passage area of the bypass passage can be secured. The flow path resistance of the compressed gas that is bypassed to the discharge chamber can be reduced.
  • a plurality of male side bypass passages 50 and 50a and a plurality of female side bypass passages 51 and 51a are provided at arbitrary different set volume ratio positions.
  • the bypass passages are provided at the positions of two different arbitrary set volume ratios on the male rotor side and the female rotor side
  • the bypass passages are provided at three or more different arbitrary set volume ratio positions. May be provided.
  • path in the position of arbitrary same setting volume ratios was shown, you may form with three or more holes.
  • FIG. 10 is a cross-sectional view of the valve section shown in FIG.
  • a leaf spring type valve 70 and a valve presser 71 to the main casing 1 together with a bolt 73 on the discharge chamber side of the bypass passage communicating the compression chamber and the discharge chamber.
  • the number of manufacturing steps of the valve mechanism can be reduced, the valve structure can be simplified, and the cost of the valve can be reduced.
  • configuring the valve that opens and closes the bypass passage with a leaf spring type valve, it is possible to provide a plurality of valves in a limited narrow space.
  • valve for opening and closing the bypass passage by a leaf spring type valve.
  • FIGS. 11 and 12 show another embodiment of the example shown in FIGS. 4 and 5.
  • the valve 110 is provided in the vertical direction (perpendicular to the axis).
  • the valve 110 is provided in the lateral direction (axial direction).
  • FIG. 12 is a cross-sectional view of the vicinity of the valve portion as viewed from the direction of arrows CC in FIG. 11 and 12, the same reference numerals as those in FIGS. 4 and 5 indicate the same or corresponding parts.
  • the valve 110 horizontally, the length of the bypass passage 50 that communicates the compression chamber and the discharge chamber can be made shorter than the example shown in FIGS.
  • reference numeral 117 denotes a spacer, which corresponds to the flange 113 in FIG.
  • FIG. 13 shows another example of the example shown in FIGS. 11 and 12, and is a cross-sectional view of a portion corresponding to FIG.
  • high-pressure oil is guided from the oil tank 25 to the valve cylinder 143 via the pipe 141, and the valve 140 that opens and closes the bypass passage 50 is hydraulically operated.
  • the valve 140 is pressed to a position where the bypass passage 50 and the discharge passage 100 are closed by high pressure oil pressure.
  • FIGS. 11 and 12 show still another example of the example shown in FIGS. 11 and 12, FIG. 14 is a sectional view corresponding to FIG. 12, and FIG. 15 is a view taken along the line EE in FIG. It is sectional drawing of the valve part vicinity seen from the direction.
  • a valve 135 having a hole in the center of a cylinder is provided in the middle of a bypass passage 50 that communicates the compression chamber and the discharge chamber 12, and the valve 135 is connected to the shaft 135 by a step motor 131 in FIG. 15.
  • the bypass passage 50 is opened and closed by turning 90 degrees.
  • the step motor 131 is controlled by inputting a signal from the pressure sensor 133 provided in the bypass passage 50 communicating with the compression chamber and the discharge chamber and the pressure sensor 133 installed in the discharge chamber 12 to the control device 132.
  • the valve 135 When the pressure of 50 becomes higher than the pressure of the discharge chamber 12, the valve 135 is opened, and when the pressure of the bypass passage 50 becomes lower than the pressure of the discharge chamber 12, the valve 135 is closed. It is something to control. According to this example, it is possible to provide a valve mechanism having a high followability with respect to a pressure change in the compression chamber.
  • FIG. 16 shows still another example of the example shown in FIGS. 11 and 12, and shows a cross-sectional view of a portion corresponding to FIG. 12 or FIG.
  • an electromagnetic valve 136 is provided in the middle of the bypass passage 50 that communicates the compression chamber and the discharge chamber 12, and the controller 132 controls the pressure in the bypass passage 50 and the discharge chamber 12 in the same manner as in the example shown in FIG.
  • the electromagnetic valve 136 is controlled by looking at the pressure and the pressure.
  • By opening the electromagnetic valve 136 the compressed gas in the compression chamber can be bypassed to the discharge chamber 12 via the bypass passage 50 and the discharge passage 100.
  • a complicated valve opening / closing mechanism can be used, and a valve mechanism having high followability to the pressure change in the compression chamber can be obtained as in the example shown in FIG.
  • a bypass passage that connects the compression chamber and the discharge chamber is provided in the vicinity of the discharge port, and a valve that opens and closes the bypass passage is provided. Can be maintained or opened to the discharge chamber.
  • the compression chamber pressure becomes higher than the discharge chamber pressure, it is possible to suppress overcompression in the compression chamber by opening the bypass passage.
  • the bypass passage valve opens and compression The compressed gas in the room can be discharged to the discharge chamber side via the bypass passage.
  • bypass passage is configured to be installed within a set volume ratio of 1.5 to 3.0, preferably 1.5 to 2.7, and an opening / closing valve for opening and closing the bypass passage is provided. This makes it possible to perform optimal operation during unload operation. Furthermore, by providing bypass passages that connect the compression chamber and the discharge chamber on both the male rotor side and the female rotor side, the compressed gas in the compression chamber can be efficiently discharged to the discharge chamber.
  • bypass passages that connect the compression chamber and the discharge chamber are respectively provided at positions that communicate with the compression chambers having different set volume ratios, over-compression during unload operation can be prevented in a wider operating range. effective.
  • the flow resistance of the bypass passage can be reduced, and the volume of the entire bypass passage can be kept small, thereby reducing the uncompressed volume generated by the bypass passage.
  • a decrease in volume efficiency can be suppressed.

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  • 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)
PCT/JP2009/064444 2008-09-26 2009-08-18 スクリュー圧縮機 WO2010035592A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP09816009A EP2343457A1 (en) 2008-09-26 2009-08-18 Screw compressor
CN2009801379258A CN102165197A (zh) 2008-09-26 2009-08-18 螺旋压缩机

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2008-247063 2008-09-26
JP2008247063A JP2010077897A (ja) 2008-09-26 2008-09-26 スクリュー圧縮機

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WO2010035592A1 true WO2010035592A1 (ja) 2010-04-01

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EP (1) EP2343457A1 (zh)
JP (1) JP2010077897A (zh)
CN (1) CN102165197A (zh)
TW (1) TW201013052A (zh)
WO (1) WO2010035592A1 (zh)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2423508A3 (en) * 2010-08-30 2016-05-18 Hitachi Appliances, Inc. capacity control for a screw compressor
EP2458215A3 (en) * 2010-11-26 2016-10-05 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Capacity control for a screw compressor

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5358608B2 (ja) 2011-03-30 2013-12-04 日立アプライアンス株式会社 スクリュー圧縮機及びこれを用いたチラーユニット
US10677246B2 (en) * 2016-07-18 2020-06-09 Johnson Controls Technology Company Variable volume ratio compressor
BR112019012004A2 (pt) * 2016-12-14 2019-10-29 Hedman Ericsson Patent Ab método para controlar o tamanho de uma câmara de combustão, e, atuador.

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JPH1113675A (ja) * 1997-06-20 1999-01-19 Hitachi Ltd スクリュー圧縮機の容量制御装置
JPH1193875A (ja) * 1997-07-25 1999-04-06 Kobe Steel Ltd ２段形油冷式スクリュ圧縮機
JP2003003976A (ja) * 2001-06-26 2003-01-08 Kobe Steel Ltd スクリュ圧縮機
JP2008157109A (ja) * 2006-12-25 2008-07-10 Hitachi Appliances Inc スクロール圧縮機および冷凍サイクル

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JPS5919833Y2 (ja) * 1980-04-21 1984-06-08 三菱重工業株式会社 全域リリ−フ弁付きスクリユ−型圧縮機
JP4190803B2 (ja) * 2002-05-23 2008-12-03 株式会社神戸製鋼所 制振装置
JP3931168B2 (ja) * 2003-11-10 2007-06-13 株式会社日立産機システム オイルフリースクリュー圧縮機

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JPS59185889A (ja) * 1983-04-02 1984-10-22 ライボルト−ヘレ−ウス・ゲゼルシヤフト・ミツト・ベシユレンクテル・ハフツング ２軸式真空ポンプ
JPS6321379A (ja) * 1986-07-11 1988-01-28 Kobe Steel Ltd スクリユ式真空ポンプ
JPH0443883A (ja) 1990-06-11 1992-02-13 Hitachi Ltd スクリュー圧縮機
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JPH10274180A (ja) * 1997-03-31 1998-10-13 Nippon Comtec Kk スクリュ圧縮機
JPH1113675A (ja) * 1997-06-20 1999-01-19 Hitachi Ltd スクリュー圧縮機の容量制御装置
JPH1193875A (ja) * 1997-07-25 1999-04-06 Kobe Steel Ltd ２段形油冷式スクリュ圧縮機
JP2003003976A (ja) * 2001-06-26 2003-01-08 Kobe Steel Ltd スクリュ圧縮機
JP2008157109A (ja) * 2006-12-25 2008-07-10 Hitachi Appliances Inc スクロール圧縮機および冷凍サイクル

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2423508A3 (en) * 2010-08-30 2016-05-18 Hitachi Appliances, Inc. capacity control for a screw compressor
EP2458215A3 (en) * 2010-11-26 2016-10-05 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Capacity control for a screw compressor

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JP2010077897A (ja) 2010-04-08
CN102165197A (zh) 2011-08-24
TW201013052A (en) 2010-04-01
EP2343457A1 (en) 2011-07-13

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