WO2018008052A1 - Compresseur à vis et dispositif à cycle de réfrigération - Google Patents

Compresseur à vis et dispositif à cycle de réfrigération Download PDF

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Publication number
WO2018008052A1
WO2018008052A1 PCT/JP2016/069740 JP2016069740W WO2018008052A1 WO 2018008052 A1 WO2018008052 A1 WO 2018008052A1 JP 2016069740 W JP2016069740 W JP 2016069740W WO 2018008052 A1 WO2018008052 A1 WO 2018008052A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
discharge port
screw
temperature
port valve
Prior art date
Application number
PCT/JP2016/069740
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English (en)
Japanese (ja)
Inventor
雅浩 神田
雅章 上川
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2016/069740 priority Critical patent/WO2018008052A1/fr
Publication of WO2018008052A1 publication Critical patent/WO2018008052A1/fr

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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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/50—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees
    • F04C18/52—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present invention relates to a refrigeration cycle apparatus having a screw compressor that compresses and discharges a fluid.
  • a screw compressor that compresses and discharges a fluid.
  • liquid compression in a screw compressor is prevented.
  • the screw compressor compresses low-temperature and low-pressure gaseous refrigerant (refrigerant gas) and discharges high-temperature and high-pressure refrigerant gas. Then, the condenser exchanges heat between the refrigerant gas and the external heat source so that the refrigerant gas becomes a high-pressure refrigerant liquid. Thereafter, the expansion valve squeezes and expands the high-pressure refrigerant liquid to obtain a low-temperature and low-pressure gas-liquid two-phase refrigerant.
  • refrigerant gas low-temperature and low-pressure gaseous refrigerant
  • the condenser exchanges heat between the refrigerant gas and the external heat source so that the refrigerant gas becomes a high-pressure refrigerant liquid.
  • the expansion valve squeezes and expands the high-pressure refrigerant liquid to obtain a low-temperature and low-pressure gas-liquid two-phase refrigerant.
  • the evaporator exchanges heat between the external heat source and the low-pressure gas-liquid two-phase refrigerant so that the low-pressure gas-liquid two-phase refrigerant becomes low-temperature and low-pressure refrigerant gas.
  • the low and low pressure refrigerant gas returns to the screw compressor.
  • the external heat source heat-exchanged with the low-pressure gas-liquid two-phase refrigerant in the evaporator has a low temperature.
  • thermometer and pressure gauge are input to the controller, and the saturation temperature and measured temperature at the measured pressure are Calculate the difference.
  • the superheat degree control which adjusts the opening degree of an expansion valve is performed so that measurement temperature may always become only a fixed value higher than saturation temperature (for example, refer patent document 1, 2).
  • the refrigerant liquid is prevented from flowing into the compressor by performing the superheat degree control for controlling the refrigerant to the superheated gas state.
  • the opening degree adjustment of the expansion valve cannot be followed.
  • the refrigerant liquid accumulates in the evaporator, eventually returning to the refrigerant liquid flowing into the compressor, and the gate rotor of the screw compressor may be damaged by the liquid compression. It was.
  • the present invention has been made to solve the above-described problems, and provides a screw compressor and a refrigeration cycle apparatus capable of suppressing breakage and the like even when refrigerant liquid returns to the compressor. With the goal.
  • a screw compressor includes a cylindrical casing main body, a screw rotor housed in an inner cylindrical surface of the casing main body and having a plurality of screw grooves on the outer peripheral surface, and a plurality of teeth meshed with the screw grooves.
  • a discharge port valve disposed between the casing main body, the casing main body and the screw rotor, wherein the discharge timing of the compressed refrigerant is changed according to the position in the direction of the rotation axis of the screw rotor; And a drive device that moves the discharge port valve according to the superheat temperature of the refrigerant flowing on the side.
  • the refrigeration cycle apparatus includes the above-described screw compressor, condenser, decompression device, and evaporator connected to each other to form a refrigerant circuit in which refrigerant is circulated, and overheating in the refrigerant flowing out of the evaporator
  • a discharge port valve control device that determines the position of the discharge port valve of the screw compressor according to the temperature is provided.
  • the drive device is arranged so that the discharge port valve is positioned at a position where the refrigerant discharge timing is advanced. Control.
  • the refrigeration cycle apparatus relates to a temperature detection device that detects a temperature on the refrigerant outflow side of the evaporator, a pressure detection device that detects a pressure on the refrigerant outflow side of the evaporator, and a detection of the temperature detection device.
  • An arithmetic device that calculates the superheat temperature from the temperature and the pressure related to detection by the pressure detection device is further provided.
  • the position of the discharge port valve is determined by the refrigerant overheating temperature, for example, when it is predicted that the refrigerant liquid has returned to the compression chamber, the discharge is performed.
  • the discharge timing can be advanced, the compression time can be reduced, and the pressure rise in the compression chamber can be suppressed. For this reason, the screw compressor is hardly damaged by liquid compression, and a highly reliable screw compressor and refrigeration cycle apparatus can be obtained.
  • FIG. (1) explaining the internal structure in the screw compressor 102 which concerns on Embodiment 1 of this invention.
  • FIG. (2) explaining the internal structure in the screw compressor 102 which concerns on Embodiment 1 of this invention.
  • FIG. (2) explaining the internal structure in the screw compressor 102 which concerns on Embodiment 1 of this invention.
  • FIG. (1) explaining the internal structure in the screw compressor 102 which concerns on Embodiment 1 of this invention.
  • FIG. (2) explaining the internal structure in the screw compressor 102 which concerns on Embodiment 1 of this invention.
  • FIG. 1 is a diagram showing a configuration of a refrigeration cycle apparatus 100 including a screw compressor 102 according to Embodiment 1 of the present invention.
  • the screw compressor 102 will be described as a device that constitutes a refrigerant circuit in which refrigerant is circulated.
  • the fluid that is sucked, compressed, and discharged by the screw compressor 102 according to the first embodiment will be described as a refrigerant that changes its state to gas and liquid.
  • the refrigeration cycle apparatus 100 in the first embodiment has a refrigerant circuit configured by connecting a screw compressor 102, a condenser 104, an expansion valve 105, and an evaporator 106 in order by refrigerant piping.
  • the inverter device 101 controls the power supply to the screw compressor 102 based on the instructed frequency, and controls the drive rotation speed of the screw compressor 102.
  • the screw compressor 102 is driven by electric power supplied via an inverter device 101 from a power supply source (not shown). The configuration of the screw compressor 102 will be described later.
  • the condenser 104 cools and condenses the refrigerant gas that is a gaseous refrigerant discharged from the screw compressor 102.
  • An expansion valve 105 serving as a decompression device decompresses and expands the refrigerant liquid that is a liquid refrigerant that has flowed out of the condenser 104.
  • the evaporator 106 evaporates the refrigerant that has passed through the expansion valve 105.
  • the refrigeration cycle apparatus 100 further includes a calculation device 107, a pressure sensor 108, a temperature sensor 109, and a control device 110.
  • the computing device 107 performs computation based on the input physical quantity data.
  • the refrigerant gas superheat temperature of the refrigerant flowing out of the evaporator 106 is calculated from the pressure data detected by the pressure sensor 108 and the temperature data detected by the temperature sensor 109.
  • a pressure sensor 108 serving as a pressure detection device and a temperature sensor 109 serving as a temperature detection device are installed on the refrigerant suction side of the screw compressor 102 and on the refrigerant outlet side of the evaporator 106 on the refrigerant outflow side.
  • the pressure sensor 108 detects the pressure of the refrigerant flowing out from the evaporator 106.
  • the temperature sensor 109 detects the temperature of the refrigerant flowing out of the evaporator 106.
  • the control device 110 controls the frequency of the inverter device 101, the opening degree of the expansion valve 105, and the like, and sends instructions to each device.
  • the control device 110 of the first embodiment has a discharge port valve control device 111.
  • the discharge port valve control device 111 performs position control of the discharge port valve 7 included in the screw compressor 102, as will be described later.
  • the screw compressor 102 sucks and compresses a refrigerant gas, which is a gaseous refrigerant, and then discharges it.
  • the discharge gas discharged from the screw compressor 102 is cooled by the condenser 104.
  • the refrigerant cooled by the condenser 104 is decompressed by the expansion valve 105.
  • the decompressed refrigerant is heated by the evaporator 106 and becomes refrigerant gas.
  • the refrigerant gas flowing out of the evaporator 106 is sucked into the screw compressor 102.
  • FIG. 2 and 3 are diagrams illustrating an internal configuration in screw compressor 102 according to Embodiment 1 of the present invention.
  • FIG. 2 is a view showing a state where the discharge port valve 7 accommodated in the inner cylinder surface of the casing body 1 is located on the discharge side in the rotation axis direction of the screw rotor 3.
  • FIG. 3 is a view showing a state where the discharge port valve 7 is located on the suction side of the screw rotor 3 in the rotation axis direction.
  • the screw compressor 102 according to the first embodiment is a single screw compressor provided with one screw rotor 3 and two gate rotors 6.
  • 2 and 3 are diagrams showing a configuration of a portion located on the upper side of the screw shaft 4 serving as a rotation shaft. The structure of the lower part of the screw shaft 4 is the same as that of the upper part.
  • the screw compressor 102 includes a casing body 1, a screw rotor 3, a gate rotor 6, a motor 2 that rotationally drives the screw rotor 3, a discharge port valve 7, and the like. ing.
  • the cylindrical casing body 1 accommodates the screw rotor 3, the gate rotor 6, the motor 2, the discharge port valve 7, and the like inside the cylinder.
  • the motor 2 includes a stator 2a that is inscribed and fixed to the casing body 1, and a motor rotor 2b that is disposed inside the stator 2a. The motor 2 is driven at a driving rotational speed based on the electric power supplied from the inverter device 101.
  • a screw rotor 3 is arranged in the casing body 1.
  • the screw rotor 3 and the motor rotor 2b are disposed and fixed around the screw shaft 4 serving as a rotation shaft.
  • the screw rotor 3 has a plurality of spiral screw grooves 5a formed on the outer peripheral surface thereof.
  • the screw rotor 3 rotates as the motor rotor 2b fixed to the screw shaft 4 rotates.
  • the screw compressor 102 according to the first embodiment has two gate rotors 6.
  • the two gate rotors 6 are symmetric with respect to the screw shaft 4 and are respectively disposed on both sides of the screw rotor 3.
  • the gate rotor 6 has a disk shape, and a plurality of teeth 6a are provided on the outer peripheral surface in the outer peripheral portion along the circumferential direction.
  • the teeth 6a of the gate rotor 6 are meshed with the screw grooves 5a.
  • a space surrounded by the teeth 6 a of the gate rotor 6, the screw groove 5 a, and the cylinder inner surface side of the casing body 1 becomes the compression chamber 5.
  • a plurality of compression chambers 5 are formed at positions that are point-symmetric with respect to the radial center of the screw rotor 3.
  • the inside of the screw compressor 102 is divided into a low pressure side which is a refrigerant suction side and a high pressure side which is a refrigerant discharge side by a partition wall (not shown).
  • the space on the low-pressure side is a low-pressure chamber (not shown) that serves as a suction pressure atmosphere.
  • the space on the high pressure side is a high pressure chamber (not shown) serving as a discharge pressure atmosphere.
  • a discharge port 10 is provided at a position on the high pressure side of the compression chamber 5 so as to communicate the discharge flow path 11 connected to the high pressure chamber and the compression chamber 5.
  • a slide groove 1 a extending in the direction of the rotation axis of the screw rotor 3 is formed at a position corresponding to the compression chamber 5 inside the casing body 1.
  • a discharge port valve 7 is accommodated in the slide groove 1a so as to be slidable along the slide groove 1a.
  • the discharge port valve 7 is integrated with the casing body 1 and forms a compression chamber 5 together with the casing body 1.
  • the discharge port valve 7 is connected to a drive device 9 such as a piston via a connecting rod 8.
  • a drive device 9 such as a piston
  • the discharge port valve 7 moves in the slide groove 1 a in the direction of the rotation axis of the screw rotor 3.
  • the driving device 9 for driving the discharge port valve 7 is not limited to a driving power source such as a device driven by a gas pressure, a device driven by a hydraulic pressure, a device driven by a motor or the like apart from a piston.
  • the internal volume ratio is a ratio between the volume of the compression chamber 5 at the time of completion of suction (start of compression) and the volume of the compression chamber 5 just before discharge from the discharge port 10. The internal volume ratio is changed by adjusting the timing at which the refrigerant is discharged from the discharge port 10.
  • an inappropriate compression loss does not occur when the actual compression ratio is an operation condition of an appropriate compression ratio that matches the internal volume ratio.
  • the time until the compression chamber 5 reaches the position of the discharge port 10 is long, and the compressed refrigerant gas is over-compressed to the discharge pressure or higher. For this reason, the screw compressor 102 performs extra compression work.
  • the time until the compression chamber 5 reaches the position of the discharge port 10 is short, the discharge port 10 opens before reaching the discharge pressure, and the refrigerant gas flows backward. Will result in insufficient compression. Therefore, the position of the discharge port valve 7 is adjusted so that the discharge start timing is optimal.
  • FIG. 4 is a diagram illustrating a compression principle of the screw compressor 102 according to the first embodiment of the present invention.
  • the operation of the screw compressor 102 according to Embodiment 1 will be described.
  • the screw rotor 3 is rotated by the motor 2 shown in FIGS. 2 and 3 via the screw shaft 4 shown in FIGS. 2 and 3, the teeth 6a of the gate rotor 6 are moved as shown in FIG. It moves relatively in the compression chamber 5 (screw groove 5a).
  • a suction stroke, a compression stroke, and a discharge stroke are sequentially performed.
  • the cycle is repeated with the suction stroke, compression stroke, and discharge stroke as one cycle.
  • each stroke will be described.
  • the discharge port valve 7 and the slide groove 1a are not shown.
  • FIG. 4A shows the state of the compression chamber 5 in the suction stroke.
  • the screw rotor 3 is driven by the motor 2 and rotates in the direction of the solid arrow.
  • the volume of the compression chamber 5 decreases as shown in FIG.
  • the compression chamber 5 communicates with the outside through the discharge flow path 11 as shown in FIG. Thereby, the high-pressure refrigerant gas compressed in the compression chamber 5 is discharged from the discharge passage 11 to the outside. Then, the same compression is performed again on the back surface of the screw rotor 3.
  • FIG. 5 is a diagram showing a flowchart relating to the position control of the discharge port valve 7 of the screw compressor 102 according to Embodiment 1 of the present invention.
  • the position control of the discharge port valve 7 performed by the control device 110 will be described based on FIG.
  • the arithmetic unit 107 calculates the refrigerant gas overheating temperature based on the pressure detected by the pressure sensor 108 and the temperature detected by the temperature sensor 109.
  • the control device 110 determines whether or not the refrigerant gas superheat temperature calculated by the arithmetic device 107 is lower than a preset target refrigerant gas superheat temperature A (step S1).
  • the controller 110 determines that the calculated refrigerant gas superheat temperature is equal to or higher than the target refrigerant gas superheat temperature A
  • the discharge port 10 is placed at an arbitrary position according to the operating state of the refrigeration cycle apparatus 100 as shown in FIG.
  • the discharge port valve 7 is moved so that is positioned (step S2). For example, the screw compressor 102 is moved to a position where the operating efficiency is highest.
  • step S1 when the controller 110 determines in step S1 that the calculated refrigerant gas superheat temperature is lower than the target refrigerant gas superheat temperature A, the position of the discharge port 10 is the lowest internal volume as shown in FIG.
  • the discharge port valve 7 is moved so as to reach the suction side position that is the ratio (step S3).
  • step S3 when the discharge port valve 7 is located at the lowest internal volume ratio, the control device 110 determines whether or not the refrigerant gas superheat temperature is lower than the preset target refrigerant gas superheat temperature B. (Step S4). When the control device 110 determines that the refrigerant gas superheat temperature is lower than the target refrigerant gas superheat temperature B, the control device 110 returns to step S3 and continues to position the discharge port valve 7 at the suction side position where the lowest internal volume ratio is obtained. Let Here, the target refrigerant gas superheat temperature A ⁇ the target refrigerant gas superheat temperature B.
  • step S4 when the control device 110 determines in step S4 that the refrigerant gas superheat temperature is equal to or higher than the target refrigerant gas superheat temperature B, the control device 110 transitions to step S2 and takes an arbitrary position according to the operating state of the refrigeration cycle apparatus 100.
  • the discharge port valve 7 is moved so that the discharge port 10 is located.
  • the screw compressor 102 includes the discharge port valve 7 that adjusts the discharge timing of the refrigerant gas from the compression chamber 5, and the control device 110 includes: If it is determined that the refrigerant gas superheat temperature is lower than the target refrigerant gas superheat temperature, the discharge port valve 7 is moved to the suction side that has the lowest internal volume ratio, and the pressure increase in the compression stroke in the compression chamber 5 is reduced. Since it did in this way, even if refrigerant liquid returns in the screw compressor 102, damage to the gate rotor 6 etc. by the liquid compression in the compression chamber 5 can be suppressed. For this reason, the highly reliable screw compressor 102 and the refrigeration cycle apparatus 100 can be obtained. In addition, an accumulator that is connected to the refrigerant suction side of the screw compressor 102 and accumulates the refrigerant liquid is unnecessary or can be configured as a small accumulator.
  • Embodiment 2 FIG.
  • the screw compressor 102 has been described as a single screw compressor.
  • the present invention is not limited to this.
  • the present invention can also be applied to a twin screw compressor in which a compression chamber is formed by meshing grooves of two screw rotors.
  • the present invention can also be applied to a mono-gate rotor type screw compressor in which one gate rotor 6 is arranged.
  • the pressure sensor 108 and the temperature sensor 109 are provided at the outlet of the evaporator 106, but the refrigerant is sucked into the compression chamber 5 of the screw compressor 102 from the outlet of the evaporator 106. It may be provided anywhere between.
  • the saturation temperature in the pressure and the refrigerant gas superheating temperature which is the difference between the temperatures are calculated.
  • the refrigerant liquid may return to the compression chamber 5 even if the calculated refrigerant gas overheating temperature is 0 ° C. or higher. Therefore, by setting the target refrigerant gas superheat temperature A to, for example, 3 ° C., the screw compressor 102 and the refrigeration cycle apparatus 100 can be obtained with high reliability by suppressing damage to the screw compressor 102. Can do.
  • the refrigeration apparatus has been described as an example of the refrigeration cycle apparatus, but the present invention is not limited to this.
  • the present invention can be applied to other refrigeration cycle apparatuses such as an air conditioner, a refrigerator, and a refrigeration apparatus.
  • 1 casing body 1a slide groove, 2 motor, 2a stator, 2b motor rotor, 3 screw rotor, 4 screw shaft, 5 compression chamber, 5a screw groove, 6 gate rotor, 6a teeth, 7 discharge port valve, 8 connecting rod, 9 Drive device, 10 discharge port, 11 discharge flow path, 100 refrigeration cycle device, 101 inverter device, 102 screw compressor, 104 condenser, 105 expansion valve, 106 evaporator, 107 arithmetic device, 108 pressure sensor, 109 temperature sensor, 110 control device, 111 discharge port valve control device.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

La présente invention concerne un compresseur à vis comprenant : un corps de carter cylindrique ; un rotor à vis qui est logé par une surface cylindrique intérieure du corps de carter et qui comporte de multiples rainures de vis sur sa surface périphérique extérieure ; un rotor de porte qui comporte de multiples dents disposées sur sa périphérie extérieure et entrant en prise avec les rainures de vis ; une soupape d'orifice de décharge qui est disposée entre le corps de carter et le rotor à vis d'une telle manière que la temporisation de décharge d'un fluide frigorigène comprimé change en fonction de la position de la soupape dans la direction de l'axe de rotation du rotor à vis ; et un dispositif d'entraînement qui amène la soupape d'orifice de décharge à se déplacer conformément à une température surchauffée du fluide frigorigène s'écoulant sur le côté aspiration.
PCT/JP2016/069740 2016-07-04 2016-07-04 Compresseur à vis et dispositif à cycle de réfrigération WO2018008052A1 (fr)

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PCT/JP2016/069740 WO2018008052A1 (fr) 2016-07-04 2016-07-04 Compresseur à vis et dispositif à cycle de réfrigération

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2016/069740 WO2018008052A1 (fr) 2016-07-04 2016-07-04 Compresseur à vis et dispositif à cycle de réfrigération

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WO2018008052A1 true WO2018008052A1 (fr) 2018-01-11

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0439573A (ja) * 1990-06-04 1992-02-10 Kobe Steel Ltd セパレート形ヒートポンプ
JPH06213515A (ja) * 1993-01-18 1994-08-02 Kobe Steel Ltd スクリュー式冷凍機の冷媒制御装置
JP2001065480A (ja) * 1999-08-26 2001-03-16 Daikin Ind Ltd スクリュー圧縮機
JP2010255595A (ja) * 2009-04-28 2010-11-11 Daikin Ind Ltd スクリュー圧縮機
JP2012197734A (ja) * 2011-03-22 2012-10-18 Daikin Industries Ltd スクリュー圧縮機

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0439573A (ja) * 1990-06-04 1992-02-10 Kobe Steel Ltd セパレート形ヒートポンプ
JPH06213515A (ja) * 1993-01-18 1994-08-02 Kobe Steel Ltd スクリュー式冷凍機の冷媒制御装置
JP2001065480A (ja) * 1999-08-26 2001-03-16 Daikin Ind Ltd スクリュー圧縮機
JP2010255595A (ja) * 2009-04-28 2010-11-11 Daikin Ind Ltd スクリュー圧縮機
JP2012197734A (ja) * 2011-03-22 2012-10-18 Daikin Industries Ltd スクリュー圧縮機

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