WO2016046907A1 - 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
WO2016046907A1
WO2016046907A1 PCT/JP2014/075230 JP2014075230W WO2016046907A1 WO 2016046907 A1 WO2016046907 A1 WO 2016046907A1 JP 2014075230 W JP2014075230 W JP 2014075230W WO 2016046907 A1 WO2016046907 A1 WO 2016046907A1
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WIPO (PCT)
Prior art keywords
economizer
compression chamber
casing
screw
screw compressor
Prior art date
Application number
PCT/JP2014/075230
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English (en)
Japanese (ja)
Inventor
雅章 上川
下地　美保子
利秀 幸田
英彰 永田
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 JP2016549696A priority Critical patent/JP6177449B2/ja
Priority to PCT/JP2014/075230 priority patent/WO2016046907A1/fr
Priority to EP14902615.5A priority patent/EP3199814B1/fr
Priority to CN201480080608.8A priority patent/CN106605069B/zh
Publication of WO2016046907A1 publication Critical patent/WO2016046907A1/fr

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    • 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
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
    • F04C29/0014—Injection of a fluid in the working chamber for sealing, cooling and lubricating with control systems for the injection of the fluid
    • 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
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid
    • 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

  • the present invention relates to a screw compressor and a refrigeration cycle apparatus.
  • an intermediate cooler has been installed in the refrigeration cycle for the purpose of increasing capacity, improving the performance of the refrigeration cycle, and improving the coefficient of performance (ratio of the refrigeration capacity to the compressor input) in the refrigeration cycle apparatus
  • a refrigeration cycle apparatus that performs an economizer operation that guides the refrigerant gas (hereinafter referred to as economizer gas) to an intermediate portion of the compressor (see, for example, Patent Document 1).
  • an intermediate cooler is arranged between the condenser and the evaporator of the refrigeration cycle, and an economizer pipe that branches in the middle from the condenser to the evaporator, and an expansion for intermediate cooling provided in the economizer pipe And a screw compressor having an economizer port to which economizer piping is connected.
  • an economizer includes a screw rotor and a casing that houses the screw rotor, and the casing jets refrigerant into a compression chamber formed between the screw rotor and the inner surface of the casing.
  • a screw compressor which has a port (for example, refer to patent documents 2).
  • Japanese Patent Laid-Open No. 11-248264 page 4, FIG. 1
  • Japanese Patent No. 4140488 5th page, FIG. 1
  • the coefficient of performance (capacity / power consumption) under rated conditions has been mainly used as an energy saving index of a refrigeration cycle apparatus equipped with a screw compressor.
  • an index close to actual driving conditions for example, a period performance coefficient IPLV (Integrated Part Load Value) determined in the United States has been attracting attention.
  • the operating time is very short throughout the year, and more than 90% of the operating time throughout the year is operated with partial load. And most of the partial load is operation at a load of 75 to 50%, especially among the total load.
  • the refrigerant circulation flow rate and the operation compression ratio differ between full load operation and partial load operation, and the coefficient of performance also changes.
  • the period coefficient of performance is an index that emphasizes the coefficient of performance under partial load conditions.
  • the high / low differential pressure of the refrigeration cycle is large and large capacity operation
  • partial load operation the high / low differential pressure of the refrigeration cycle is small and small capacity operation is performed.
  • the high and low differential pressure is large, and the coefficient of performance can be improved by operating the economizer.
  • the partial load operation the height difference pressure becomes smaller, and the effect of the economizer operation becomes smaller as the height difference pressure becomes smaller.
  • the effect of increasing the capacity is small depending on the conditions, and the coefficient of performance deteriorates due to the increase in power consumption. Therefore, the period coefficient of performance can be improved by switching the drive / stop of the economizer operation according to the operation conditions such as full load operation and partial load operation.
  • the present invention has been made to solve the above-described problems, and is a screw compressor capable of improving the position of the economizer port, realizing a high coefficient of performance in a wide operation range, and improving the performance. And it aims at providing a refrigerating cycle device.
  • a screw compressor includes a casing, a screw rotor arranged to rotate in the casing, a compression chamber formed between the casing and the screw rotor, and compressing refrigerant gas, and an inner cylinder of the casing
  • a first slide valve provided movably, and an economizer port formed on the first slide valve and communicating the economizer gas flow path with the compression chamber according to the position of the first slide valve, , The first position where the economizer gas flow path communicates with the compression chamber, and the economizer port pressure It is to move to a second position not in communication with the chamber.
  • a refrigeration cycle apparatus includes a refrigerant circuit in which the screw compressor, the condenser, the high pressure portion of the intermediate cooler, the decompression device, and the evaporator are connected in order by refrigerant piping, and the intermediate cooler and the decompression device. And an economizer pipe connected to the economizer gas flow path of the screw compressor via the expansion valve for the intercooler and the low pressure portion of the intercooler.
  • FIG. 1 It is a cross-sectional schematic diagram which shows the economizer port position in low differential pressure operation conditions, such as the partial load operation
  • FIG. 1 is a refrigerant circuit diagram of a refrigeration cycle apparatus including a screw compressor according to Embodiment 1 of the present invention.
  • the same reference numerals denote the same or corresponding parts, and are common to the whole text of the embodiments described below.
  • the form of the component shown by the whole specification is an illustration to the last, and is not limited to these description.
  • the combination of the constituent elements is not limited to the combination in each embodiment, and the constituent elements described in the other embodiments can be applied to other embodiments as appropriate.
  • the pressure level is not particularly determined in relation to the absolute value, but is relatively determined in terms of the state and operation of the system, apparatus, and the like.
  • a screw compressor 102 driven by an inverter 101, a condenser 103, a high pressure section of an intercooler 104, an expansion valve 105 as a decompression apparatus, and an evaporator 106 are connected in order by refrigerant piping. Provided with a refrigerant circuit.
  • the refrigeration cycle apparatus 100 further branches from between the intermediate cooler 104 and the expansion valve 105, and an economizer pipe 108 connected to the screw compressor 102 via the intermediate cooler expansion valve 107 and the low pressure portion of the intermediate cooler 104. Have.
  • the condenser 103 cools and condenses the gas discharged from the screw compressor 102.
  • the expansion valve 105 squeezes and expands the mainstream refrigerant that has flowed out of the intercooler 104.
  • the evaporator 106 evaporates the mainstream refrigerant that has flowed out of the expansion valve 105.
  • the intercooler 104 has a high-pressure part and a low-pressure part, and the high-pressure side refrigerant, which is the mainstream refrigerant between the condenser 103 and the expansion valve 105, passes through the high-pressure part, and the low-pressure part.
  • the intermediate cooler 104 cools the high-pressure side refrigerant by exchanging heat between the high-pressure side refrigerant and the intermediate-pressure refrigerant.
  • the refrigeration cycle apparatus 100 further includes a control device 109.
  • the control device 109 controls the inverter 101, the expansion valve 105, the intercooler expansion valve 107, the position control of a slide valve to be described later of the screw compressor 102, and the drive and stop of the economizer operation for injecting economizer gas into the compression chamber. Take control.
  • FIG. 2 is a schematic longitudinal sectional view of the screw compressor according to Embodiment 1 of the present invention.
  • the electric motor 2 is arranged in a cylindrical casing 1 constituting the screw compressor 102.
  • the electric motor 2 includes a stator 2a that is inscribed and fixed to the casing 1, and a motor rotor 2b that is disposed inside the stator 2a.
  • the screw rotor 3 is disposed in the casing 1, the screw rotor 3 and the motor rotor 2 b are disposed on the same axis line, and both the rotors 3 and 2 b are fixed to the screw shaft 4.
  • the screw rotor 3 is formed with a plurality of spiral screw grooves 5 a on the outer peripheral surface thereof, and is connected to a motor rotor 2 b fixed to the screw shaft 4 and is driven to rotate.
  • the teeth 6 a of the gate rotor 6 are engaged with the screw grooves 5 a, and a space surrounded by the teeth 6 a of the gate rotor 6, the screw grooves 5 a and the inner cylindrical surface of the casing 1 becomes the compression chamber 5.
  • the casing 1 is divided into a low pressure side (suction side) and a high pressure side (discharge side) by a partition wall (not shown), and a discharge port 7 (described later) that opens to a discharge chamber (not shown) on the high pressure side. 3) is formed.
  • a slide groove 1a extending in the direction of the rotation axis of the screw rotor 3 is formed on the inner cylindrical surface of the casing 1, and a slide valve that is a first slide valve is formed in the slide groove 1a. 8 is slidably stored. Further, this slide valve 8 forms part of the inner cylinder surface together with the casing 1 in order to form the compression chamber 5. Further, the slide valve 8 is formed with an economizer port 8a. The economizer port 8 a is formed so as to penetrate from the outer peripheral surface that is a sliding contact surface with the slide groove 1 a in the slide valve 8 to the inner peripheral surface that is a sliding contact surface with the screw rotor 3 in the slide valve 8.
  • FIG. 2 shows a case where one slide valve 8 having an economizer port 8 a is provided in the casing 1.
  • the casing 1 has an economizer gas flow path 1b for guiding the refrigerant gas from the intermediate cooler 104 to the compression chamber 5 (screw groove 5a in the compression stroke).
  • the economizer gas flow path 1b is an economizer port 8a. Communicating with the compression chamber 5 via An economizer pipe 108 is connected to the economizer gas flow path 1b.
  • the refrigerant gas that has flowed out of the intermediate cooler 104 and branched and cooled the main stream liquid flows into the compression chamber 5 through the economizer pipe 108, the economizer gas flow path 1b, and the economizer port 8a.
  • the economizer gas flow path 1b in the casing 1 is provided with a space (not shown) for suppressing pulsation when the gas flows, and communicates with the compression chamber 5 via this space. There is also.
  • the slide valve 8 is connected to a drive device 10 such as a piston via a connecting rod 9, and moves in the slide groove 1 a in the direction of the rotation axis of the screw rotor 3 by driving the drive device 10.
  • the driving device 10 for driving the slide valve 8 is not limited to a driving method such as a device driven by gas pressure, a device driven by hydraulic pressure, a device driven by a motor or the like separately from the piston.
  • the refrigerant gas flowing out of the evaporator 106 is sucked into the screw compressor 102 and compressed, and then discharged.
  • the discharged refrigerant gas is cooled by the condenser 103.
  • the refrigerant cooled by the condenser 103 flows into the intermediate cooler 104.
  • the intermediate cooler 104 the high-pressure side refrigerant that flows out of the condenser 103 and flows into the high-pressure part, and the intermediate pressure that branches after passing through the intermediate cooler 104, is decompressed by the intermediate cooler expansion valve 107, and flows into the low-pressure part. Heat is exchanged with the refrigerant.
  • the high-pressure side refrigerant that has left the condenser 103 and directly flows into the high-pressure portion of the intermediate cooler 104 is supercooled by heat exchange with the intermediate-pressure refrigerant. This increase in supercooling increases the refrigeration effect of the evaporator 106.
  • the intermediate pressure refrigerant that has flowed into the low pressure portion of the intermediate cooler 104 cools the high pressure side refrigerant on the high pressure portion side, and then passes through the economizer pipe 108 and the economizer gas flow path 1b to the economizer port provided in the slide valve 8.
  • the compression chamber 5 is injected from 8a. That is, the economizer gas is injected from the economizer port 8a into the compression chamber 5 by the differential pressure between the high pressure and the intermediate pressure of the economizer gas and the pressure in the compression chamber 5, and is mixed with the compressed gas.
  • the operation of the refrigerant circuit when the height difference in the refrigeration cycle such as partial load operation (load operation less than 100%) is small will be described.
  • the high / low differential pressure is small, the differential pressure between the outlet of the intermediate cooler and the compression chamber 5 is small, and the economizer gas does not easily flow into the compression chamber 5. In this way, the differential pressure is reduced during operation of the economizer and the operation becomes unstable.
  • the expansion effect of the refrigerating capacity is small, and the power increase due to the economizer gas flowing in during compression becomes larger and the coefficient of performance decreases. Therefore, under the condition where the high / low differential pressure is small, the intermediate cooler expansion valve 107 is closed and the economizer operation is not performed.
  • FIG. 3 is a diagram showing the compression principle of the screw compressor according to Embodiment 1 of the present invention.
  • the screw rotor 3 is rotated by the electric motor 2 (see FIG. 2) via the screw shaft 4 (see FIG. 2), whereby the teeth 6a of the gate rotor 6 are compressed into the compression chamber 5 (screw groove 5a). Move relatively inside.
  • the suction stroke, the compression stroke, and the discharge stroke are set as one cycle, and this cycle is repeated.
  • each stroke will be described.
  • FIG. 3A shows the state of the compression chamber 5 during the suction stroke.
  • the screw rotor 3 is driven by the electric motor 2 and rotates in the direction of the solid line arrow. As a result, the volume of the compression chamber 5 is reduced as shown in FIG.
  • the compression chamber 5 communicates with the discharge port 7 as shown in FIG. Thereby, the high-pressure refrigerant gas compressed in the compression chamber 5 is discharged from the discharge port 7 to the outside. Then, the same compression is performed again on the back surface of the screw rotor 3.
  • the economizer port 8a, the slide valve 8 having the economizer port 8 and the slide groove 1a are not shown. However, during the economizer operation, economizer gas flows into the compression chamber 5 from the economizer port 8a during the compression stroke. . The economizer gas that has flowed into the compression chamber 5 is compressed together with the suction gas, and is discharged to the outside in the discharge stroke.
  • FIG. 4 is a schematic cross-sectional view showing an economizer port position under high differential pressure operation conditions such as full load operation of the screw compressor according to Embodiment 1 of the present invention.
  • FIG. 5 is a development view of the inner cylindrical surface of the casing and the screw rotor under high differential pressure operation conditions such as full load operation of the screw compressor according to Embodiment 1 of the present invention.
  • the control device 109 moves the slide valve 8 having the economizer port 8a to the discharge side (the left side in FIGS. 4 and 5) as shown by the white arrow in FIGS. 8a is positioned at a position (first position) communicating with the economizer gas flow path 1b and the compression chamber 5.
  • the economizer gas flow path 1b provided in the casing 1 communicates with the compression chamber 5 via the economizer port 8a.
  • economizer gas is injected from the economizer port 8a into the compression chamber 5 via the economizer gas flow path 1b.
  • the pressure (intermediate pressure) when the economizer port 8a is in communication with the compression chamber 5 is increased, the ability expansion effect by the economizer operation is reduced.
  • the economizer gas is injected into the compression chamber 5 in a state where the compression chamber 5 is not closed, the economizer gas flows out of the compression chamber 5 to the suction side and inhibits the suction gas from flowing into the screw groove 5a. To do. Therefore, the economizer port 8a is moved to the position shown in FIG. 5 by moving the slide valve 8 so that the economizer gas is injected into the low-pressure compression chamber 5 as much as possible within a range that does not inhibit the suction gas from flowing into the compression chamber 5. It is trying to be located in. This will be described below.
  • the compression chamber 5 surrounded by a dotted line is in a position where suction of suction gas (suction gas is closed) is completed. Therefore, by placing the economizer port 8a at the position shown in FIG. 5, that is, at the position where the suction gas starts to be communicated when compression of the suction gas is completed (compression start), the suction gas is prevented from flowing into the compression chamber 5. It is possible to inject the economizer gas into the low pressure compression chamber 5 as much as possible.
  • control device 109 performs the economizer operation under conditions where the differential pressure is relatively large even in the partial load operation and the economizer effect is obtained. That is, the control device 109 moves the slide valve 8 to the position shown in FIG. 5 so that the economizer gas flow path 1b, the economizer port 8a, and the compression chamber 5 provided in the casing 1 communicate with each other. To be injected.
  • FIG. 6 is a schematic cross-sectional view showing an economizer port position under low differential pressure operation conditions such as partial load operation of the screw compressor according to Embodiment 1 of the present invention.
  • FIG. 7 is a development view of the inner cylindrical surface of the casing and the screw rotor under low differential pressure operation conditions such as partial load operation of the screw compressor according to Embodiment 1 of the present invention.
  • the control device 109 moves the slide valve 8 having the economizer port 8a to the suction side (right side in FIGS. 6 and 7) as indicated by the white arrows in FIGS. Specifically, the economizer port 8a is moved to an axial position (hereinafter referred to as a second position) that does not communicate with the compression chamber 5 (screw groove 5a).
  • a second position an axial position that does not communicate with the compression chamber 5 (screw groove 5a).
  • the economizer gas flow path 1b provided in the casing 1 and the economizer port 8a do not communicate with each other, and further, the compression chamber 5 and the economizer port 8a do not communicate with each other. That is, the compression chamber 5 and the economizer port 8a do not communicate at all while the economizer operation is stopped.
  • the economizer port 8a moves to an axial position not communicating with the compression chamber 5 (screw groove 5a) and is disconnected from the compression chamber 5 (screw groove 5a). Therefore, when the economizer operation is stopped, the operation is performed in a state where the economizer port 8 a and the economizer gas flow path 1 b are not involved in the compression chamber 5 from the intake stroke to the discharge stroke. Therefore, the economizer port 8a and the economizer gas flow path 1b portion do not become a volume portion (dead volume) that is wastedly compressed. That is, there is no dead volume in the screw compressor 102 of the first embodiment.
  • control device 109 stops the economizer operation under conditions where the differential pressure is relatively small and the economizer effect is small even in full load operation. That is, the control device 109 moves the slide valve 8 to the second position so that the economizer gas flow path 1b, the economizer port 8a, and the compression chamber 5 provided in the casing 1 do not communicate with each other.
  • the slide valve 8 having the economizer port 8a is accommodated in the casing 1 so as to be slidable in the direction of the rotation axis of the screw rotor 3. Then, the slide valve 8 is moved to a first position where the economizer gas flow path 1b, the economizer port 8a and the compression chamber 5 communicate with each other, and a second position where the economizer gas flow path 1b, the economizer port 8a and the compression chamber 5 do not communicate with each other. Configured to be possible.
  • the economizer effect is obtained and the coefficient of performance is improved by performing the economizer operation under the high differential pressure operation condition (the operation condition where the high and low differential pressure of the refrigeration cycle is greater than the predetermined differential pressure).
  • the economizer operation is stopped under low differential pressure operating conditions (operating conditions where the high and low differential pressures of the refrigeration cycle are equal to or lower than the predetermined differential pressure).
  • the coefficient of performance can be improved. That is, according to the first embodiment, it is possible to obtain the screw compressor 102 and the refrigeration cycle apparatus 100 that can realize a high coefficient of performance in a wide operation range.
  • the slide valve 8 is located at the first position and can be moved by moving the slide valve 8 to the “most discharge side” of the movable range.
  • the slide valve 8, the connecting rod 9, and the drive device 10 may be configured such that the slide valve 8 is positioned at the second position by moving the slide valve 8 to the “most suction side” in the range.
  • the economizer port 8a communicates with the economizer gas flow path 1b and the compression chamber 5 in the axial direction.
  • the economizer gas flow path 1b provided in the casing 1 communicates with the compression chamber 5 via the economizer port 8a.
  • the economizer port 8a is moved to the discharge side (left side in FIG. 9) as indicated by the white arrow in FIG. Specifically, the economizer port 8a is moved to an axial position that does not communicate with the compression chamber 5 (screw groove 5a).
  • the position for communicating the compression chamber and the economizer flow path and the position for not communicating with the compression chamber may be configured opposite to the above.
  • FIG. The second embodiment is different from the first embodiment only in the shape of the suction side end surface of the slide valve 8 having the economizer port 8a.
  • FIG. 10 is a developed view of the casing inner cylindrical surface and screw rotor of the screw compressor according to Embodiment 2 of the present invention.
  • the second embodiment differences from the first embodiment will be described, and configurations not described in the second embodiment are the same as those in the first embodiment.
  • the suction side end face 8b of the slide valve 8 having the economizer port 8a has a shape along the inclination of the screw groove 5a.
  • the suction side end face 8b of the slide valve 8 has a shape along the inclination of the screw groove 5a, but in short, it may be formed by an inclined face.
  • the surface necessary for closing the screw groove 5a can be secured by forming the suction side end face 8b of the slide valve 8 along the inclination of the screw groove 5a, a more optimal shape (downsizing) is possible. . Further, by eliminating a surface unnecessary for confinement, the viscous resistance of oil existing between the slide valve 8 and the outer periphery of the screw rotor can be reduced.
  • Embodiment 3 FIG.
  • the first embodiment and the second embodiment have the configuration including the slide valve 8 for changing the position of the economizer port 8a.
  • the third embodiment further includes a slide valve for changing the internal volume ratio.
  • the present invention relates to a screw compressor 102 whose capacity can be controlled.
  • FIG. 11 is a development view of the inner cylindrical surface of the casing and the screw rotor of the screw compressor according to Embodiment 3 of the present invention.
  • the third embodiment differences from the first embodiment will be described, and configurations not described in the third embodiment are the same as those in the first embodiment.
  • a slide valve 11 for changing the internal volume ratio which is a second slide valve, can be moved in the casing 1 in the direction of the rotation axis of the screw rotor 3. It is stored.
  • the slide valve 11 adjusts the discharge start (compression completion) timing of the high-pressure gas compressed in the compression chamber 5 according to the slide position.
  • the discharge-side end face 11a of the slide valve 11 constitutes a part of the discharge port 7, and the discharge timing is adjusted by changing the discharge area of the discharge port 7 according to the slide position, thereby changing the internal volume ratio. That is, if the discharge timing is advanced, the operation becomes a low internal volume ratio, and if the discharge timing is delayed, the operation becomes a high internal volume ratio.
  • the internal volume ratio is a ratio of 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 immediately before the discharge, and when the volume when the suction is completed and the discharge port 7 is opened.
  • the ratio to the volume of In general, screw compressors do not cause improper compression loss under the proper compression ratio operating conditions in which the actual compression ratio matches the internal volume ratio, but when operating at a low compression ratio, compression is performed until the discharge port opens. The compressed gas is over-compressed above the discharge pressure, and extra compression work is performed. On the other hand, when the operation is performed at a high compression ratio, the discharge port opens before reaching the discharge pressure, resulting in an under-compressed state in which the gas flows backward. Therefore, the position of the slide valve 11 is adjusted so that the discharge timing is optimal.
  • the slide valve 8 having the economizer port 8a moves in two stages, such as when it communicates with the economizer gas flow path 1b, the economizer port 8a, and the compression chamber 5, but it does not communicate with it. Since the slide valve 11 can be freely moved, it can be moved in accordance with an appropriate discharge timing.
  • the same effects as those of the first embodiment can be obtained, and the slide valve 11 for changing the internal volume ratio is further provided, so that the discharge timing is appropriate.
  • the slide valve 11 for changing the internal volume ratio is further provided, so that the discharge timing is appropriate.
  • overcompression and undercompression can be suppressed, and the coefficient of performance can be improved. That is, according to the third embodiment, it is possible to obtain the screw compressor 102 and the refrigeration cycle apparatus 100 that can achieve a higher coefficient of performance in a wide operation range.
  • the screw compressor of the present invention may be applied to a twin screw compressor having a pair of male and female screw rotors and forming the compression chamber 5 by meshing them.

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

Abstract

L'invention concerne un compresseur à vis, équipé des éléments suivants : un boîtier (1) ; un rotor à vis (3) disposé de manière à tourner dans le boîtier (1) ; une chambre de compression (5) formée entre le boîtier (1) et le rotor à vis (3) de manière à comprimer du gaz réfrigérant ; une rainure de coulissement (1a) formée dans la surface de cylindre interne du boîtier (1) qui s'étend dans la direction de l'axe de rotation du rotor à vis (3) ; un passage de gaz d'économiseur (1b) formé dans le boîtier (1) de manière à fournir une communication entre l'extérieur du boîtier (1) et la rainure de coulissement (1a) ; un robinet à tiroir (8) prévu dans la rainure de coulissement (1a) de manière à pouvoir coulisser dans la direction de l'axe de rotation du rotor à vis (3) ; et un orifice d'économiseur (8a) formé dans le robinet à tiroir (8) de manière à amener le passage de gaz d'économiseur (1b) en communication avec la chambre de compression (5) conformément à la position du robinet à tiroir (8). Le robinet à tiroir (8) est conçu pour se déplacer dans une première position, dans laquelle le passage de gaz d'économiseur (1b) communique avec la chambre de compression (5) et une seconde position, dans laquelle l'orifice d'économiseur (8a) ne communique pas avec la chambre de compression (5).
PCT/JP2014/075230 2014-09-24 2014-09-24 Compresseur à vis et dispositif à cycle de réfrigération WO2016046907A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2016549696A JP6177449B2 (ja) 2014-09-24 2014-09-24 スクリュー圧縮機および冷凍サイクル装置
PCT/JP2014/075230 WO2016046907A1 (fr) 2014-09-24 2014-09-24 Compresseur à vis et dispositif à cycle de réfrigération
EP14902615.5A EP3199814B1 (fr) 2014-09-24 2014-09-24 Compresseur à vis et dispositif à cycle de réfrigération
CN201480080608.8A CN106605069B (zh) 2014-09-24 2014-09-24 螺杆压缩机以及制冷循环装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2014/075230 WO2016046907A1 (fr) 2014-09-24 2014-09-24 Compresseur à vis et dispositif à cycle de réfrigération

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WO2016046907A1 true WO2016046907A1 (fr) 2016-03-31

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EP (1) EP3199814B1 (fr)
JP (1) JP6177449B2 (fr)
CN (1) CN106605069B (fr)
WO (1) WO2016046907A1 (fr)

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WO2018131089A1 (fr) * 2017-01-11 2018-07-19 三菱電機株式会社 Dispositif à cycle de réfrigération
EP3505765A4 (fr) * 2016-08-23 2019-08-14 Mitsubishi Electric Corporation Compresseur à vis et dispositif à cycle frigorifique

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WO2016084176A1 (fr) * 2014-11-26 2016-06-02 三菱電機株式会社 Compresseur à vis et dispositif à cycle de réfrigération
CN107461222A (zh) * 2017-09-13 2017-12-12 北京工业大学 一种集成滑阀的单螺杆膨胀机
CN107525319B (zh) * 2017-09-18 2020-10-02 特灵空调系统(中国)有限公司 空调控制系统及空调控制方法
CN114729639A (zh) * 2019-11-26 2022-07-08 三菱电机株式会社 螺杆式压缩机
CN114109823B (zh) * 2021-09-28 2022-11-22 上海履正能源科技有限公司 一种螺杆压缩机变频和容调滑阀结合的控制方法
CN114216173B (zh) * 2021-12-16 2023-02-17 珠海格力电器股份有限公司 具有新风输送功能的压缩机、空调器及其控制方法
CN115666026B (zh) * 2022-09-15 2023-09-19 南京晗创智能科技有限公司 一种深基坑监测测点保护装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3505765A4 (fr) * 2016-08-23 2019-08-14 Mitsubishi Electric Corporation Compresseur à vis et dispositif à cycle frigorifique
WO2018131089A1 (fr) * 2017-01-11 2018-07-19 三菱電機株式会社 Dispositif à cycle de réfrigération

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CN106605069A (zh) 2017-04-26
JPWO2016046907A1 (ja) 2017-04-27
EP3199814A4 (fr) 2018-05-09
CN106605069B (zh) 2019-07-12
EP3199814B1 (fr) 2021-01-06
JP6177449B2 (ja) 2017-08-09
EP3199814A1 (fr) 2017-08-02

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