EP3225848A1 - 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
EP3225848A1
EP3225848A1 EP14906847.0A EP14906847A EP3225848A1 EP 3225848 A1 EP3225848 A1 EP 3225848A1 EP 14906847 A EP14906847 A EP 14906847A EP 3225848 A1 EP3225848 A1 EP 3225848A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant liquid
screw compressor
casing
injection port
screw
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP14906847.0A
Other languages
German (de)
English (en)
Other versions
EP3225848A4 (fr
Inventor
Masaaki Kamikawa
Masahiro Kanda
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP3225848A1 publication Critical patent/EP3225848A1/fr
Publication of EP3225848A4 publication Critical patent/EP3225848A4/fr
Withdrawn legal-status Critical Current

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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
    • F04C18/48—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
    • 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
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
    • 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
    • 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

Definitions

  • the present invention relates to a screw compressor and a refrigeration cycle apparatus.
  • a traditional screw compressor includes a screw rotor having one end or a suction end and the other end or discharge end of fluid, and a columnar slidable valve disposed around the screw rotor and slides along the rotational axis of the screw rotor (see, for example, Patent Literature 1).
  • the sliding movement of the slidable valve in the axial direction of the screw rotor shifts the position for start of discharge (completion of compression) of high-pressure gas compressed in a compression chamber. This operation changes the opening timing of a discharge port, thereby varying the internal volume ratio.
  • the internal volume ratio indicates the ratio of the volume of the compression chamber just before a discharging operation to the volume of the compression chamber at the completion of an suction operation (start of compression).
  • the stop position of the slidable valve is controlled to achieve an internal volume ratio providing high compression efficiency, in response to the compression ratio (ratio of the discharge pressure to the intake pressure) depending on the operational loads.
  • the slidable valve is shifted depending on the operational mode, i.e., a full load mode or a partial load mode.
  • the slidable valve is shifted to the suction end in the partial load mode to advance the opening timing of the discharge port, and is shifted to the discharge end in the full load mode to delay the opening timing of the discharge port.
  • refrigerant liquid is injected into a compression chamber through an injection port of the screw compressor to avoid an excess increase in the temperature of discharged gas, thereby optimizing the temperature and degree of superheat of the discharged gas (see, for example, Patent Literature 2).
  • the energy saving performance had been generally represented by the coefficient of performance (ratio of the refrigeration capacity to an electric power consumption) under the rated condition (full load condition: 100% load).
  • indexes approximating the actual operational conditions for example, an integrated part load value (IPLV) standardized in the United States, are recently drawing attentions..
  • IPLV integrated part load value
  • Atypical refrigeration cycle apparatus runs under the rated condition in a very short period of the year.
  • the refrigeration cycle apparatus runs under the partial load mode for 90% or more of the gross annual operation time.
  • the refrigeration cycle apparatus is operated under 75% to 50% of the full load.
  • the full load mode differs from the partial load mode in the flow rate of refrigerant circulation, operational compression ratio, and coefficient of performance.
  • an injecting operation for injecting refrigerant liquid into a compression chamber is effective for lowering the discharge temperature.
  • a small pressure difference such as the partial load (low load) mode
  • the injecting operation is stopped in the small-pressure difference mode.
  • Patent Literature 1 discloses a technique of varying the internal volume ratio with the slidable valve to control the operational capacity, but does not discuss the prevention of an excess increase in the discharge temperature by the injecting operation.
  • the prevention of an excessive increase in the discharge temperature is important, because such an excessive increase in the discharge temperature causes seizure due to disappearance of the gap between a screw rotor of the screw compressor and a casing and deteriorates refrigerating machine oil or refrigerant and thus impairs the reliability of the operation.
  • Patent Literature 2 discusses this respect, the device disclosed in Patent Literature 2 has a problem during the stop of the injecting operation depending on the position of the injection port, as follows: Although the position of the injection port is not clearly described in Patent Literature 2, a typical injection port is disposed in a fixed position in a casing accommodating the screw rotor so as to communicate with the compression chamber. It is presumed that the position of the injection port is generally determined for achieving sufficient effects of the injecting operation. Unfortunately, this injection port functions as a volume part (dead volume) subject to unnecessary compression from low pressure to high pressure during the stop of the injecting operation. That is, during the stop of the injecting operation in the small-pressure difference mode, the injection port causes re-expansion loss while passing over the compression chamber without injection of refrigerant liquid, thereby impairing the performance of the screw compressor.
  • this injection port functions as a volume part (dead volume) subject to unnecessary compression from low pressure to high pressure during the stop of the injecting operation. That is, during the stop of the injecting
  • the present invention is made to address the above problem and an object thereof is to provide a screw compressor and a refrigeration cycle apparatus that have a controllable internal volume ratio and in which the position of an injection port is set to an appropriate position to achieve high coefficient of performance in a wide range of operation, and ensure high reliability and high performance with a low cost structure.
  • a screw compressor includes a casing; a screw rotor disposed to be rotatable in the casing; a compression chamber defined between the casing and the screw rotor, the compression chamber being configured to compress refrigerant gas; a slide groove extending on an inner peripheral surface of the casing along a rotational axis of the screw rotor; a refrigerant liquid passage formed in the casing, the refrigerant liquid passage being configured to communicate between an outside of the casing and the slide groove; and a slidable valve slidable on the slide groove along the rotational axis of the screw rotor, the slidable valve being configured to vary an internal volume ratio, the slidable valve having an injection port configured to allow the refrigerant liquid passage to communicate with the compression chamber depending on a position of the slidable valve, the slidable valve being configured to shift between a first position and a second position, the injection port communicating with the refrigerant liquid passage at the first position, the injection
  • a refrigeration cycle apparatus includes a refrigerant circuit including the above screw compressor, a condenser, an expansion device, and an evaporator connected in sequence with refrigerant pipes; and an injection pipe branching from a portion between the condenser and the expansion device and connected to the refrigerant liquid passage of the screw compressor through an expansion valve.
  • An embodiment of the invention can provide a screw compressor and a refrigeration cycle apparatus that have a controllable discharge timing and include an injection port shifted to an appropriate position to achieve high coefficient of performance in a wide range of operation, and ensure high reliability and high performance with a low cost structure.
  • Fig. 1 illustrates a refrigerant circuit of a refrigeration cycle apparatus including a screw compressor according to Embodiment 1 of the invention.
  • the components having the same reference sign are same as or equivalent to each other throughout the following description.
  • the embodiments of the components disclosed in the entire specification are given for mere illustration and should not be construed to limit the invention.
  • the combinations of the components in the embodiments should not be construed to limit the invention, and the components in one embodiment may be appropriately applied to any other embodiment.
  • High and low pressures are not absolutely determined relative to a fixed reference value, but relatively determined based on the state and operation of the system and device.
  • a refrigeration cycle apparatus 100 is equipped with a refrigerant circuit including a screw compressor 102 driven by an inverter 101, a condenser 103, an expansion valve 105 (that is a pressure-reducing device), and an evaporator 106 which are connected in sequence with refrigerant pipes.
  • the refrigeration cycle apparatus 100 further includes an injection pipe 104 branching from a portion between the condenser 103 and the expansion valve 105 and connected to the screw compressor 102 through an expansion valve 107.
  • the condenser 103 cools and condenses gas discharged from the screw compressor 102.
  • the expansion valve 105 performs throttle expansion to main-stream refrigerant from the condenser 103.
  • the evaporator 106 evaporates the main-stream refrigerant from the expansion valve 105.
  • the screw compressor 102 is provided with a discharge temperature sensor 102a adjacent to the discharge end of the screw compressor 102.
  • the discharge temperature sensor 102a detects the temperature (discharge temperature) of gas discharged from the screw compressor 102.
  • the discharge temperature detected by the discharge temperature sensor 102a is output to a controller 109 (described below).
  • the refrigeration cycle apparatus 100 further includes a controller 109.
  • the controller 109 is composed of, for example, a microcomputer including a CPU, RAM, and ROM, and controls the entire refrigeration cycle apparatus 100 under instructions of a control program stored in the ROM.
  • the controller 109 controls the inverter 101 and the expansion valve 105, shifts the position of a slidable valve 8 (described below) of the screw compressor 102, controls the drive and stop of an injecting operation (injection of refrigerant liquid decompressed in the expansion valve 107 into the screw compressor 102), and varies the amount of refrigerant liquid injected into a compression chamber 5 in the injecting operation.
  • Fig. 2 is a schematic longitudinal-sectional view of the screw compressor according to Embodiment 1 of the invention.
  • the screw compressor 102 includes a tubular casing 1 accommodating a motor 2.
  • the motor 2 is equipped with a stator 2a fixed to the inner surface of the casing 1 and a motor rotor 2b disposed inside the stator 2a.
  • the casing 1 also accommodates a screw rotor 3.
  • the screw rotor 3 and the motor rotor 2b are disposed on the same axis and fixed to a screw shaft 4.
  • the screw rotor 3 has helical screw grooves 5a on the outer peripheral surface, and is coupled to the motor rotor 2b fixed to the screw shaft 4 to be rotated.
  • the screw grooves 5a engage with teeth 6a of gate rotors 6.
  • a space surrounded by the teeth 6a of the gate rotors 6, the screw grooves 5a, and the inner peripheral surface of the casing 1 defines a compression chamber 5.
  • the casing 1 is divided by a partition (not shown) into a low-pressure compartment (adjacent to the suction end) and a high-pressure compartment (adjacent to the discharge end).
  • the high-pressure compartment has a discharge outlet 7 (refer to Fig. 3 described below) in communication with a discharge chamber (not shown).
  • the inner peripheral surface of the casing 1 has a slide groove 1a extending along the rotational axis of the screw rotor 3.
  • the slide groove 1 a accommodates a slidable valve 8 for varying the internal volume ratio, such that the slidable valve 8 can slide on the slide groove 1a.
  • the slidable valve 8 and the casing 1 constitute part of the inner peripheral surface to define the compression chamber 5.
  • the slidable valve 8 has an injection port 8a to vary the internal volume ratio and shift the injection port 8a.
  • the injection port 8a penetrates through the slidable valve 8 from the outer surface sliding on the slide groove 1 a to the inner surface sliding on the screw rotor 3.
  • Fig. 2 illustrates an example of the casing 1 that accommodates a single slidable valve 8 having the injection port 8a.
  • the drive unit 10 for driving the slidable valve 8 is a unit such as those powered by gas pressure or oil pressure, or powered by a motor other than a piston, and the driving method is not limited.
  • the slidable valve 8 constitutes part of the discharge outlet 7.
  • the sliding movement of the slidable valve 8 in the axial direction can change the discharge timing and thus vary the internal volume ratio.
  • the slidable valve 8 shifted adjacent to the suction end allows the discharge outlet 7 to open earlier and thus achieve an advanced discharge timing
  • the slidable valve 8 shifted adjacent to the discharge end allows the discharge outlet 7 to open later and thus achieve a delayed discharge timing.
  • the advanced discharge timing provides an operation of a small internal volume ratio
  • the delayed discharge timing provides an operation of a large internal volume ratio.
  • a screw compressor has a proper compression ratio matching the internal volume ratio.
  • the screw compressor does not cause any loss due to improper compression in an operational mode of the proper compression ratio.
  • the gas In an operational mode of a compression ratio smaller than the proper compression ratio, however, the gas is over-compressed before the opening of an outlet to have a pressure higher than the discharge pressure, resulting in unnecessary compression.
  • the outlet In an operational mode of a compression ratio larger than the proper compression ratio, the outlet opens before achieving the discharge pressure, resulting in insufficient compression that causes reverse flow of gas.
  • the position of the slidable valve 8 is adjusted for optimizing the discharge timing.
  • the casing 1 has a refrigerant liquid passage 1 b for introducing refrigerant liquid separating from the portion between the condenser 103 and the expansion valve 105 into the screw grooves 5a (compression chamber 5).
  • the refrigerant liquid passage 1 b communicates with the compression chamber 5 through the injection port 8a.
  • the refrigerant liquid passage 1b is also connected to the injection pipe 104. In this configuration, the refrigerant liquid flowing out of the condenser 103 separates, and then flows through the injection pipe 104, the refrigerant liquid passage 1 b, and the injection port 8a into the compression chamber 5.
  • Fig. 3 illustrates the principle of compression in the screw compressor according to Embodiment 1 of the invention.
  • Fig. 3(a) illustrates the state of the compression chamber 5 during the intake stroke.
  • the screw rotor 3 is driven by the motor 2 to rotate along the direction of the solid arrow. This rotation reduces the volume of the compression chamber 5, as illustrated in Fig. 3(b) .
  • the injecting operation causes the refrigerant liquid to enter the compression chamber 5 from the injection port 8a during the compression stroke.
  • the refrigerant liquid flowing in the compression chamber 5 is compressed together with suction gas, and is discharged to the outside during the discharge stroke.
  • Fig. 4 is a schematic sectional view illustrating the position of the slidable valve and the position of the injection port of the screw compressor according to Embodiment 1 of the invention in the large-pressure difference mode, such as a 100% load (full load) or 75% load mode.
  • Fig. 5 is a development view of the inner peripheral surface of the casing and the screw rotor of the screw compressor according to Embodiment 1 of the invention in the large-pressure difference mode, such as the 100% load (full load) or 75% load mode.
  • the discharge timing is delayed to increase the internal volume ratio.
  • the controller 109 controls the slidable valve 8 to move toward the discharge end (the left of Fig. 4 or 5 ), as illustrated with the outline arrow of Fig. 4 or 5 to delay the discharge timing.
  • This movement shifts the injection port 8a of the slidable valve 8 to a first position where the injection port 8a communicates with the refrigerant liquid passage 1 b and the compression chamber 5.
  • the injection port 8a at the first position thus brings the refrigerant liquid passage 1 b of the casing 1 into communication with the compression chamber 5 through the injection port 8a.
  • the controller 109 controls the expansion valve 107 to adjust the amount of refrigerant liquid injected into the screw compressor 102, such that the discharge temperature detected by the discharge temperature sensor 102a is maintained constant.
  • the refrigerant liquid having the adjusted volume is injected into the compression chamber 5 through the refrigerant liquid passage 1 b and the injection port 8a. That is, a constant discharge temperature can be achieved by the shift of position of the slidable valve 8 for varying the internal volume ratio appropriately for the large-pressure difference mode and the injection of refrigerant liquid into the screw compressor 102.
  • the refrigerant liquid should preferably be injected before the pressure rise in the compression chamber 5. It is thus preferred that the first position be a position corresponding to the position from which the injection port 8 communicates with the compression chamber 5 at the completion of an suction operation (trapping) of suction gas in the compression chamber 5. In this case, the refrigerant liquid is injected at the beginning of the compression stroke just after the trapping of suction gas. The injecting operation is thus effectively conducted without outflow of main-stream refrigerant to the low-pressure compartment or inhibition of the suction operation of suction gas.
  • a small-pressure difference mode such as a partial load mode (e.g., 50% or 25% load mode).
  • Fig. 6 is a schematic sectional view illustrating the position of the injection port of the screw compressor according to Embodiment 1 of the invention in the small-pressure difference mode, such as a partial load mode (e.g., 50% or 25% load mode).
  • Fig. 7 is a development view of the inner peripheral surface of the casing and the screw rotor of the screw compressor according to Embodiment 1 of the invention in the small-pressure difference mode, such as the partial load mode.
  • the controller 109 controls the slidable valve 8 to move toward the suction end (the right of Fig. 6 or 7 ), as illustrated with the outline arrow of Fig. 6 or 7 .
  • the slidable valve 8 is moved to a proper position for varying the internal volume ratio or the discharge timing appropriately for the small-pressure difference mode.
  • the mode does not require injection of refrigerant liquid for lowering the discharge temperature, as described above.
  • the injecting operation is thus not conducted.
  • This mode requires a configuration for preventing the refrigerant liquid passage 1 b from functioning as a volume part (dead volume) subject to unnecessary compression.
  • the injection port 8a is shifted to a position (hereinafter referred to as "second position") in the axial direction closer to the suction end than the first position is during the stop of the injecting operation according to Embodiment 1, as described in detail below.
  • the injection port 8a at the second position does not communicate with the refrigerant liquid passage 1 b.
  • the slidable valve 8 has two required functions in the small-pressure difference mode: the adjustment of the internal volume ratio and the shift of the injection port 8a to the second position.
  • the movement of the slidable valve 8 to vary the internal volume ratio can shift the injection port 8a to the second position.
  • the injection port 8a is shifted to the position in the axial direction so as not to communicate with the refrigerant liquid passage 1 b of the casing 1, in other words, so as to be separated from the refrigerant liquid passage 1 b in the small-pressure difference mode. Accordingly, the refrigerant liquid passage 1 b does not affect the compression chamber 5 from the intake stroke to the discharge stroke in the small-pressure difference mode.
  • This configuration prevents the portion upstream of the refrigerant liquid passage 1 b from being a dead volume. Accordingly, the screw compressor 102 according to Embodiment 1 has a smaller dead volume than those of traditional screw compressors.
  • the injection port 8a positioned at the second position does not communicate with the refrigerant liquid passage 1 b but communicates with the compression chamber 5. It is preferred that the injection port 8a at the second position does not communicate with the compression chamber 5 to reduce the dead volume and re-expansion loss.
  • the injection port 8a positioned at the second position communicates with the compression chamber 5 due to the moving stroke of the slidable valve 8 and the opening timing of the discharge outlet 7 in response to the movement of the slidable valve 8.
  • the injection port 8a at the second position should preferably be not communicating with the compression chamber 5 if possible. It should be noted that the configuration including the injection port 8a in communication with the compression chamber 5 can also reduce the re-expansion loss during the stop of the injecting operation because the second position is closer to the suction end than the first position is, as described in detail below.
  • Fig. 8 illustrates a difference in timing of opening to the compression chamber in the screw compressor according to Embodiment 1 of the invention between the case of the injection port at the first position and the case of the injection port at the second position.
  • Fig. 8 also illustrates the relationship between the rotational angle of the screw and the pressure in the compression chamber 5 (the internal pressure of the screw grooves 5a) in the individual cases of the first position and the second position.
  • the timing of opening of the injection port 8a at the second position to the compression chamber 5 is earlier than that of the injection port 8a at the first position.
  • the internal space of the injection port 8a is compressed within a small range of rotational angle of the screw. Accordingly, the injection port 8a at the second position can reduce the re-expansion loss in the partial load mode.
  • the slidable valve 8 has two functions: the adjustment of the internal volume ratio and the shift of the injection port 8a.
  • the movement of the slidable valve 8 can shift the injection port 8a between the first position and the second position, thereby switching the mode of the refrigerant liquid passage 1 b in communication with the compression chamber 5 through the injection port 8a to the mode of the refrigerant liquid passage 1 b not communicating with the compression chamber 5, and vice versa, depending on the operational condition.
  • the injecting operation is conducted in a mode where the discharge temperature readily increases, such as a large-pressure difference mode (involving a pressure difference in the refrigeration cycle larger than a predetermined pressure difference or a predetermined compression ratio).
  • a large-pressure difference mode involving a pressure difference in the refrigeration cycle larger than a predetermined pressure difference or a predetermined compression ratio.
  • the refrigerant liquid passage 1 b is separated from the compression chamber 5 in a mode where the discharge temperature does not readily increase, such as a small-pressure difference mode (involving a pressure difference in the refrigeration cycle equal to or smaller than the predetermined pressure difference or the predetermined compression ratio).
  • the refrigerant liquid passage 1 b thus has no dead volume. This configuration can reduce the pressure increase in the injection port 8a and can thus reduce the re-expansion loss and achieve high coefficient of performance.
  • the injection port 8a is provided to the slidable valve 8 for varying the internal volume ratio and is controlled to be at an appropriate position.
  • the screw compressor 102 and the refrigeration cycle apparatus 100 are provided that can thereby achieve high coefficient of performance in a wide range of operation and the screw compressor can have a low cost structure with high reliability.
  • Embodiment 2 differs from Embodiment 1 in the connection of pipes in the refrigeration cycle apparatus 100.
  • Fig. 9 illustrates a refrigerant circuit of a refrigeration cycle apparatus including a screw compressor according to Embodiment 2 of the invention.
  • Embodiment 2 will focus on the difference from Embodiment 1.
  • the components not described in Embodiment 2 are same as to those in Embodiment 1.
  • the device according to Embodiment 2 further includes a refrigerant liquid pipe 108 branching from a portion between the condenser 103 and the expansion valve 105 and connected to a portion between the evaporator 106 and the screw compressor 102, in addition to the configuration of Embodiment 1.
  • the refrigerant liquid pipe 108 is provided with a solenoid valve and/or an expansion mechanism (e.g., a fixed throttle or expansion valve) 110 in the intermediate part.
  • the illustrated configuration includes the expansion mechanism 110 alone.
  • the expansion mechanism 110 is open only while the injection port 8a resides at the second position, and varies the volume of injection based on the discharge temperature detected by the discharge temperature sensor 102a.
  • the refrigeration cycle apparatus has a low discharge temperature and does not require the injection of refrigerant liquid in the small-pressure difference mode, and thus does not conduct the injecting operation, as described above.
  • the slidable valve 8 is moved to shift the injection port 8a to the second position in the small-pressure difference mode, as in Embodiment 1.
  • This configuration has a decreased dead volume and a decreased range of rotational angle of the screw (X in Fig. 8 ) overlapping with the compression stroke. The configuration can thus reduce the re-expansion loss.
  • a transitional operation, activating operation, or pull-down operation may however cause a high temperature (intake temperature) and a high degree of superheat of intake refrigerant.
  • a high intake temperature may also raise the temperature of the discharged gas.
  • the controller 109 according to Embodiment 2 opens the expansion mechanism 110 to inject refrigerant liquid from the refrigerant liquid pipe 108 into the compression chamber 5, in response to an increase in discharge temperature above a reference temperature and the requirement for injection of refrigerant liquid.
  • this configuration can lower the discharge temperature through the injection of the refrigerant liquid into the portion between the evaporator 106 and the screw compressor 102, in contrast to Embodiment 1.
  • the configuration can thus ensure high reliability of the screw compressor 102.
  • the expansion mechanism 110 provided to the refrigerant liquid pipe 108 may also be controlled based on the temperature or degree of superheat of intake refrigerant.
  • Embodiment 2 can bring about effects equivalent to those of Embodiment 1, and ensure high reliability of the screw compressor 102 regardless of a sudden change in operation, such as an increase in temperature of suction gas, in the small-pressure difference mode.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP14906847.0A 2014-11-26 2014-11-26 Compresseur à vis et dispositif à cycle de réfrigération Withdrawn EP3225848A4 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2014/081284 WO2016084176A1 (fr) 2014-11-26 2014-11-26 Compresseur à vis et dispositif à cycle de réfrigération

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EP3225848A1 true EP3225848A1 (fr) 2017-10-04
EP3225848A4 EP3225848A4 (fr) 2018-10-17

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JP (1) JP6234611B2 (fr)
WO (1) WO2016084176A1 (fr)

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WO2018037469A1 (fr) * 2016-08-23 2018-03-01 三菱電機株式会社 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
WO2022044149A1 (fr) * 2020-08-26 2022-03-03 三菱電機株式会社 Dispositif à cycle frigorifique
CN114857793B (zh) * 2022-05-20 2023-03-31 珠海格力电器股份有限公司 一种冷凝机组及其喷液控制方法、控制装置和空调器

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EP3225848A4 (fr) 2018-10-17
JPWO2016084176A1 (ja) 2017-04-27
WO2016084176A1 (fr) 2016-06-02

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