EP3199814A1 - Compresseur à vis et dispositif à cycle de réfrigération - Google Patents

Compresseur à vis et dispositif à cycle de réfrigération Download PDF

Info

Publication number
EP3199814A1
EP3199814A1 EP14902615.5A EP14902615A EP3199814A1 EP 3199814 A1 EP3199814 A1 EP 3199814A1 EP 14902615 A EP14902615 A EP 14902615A EP 3199814 A1 EP3199814 A1 EP 3199814A1
Authority
EP
European Patent Office
Prior art keywords
economizer
compression chamber
casing
screw
screw compressor
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.)
Granted
Application number
EP14902615.5A
Other languages
German (de)
English (en)
Other versions
EP3199814A4 (fr
EP3199814B1 (fr
Inventor
Masaaki Kamikawa
Mihoko Shimoji
Toshihide Kouda
Hideaki Nagata
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 EP3199814A1 publication Critical patent/EP3199814A1/fr
Publication of EP3199814A4 publication Critical patent/EP3199814A4/fr
Application granted granted Critical
Publication of EP3199814B1 publication Critical patent/EP3199814B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F04C29/0007—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.
  • Some traditional refrigeration cycle apparatuses are equipped with an intermediate cooler in the refrigeration cycle in order to increase the refrigeration capacity and improve the performance or coefficient of performance (ratio of the refrigeration capacity to an input to a compressor) of the refrigeration cycle (see, for example, Patent Literature 1).
  • the refrigeration cycle apparatus After cooling main-stream liquid in the intermediate cooler with refrigerant gas, the refrigeration cycle apparatus performs economizing operation to introduce the refrigerant gas (hereinafter referred to as "economizer gas”) into an intermediate part of the compressor.
  • the intermediate cooler is disposed between a condenser and an evaporator in the refrigeration cycle.
  • the refrigeration cycle apparatus further includes an economizer pipe branching from an intermediate portion of the passage from the condenser to the evaporator, an expansion valve for intermediate cooling disposed on the economizer pipe, and a screw compressor having an economizer port connected to the economizer pipe.
  • Some traditional screw compressors include a screw rotor and a casing accommodating the screw rotor.
  • the casing has an economizer port for injecting refrigerant into a compression chamber defined between the screw rotor and the inner surface of the casing (see, for example, Patent Literature 2).
  • the energy saving performance was generally represented by the coefficient of performance (ratio of the refrigeration capacity to an electric power consumption) under the rated condition (full load mode: 100% load).
  • indexes based on approximately the actual operational conditions, for example, an integrated part load value (IPLV) standardized in the United States.
  • IPLV integrated part load value
  • a typical refrigeration cycle apparatus runs under the rated condition in a very short period of the year.
  • more than 90% of the annual operation is operated in a partial load mode.
  • Most of the partial load mode 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. These circumstances of the actual operation draw attention on the IPLV.
  • the IPLV is an index based on the coefficient of performance in the partial load mode.
  • the full load mode has a large pressure difference in the refrigeration cycle, which indicates high capacity operation, whereas the partial load mode has a small pressure difference in the refrigeration cycle, which indicates low capacity operation.
  • the economizing operation is effective to increase the coefficient of performance.
  • the economizing operation becomes less effective. Under some conditions in the partial load mode, the economizing operation is less effective for an increase in the refrigeration capacity and adversely increases the electric power consumption, resulting in a decrease in the coefficient of performance.
  • the economizing operation can be switched between the drive and halt depending on operational conditions, such as the full load mode and the partial load mode.
  • An object of the invention which has been accomplished to overcome the above problems, is to provide a screw compressor and a refrigeration cycle apparatus that include an economizer port in a better position and can achieve high coefficient of performance and high refrigeration capacity in a wide range of operation.
  • a screw compressor of the invention includes
  • a refrigeration cycle apparatus of the invention includes a refrigerant circuit including the screw compressor, a condenser, a high-pressure unit of an intermediate cooler, an expansion device, and an evaporator connected in sequence with a refrigerant pipe; and an economizer pipe branching from a portion between the intermediate cooler and the expansion device and connected to the economizer gas passage of the screw compressor through an expansion valve for the intermediate cooler and a low-pressure unit of the intermediate cooler.
  • the invention can provide a screw compressor and a refrigeration cycle apparatus that include an economizer port in an optimized position and can achieve high coefficient of performance and high refrigeration capacity in a wide range of operation.
  • Fig. 1 illustrates a refrigerant circuit of a refrigeration cycle apparatus including a screw compressor according to Embodiment 1 of the invention.
  • the components referred to by 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 another embodiment.
  • High and low pressures are not absolutely determined relative to a fixed reference value, but relatively determined based on states and operations of the system and the apparatus, etc.
  • a refrigeration cycle apparatus 100 is equipped with a refrigerant circuit including a screw compressor 102 driven by an inverter 101, a condenser 103, a high-pressure unit of an intermediate cooler 104, an expansion valve 105 (expansion device), and an evaporator 106, which are connected in sequence with a refrigerant pipe.
  • the refrigeration cycle apparatus 100 further includes an economizer pipe 108, which branches from a portion between the intermediate cooler 104 and the expansion valve 105 and is connected to the screw compressor 102 through an intermediate-cooler expansion valve 107 (expansion valve for the intermediate cooler) and a low-pressure unit of the intermediate cooler 104.
  • the condenser 103 cools and condenses gas discharged from the screw compressor 102.
  • the expansion valve 105 performs throttle expansion to main-stream refrigerant flowing out from the intermediate cooler 104.
  • the evaporator 106 evaporates the main-stream refrigerant from the expansion valve 105.
  • the intermediate cooler 104 has the high-pressure unit and the low-pressure unit, as described above. High-pressure refrigerant (main-stream refrigerant between the condenser 103 and the expansion valve 105) passes through the high-pressure unit, whereas intermediate-pressure refrigerant (the pressure of part of the high-pressure refrigerant is reduced by the intermediate-cooler expansion valve 107 to an intermediate pressure within the whole pressure range in the refrigeration cycle) passes through the low-pressure unit.
  • the intermediate cooler 104 then causes heat exchange between the high-pressure refrigerant and the intermediate-pressure refrigerant to cool the high-pressure refrigerant.
  • the refrigeration cycle apparatus 100 further includes a controller 109.
  • the controller 109 controls the inverter 101, the expansion valve 105, and the intermediate-cooler expansion valve 107, controls the position of at least one slidable valve (described below) of the screw compressor 102, and controls the drive and halt of economizing operation for injecting economizer gas into a compression chamber.
  • 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 an outlet 7 ( 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 direction of the rotational axis of the screw rotor 3.
  • the slide groove 1a slidably accommodates a slidable valve 8 (first slidable valve).
  • the slidable valve 8 constitutes part of the inner peripheral surface with the casing 1 to define the compression chamber 5.
  • the slidable valve 8 has an economizer port 8a.
  • the economizer port 8a penetrates the slidable valve 8 from its outer surface to slide on the slide groove 1a to its inner surface to slide on the screw rotor 3.
  • Fig. 2 illustrates an example of the casing 1 that accommodates a single slidable valve 8 having the economizer port 8a.
  • the casing 1 has an economizer gas passage 1b for introducing refrigerant gas from the intermediate cooler 104 into the compression chamber 5 (the screw grooves 5a during a compression stroke).
  • the economizer gas passage 1b communicates with the compression chamber 5 through the economizer port 8a.
  • the economizer gas passage 1b is also connected to the economizer pipe 108.
  • the refrigerant gas from the intermediate cooler 104 separates from the main stream to cool the main-stream liquid, and then flows into the compression chamber 5 through the economizer pipe 108, the economizer gas passage 1b, and the economizer port 8a.
  • the economizer gas passage 1b of the casing 1 may have a space (not shown) for reducing the pulsation of flowing gas and communicate with the compression chamber 5 through the space, for example.
  • the slidable valve 8 is coupled to a drive unit 10 including a piston or the like, with a coupling rod 9, and is driven by the drive unit 10 to slide in the slide groove 1a along the direction of the rotational axis of the screw rotor 3.
  • the drive unit 10 for driving the slidable valve 8 a unit such as those powered by gas pressure or oil pressure, or powered by a motor other than a piston, that is, the driving method is not limited.
  • the screw compressor 102 sucks refrigerant gas flowing from the evaporator 106, and compresses and discharges the refrigerant gas.
  • the discharged refrigerant gas is cooled in the condenser 103.
  • the refrigerant cooled in the condenser 103 flows into the intermediate cooler 104.
  • the intermediate cooler 104 causes heat exchange between high-pressure refrigerant, which flows from the condenser 103 into the high-pressure unit, and intermediate-pressure refrigerant, which branches off after passing through the intermediate cooler 104, undergoes decompression in the intermediate-cooler expansion valve 107, and then enters the low-pressure unit.
  • the high-pressure refrigerant that flows directly from the condenser 103 into the high-pressure unit of the intermediate cooler 104 is subcooled by the heat exchange with the intermediate-pressure refrigerant.
  • the addition of subcooling degree enhances the refrigerating effects of the evaporator 106.
  • the intermediate-pressure refrigerant entering the low-pressure unit of the intermediate cooler 104 cools the high-pressure refrigerant in the high-pressure unit, flows through the economizer pipe 108 and the economizer gas passage 1b, and is injected from the economizer port 8a of the slidable valve 8 into the compression chamber 5.
  • the difference of the high-pressure side pressure and the intermediate pressure of the economizer gas as the high-pressure side from the pressure in the compression chamber 5 causes the economizer gas to be injected from the economizer port 8a into the compression chamber 5.
  • the injected economizer gas is mixed with compressed gas.
  • the pressure difference is small between the exit of the intermediate cooler and the compression chamber 5.
  • Such a small pressure difference prevents the economizer gas from readily entering the compression chamber 5.
  • the small pressure difference thus destabilizes the economizing operation.
  • the small pressure difference impairs the effects of the increased refrigeration capacity and adversely increases the electric power consumption due to the injection of the economizer gas during compression, resulting in a decrease in the coefficient of performance.
  • the intermediate-cooler expansion valve 107 is closed to halt the economizing operation under a small-pressure-difference condition.
  • Fig. 3 illustrates the principle of compression in the screw compressor according to Embodiment 1.
  • Fig. 3(a) illustrates a 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 economizer gas in the economizing operation enters the compression chamber 5 from the economizer port 8a during the compression stroke.
  • the economizer gas in the compression chamber 5 is compressed together with sucked gas, and is discharged to the outside during the discharge stroke.
  • Fig. 4 is a schematic sectional view illustrating the position of the economizer port of the screw compressor according to Embodiment 1 of the invention under a large-pressure-difference condition, such as the full 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 under a large-pressure-difference condition, such as the full load mode.
  • the controller 109 controls the slidable valve 8 having the economizer port 8a to move toward the discharge end (the left of Fig. 4 or 5 ), as illustrated with the outline arrow of Fig. 4 or 5 , such that the economizer port 8a is disposed in a position (first position) so as to communicate with the economizer gas passage 1b and the compression chamber 5.
  • the economizer gas passage 1b of the casing 1 thus communicates with the compression chamber 5 through the economizer port 8a.
  • the economizer gas While the compression chamber 5 is being in communication with the economizer port 8a in the compression stroke, the economizer gas is injected through the economizer gas passage 1b and the economizer port 8a into the compression chamber 5.
  • the pressure (intermediate pressure) in the economizer port 8a in communication with the compression chamber 5 increases, the effects of increasing the refrigeration capacity by the economizing operation decrease.
  • the economizer gas which is injected into the compression chamber 5 before completion of closing of the compression chamber 5, flows from the compression chamber 5 toward the suction end and inhibits sucked gas from entering the screw grooves 5a.
  • the slidable valve 8 is moved for shifting the economizer port 8a to the position illustrated in Fig. 5 , so that the economizer gas is injected into the compression chamber 5 at a low pressure as much as possible without inhibiting the sucked gas from entering the compression chamber 5. The details will be explained below.
  • the economizer port 8a is disposed in the position illustrated in Fig. 5 , i.e., the position from which the economizer port 81a is open to communication with the compression chamber 5 upon the completion of trapping of the sucked gas (upon the start of compression).
  • the economizer gas can thus be injected into the compression chamber 5 at a low pressure as much as possible without inhibiting the sucked gas from entering the compression chamber 5.
  • the controller 109 Even in the partial load mode, the controller 109 also performs the economizing operation if the pressure difference is relatively large to ensure the economization.
  • the controller 109 controls the slidable valve 8 to move to the position illustrated in Fig. 5 such that the economizer gas passage 1b of the casing 1, the economizer port 8a, and the compression chamber 5 communicate with each other. The economizer gas is thus injected into the compression chamber 5.
  • Fig. 6 is a schematic sectional view illustrating the position of the economizer port of the screw compressor according to Embodiment 1 of the invention under a small-pressure-difference condition, such as the partial 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 under a small-pressure-difference condition, such as the partial load mode.
  • the controller 109 controls the slidable valve 8 having the economizer port 8a 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 economizer port 8a is shifted to a position (hereinafter referred to as "second position") along the axis direction so as not to communicate with the compression chamber 5 (screw grooves 5a).
  • the economizer port 8a thus does not communicate with the economizer gas passage 1b of the casing 1 or the compression chamber 5.
  • the economizer port 8a is completely separated from the compression chamber 5 during the halt of the economizing operation.
  • the economizer port 8a is shifted to the position along the axis direction so as not to communicate with the compression chamber 5 (screw grooves 5a), in other words, so as to be separated from the compression chamber 5 (screw grooves 5a) during the halt of the economizing operation. Accordingly, the economizer port 8a and the economizer gas passage 1b do not affect the compression chamber 5 from the intake stroke to the discharge stroke during the halt of the economizing operation.
  • This configuration prevents the economizer port 8a and the economizer gas passage 1b from being a volume part (dead volume) that is subject to useless compression. That is, the screw compressor 102 according to Embodiment 1 has no dead volume.
  • the controller 109 halts the economizing operation under the condition of a relatively small pressure difference not causing effective economization.
  • the controller 109 controls the slidable valve 8 to move to the second position such that the economizer gas passage 1b of the casing 1, the economizer port 8a, and the compression chamber 5 do not communicate with each other.
  • the slidable valve 8 having the economizer port 8a is accommodated in the casing 1 so as to be slidable along the direction of the rotational axis of the screw rotor 3 according to Embodiment 1.
  • the slidable valve 8 can move between the first position, which allows the economizer gas passage 1b, the economizer port 8a, and the compression chamber 5 to communicate with each other, and the second position, which prevents the economizer gas passage 1b, the economizer port 8a, and the compression chamber 5 from communicating with each other.
  • Embodiment 1 can provide the screw compressor 102 and the refrigeration cycle apparatus 100 that can achieve a high coefficient of performance in a wide range of operation.
  • the slidable valve 8 may have any range of movement.
  • the slidable valve 8, the coupling rod 9, and the drive unit 10 may be disposed, such that the first position of the slidable valve 8 is "most adjacent to the discharge end" in the range of movement of the slidable valve 8 whereas the second position of the slidable valve 8 is "most adjacent to the suction end" in the range of movement of the slidable valve 8.
  • the economizer port 8a is shifted toward the suction end (the right of Fig. 8 ) during performing the economizing operation, as illustrated with the outline arrow of Fig. 8 .
  • the economizer port 8a is disposed in the position along the axis direction so as to communicate with the economizer gas passage 1 b and the compression chamber 5.
  • the economizer gas passage 1b of the casing 1 thus communicates with the compression chamber 5 through the economizer port 8a.
  • the economizer port 8a is shifted toward the discharge end (the left of Fig. 9 ) during the halt of the economizing operation, as illustrated with the outline arrow of Fig. 9 .
  • the economizer port 8a is disposed in the position along the axis direction so as not to communicate with the compression chamber 5 (screw grooves 5a).
  • the position to communicate the economizer passage with the compression chamber and the position not to communicate may be interchangeable.
  • Embodiment 2 differs from Embodiment 1 only in the shape of the suction end surface of the slidable valve 8 having the economizer port 8a.
  • Fig. 10 is a development view of the inner peripheral surface of the casing and the screw rotor of the screw compressor according to Embodiment 2 of the invention.
  • the following explanation of Embodiment 2 focuses on the difference from Embodiment 1.
  • the components not described in Embodiment 2 are identical to those in Embodiment 1.
  • the slidable valve 8 having the economizer port 8a has a suction end surface 8b, which extends along the slope of each of the screw grooves 5a.
  • This shape of the suction end surface 8b in comparison to a suction end surface 8b of the slidable valve 8 perpendicular to the screw shaft 4 in Embodiment 1, can bring about the following advantageous effects: the configuration does not require an extra space for movement of the slidable valve 8 and can thus achieve a reduction in size of the components in addition to the effects comparable to those in Embodiment 1.
  • the suction end surface 8b of the slidable valve 8 extends along the slope of the screw groove 5a in this embodiment, the suction end surface 8b may be any inclined surface.
  • suction end surface 8b of the slidable valve 8 extending along the slope of the screw groove 5a can ensure to have necessary surface for closing the screw groove 5a, leading to further optimization of the shape (a reduction in size).
  • a reduction in the surfaces of the slidable valve 8 useless for the closing can decrease the viscous resistance of the oil between the slidable valve 8 and the outer surface of the screw rotor.
  • a volume-controllable screw compressor 102 according to Embodiment 3 further includes a slidable valve for varying the internal volume ratio.
  • Fig. 11 is a development view of the inner peripheral surface of the casing and the screw rotor of the screw compressor according to Embodiment 3 of the invention.
  • the following explanation of Embodiment 3 focuses on the differences from Embodiment 1.
  • the components not described in Embodiment 3 are identical to those in Embodiment 1.
  • the casing 1 further accommodates a slidable valve 11 (second slidable valve) for varying the internal volume ratio, in addition to the slidable valve 8, such that the slidable valve 11 is slidable along the direction of the rotational axis of the screw rotor 3.
  • the slidable valve 11 adjusts the timing to start discharge of high-pressure gas compressed in the compression chamber 5 (the timing of completion of compression) depending on the slide position of the slidable valve 11.
  • the slidable valve 11 has a discharge end surface 11a constituting part of the outlet 7. A change in the discharging area of the outlet 7 depending on the slide position varies the discharge timing and the internal volume ratio. In specific, advanced discharge timing provides an operation with a small internal volume ratio, whereas delayed discharge timing provides an operation with a large internal volume ratio.
  • the internal volume ratio indicates the ratio of the volume of the compression chamber 5 just before the discharge to the volume of the compression chamber 5 upon the completion of an intake operation (start of compression), i.e., the ratio of the volume upon the opening of the outlet 7 to the volume upon the completion of the intake operation.
  • start of compression i.e., the ratio of the volume upon the opening of the outlet 7 to the volume upon the completion of the intake operation.
  • a screw compressor does not cause loss due to improper compression under an operational condition of a proper compression ratio, i.e., in the case of the actual compression ratio matching the internal volume ratio.
  • the gas is over-compressed before the opening of an outlet to have a pressure higher than the discharge pressure, resulting in excess compression.
  • the outlet opens before achieving the discharge pressure, resulting in insufficient compression that causes reverse flow of gas.
  • the position of the slidable valve 11 is adjusted for optimizing the discharge timing.
  • the slidable valve 8 having the economizer port 8a moves between two positions, i.e., the position allowing for communication and the position preventing the communication between the economizer gas passage 1b, the economizer port 8a, and the compression chamber 5.
  • the slidable valve 11 for varying the internal volume ratio can freely move in accordance with any proper discharge timing.
  • Embodiment 3 further includes the slidable valve 11 for varying the internal volume ratio that can move to a position for optimizing the discharge timing.
  • the configuration can thus prevent over-compression and insufficient compression and increase the coefficient of performance in addition to bringing about the effects comparable to those in Embodiment 1. That is, Embodiment 3 can provide the screw compressor 102 and the refrigeration cycle apparatus 100 that can achieve a higher coefficient of performance in a wide range of operation.
  • the screw compressor according to an embodiment of the invention may be replaced with a twin-screw compressor including male and female screw rotors that engage with each other to define a compression chamber 5, other than a single-screw compressor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP14902615.5A 2014-09-24 2014-09-24 Compresseur à vis et dispositif à cycle de réfrigération Active EP3199814B1 (fr)

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

Publications (3)

Publication Number Publication Date
EP3199814A1 true EP3199814A1 (fr) 2017-08-02
EP3199814A4 EP3199814A4 (fr) 2018-05-09
EP3199814B1 EP3199814B1 (fr) 2021-01-06

Family

ID=55580469

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14902615.5A Active EP3199814B1 (fr) 2014-09-24 2014-09-24 Compresseur à vis et dispositif à cycle de réfrigération

Country Status (4)

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

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107525319A (zh) * 2017-09-18 2017-12-29 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
EP3225848A4 (fr) * 2014-11-26 2018-10-17 Mitsubishi Electric Corporation Compresseur à vis et dispositif à cycle de réfrigération
EP3505765A4 (fr) * 2016-08-23 2019-08-14 Mitsubishi Electric Corporation Compresseur à vis et dispositif à cycle frigorifique

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018131089A1 (fr) * 2017-01-11 2018-07-19 三菱電機株式会社 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
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

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6035169U (ja) * 1983-08-17 1985-03-11 株式会社神戸製鋼所 スクリュ冷凍圧縮機
JPH0820137B2 (ja) * 1990-09-26 1996-03-04 ダイキン工業株式会社 スクリュー冷凍装置
JPH05106572A (ja) * 1991-10-17 1993-04-27 Daikin Ind Ltd 一軸形スクリユー圧縮機
JP4183021B1 (ja) * 2007-06-11 2008-11-19 ダイキン工業株式会社 圧縮機および冷凍装置
CN103486038B (zh) * 2012-06-12 2016-07-06 珠海格力电器股份有限公司 滑阀、滑阀调节机构及具有该滑阀调节机构的螺杆压缩机
CN202628525U (zh) * 2012-07-02 2012-12-26 珠海格力电器股份有限公司 螺杆压缩机用滑阀及包括该滑阀的螺杆压缩机
CN103527485A (zh) * 2012-07-02 2014-01-22 珠海格力电器股份有限公司 螺杆压缩机用滑阀及包括该滑阀的螺杆压缩机
CN102909580B (zh) * 2012-08-23 2015-04-01 联德机械（杭州）有限公司 一种双螺杆压缩机的滑阀工装及滑阀加工方法
CN105247217B (zh) * 2013-05-30 2017-03-15 三菱电机株式会社 螺杆压缩机和冷冻循环装置

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3225848A4 (fr) * 2014-11-26 2018-10-17 Mitsubishi Electric Corporation Compresseur à vis et dispositif à cycle de réfrigération
EP3505765A4 (fr) * 2016-08-23 2019-08-14 Mitsubishi Electric Corporation Compresseur à vis et dispositif à cycle frigorifique
CN107525319A (zh) * 2017-09-18 2017-12-29 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

Also Published As

Publication number Publication date
CN106605069A (zh) 2017-04-26
JPWO2016046907A1 (ja) 2017-04-27
EP3199814A4 (fr) 2018-05-09
WO2016046907A1 (fr) 2016-03-31
CN106605069B (zh) 2019-07-12
EP3199814B1 (fr) 2021-01-06
JP6177449B2 (ja) 2017-08-09

Similar Documents

Publication Publication Date Title
EP3199814B1 (fr) Compresseur à vis et dispositif à cycle de réfrigération
US7722346B2 (en) Oil supply method of two-stage screw compressor, two-stage screw compressor applying the method, and method of operating refrigerating machine having the compressor
EP3136020A1 (fr) Système de réfrigération par compression à deux étages
EP3425202B1 (fr) Compresseur à vis et dispositif à cycle de réfrigération
JP6058133B2 (ja) スクリュー圧縮機及び冷凍サイクル装置
JP2006258397A (ja) 冷凍装置
CN109154455B (zh) 制冷循环装置
CA2885727C (fr) Appareil et procede pour ameliorer le rendement de compresseur
TWI626380B (zh) 螺桿壓縮機以及具有螺桿壓縮機之冷凍循環裝置
EP3225848A1 (fr) Compresseur à vis et dispositif à cycle de réfrigération
JP5951125B2 (ja) スクリュー圧縮機及び冷凍サイクル装置
JP6177450B2 (ja) スクリュー圧縮機および冷凍サイクル装置
WO2017094057A1 (fr) Compresseur à vis unique et dispositif à cycle de réfrigération
KR101330332B1 (ko) 2단 스크류 압축식 냉동 장치
EP3505765B1 (fr) Compresseur à vis et dispositif à cycle frigorifique
CN221347264U (zh) 螺杆压缩机以及制冷装置
KR101248437B1 (ko) 용적식 압축기
EP3252310B1 (fr) Compresseur à vis
JP2014029158A (ja) 冷凍装置

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20170110

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAX Request for extension of the european patent (deleted)
A4 Supplementary search report drawn up and despatched

Effective date: 20180411

RIC1 Information provided on ipc code assigned before grant

Ipc: F04C 29/00 20060101ALI20180405BHEP

Ipc: F25B 1/047 20060101ALI20180405BHEP

Ipc: F04C 18/52 20060101ALI20180405BHEP

Ipc: F04C 18/16 20060101ALI20180405BHEP

Ipc: F04C 29/04 20060101AFI20180405BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20200729

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1352662

Country of ref document: AT

Kind code of ref document: T

Effective date: 20210115

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602014074128

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20210106

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1352662

Country of ref document: AT

Kind code of ref document: T

Effective date: 20210106

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210407

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210506

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210406

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210406

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210506

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602014074128

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

26N No opposition filed

Effective date: 20211007

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20210930

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20210924

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210506

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210924

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210924

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210924

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210930

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210930

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20140924

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230512

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210206

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

REG Reference to a national code

Ref country code: DE

Ref legal event code: R084

Ref document number: 602014074128

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210106

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20240730

Year of fee payment: 11