EP3425202B1 - 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
EP3425202B1
EP3425202B1 EP16892504.8A EP16892504A EP3425202B1 EP 3425202 B1 EP3425202 B1 EP 3425202B1 EP 16892504 A EP16892504 A EP 16892504A EP 3425202 B1 EP3425202 B1 EP 3425202B1
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EP
European Patent Office
Prior art keywords
screw
compression chamber
economizer
screw compressor
slide valve
Prior art date
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EP16892504.8A
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German (de)
English (en)
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EP3425202A1 (fr
EP3425202A4 (fr
Inventor
Masaaki Kamikawa
Mihoko Shimoji
Hideaki Nagata
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP3425202A4 publication Critical patent/EP3425202A4/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/48—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
    • 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
    • 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
    • F04C28/08—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the rotational speed
    • 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

Definitions

  • the present invention relates to, for example, a screw compressor and a refrigeration cycle apparatus that perform refrigerant compression.
  • the present invention relates to, in particular, a screw compressor or the like including economizer ports.
  • a conventional refrigeration cycle apparatus including, as a device configuring a refrigerant circuit, an intermediate cooler to perform heat exchange between refrigerant and refrigerant to increase, for example, a capacity and improve performance and a coefficient of performance (a ratio of a refrigeration capacity to a compressor input) of the refrigeration cycle.
  • Some refrigeration cycle apparatus including the intermediate cooler can perform economizer operation for leading gaseous refrigerant (hereinafter referred to as economizer gas) after cooling of liquid refrigerant in the intermediate cooler to a compressor intermediate unit.
  • the intermediate cooler is disposed between a condenser and an evaporator of the refrigerant circuit.
  • the refrigeration cycle apparatus includes an economizer pipe branching from a main refrigerant circuit halfway between the evaporator and the condenser.
  • An expansion valve for intermediate cooling is set in the economizer pipe.
  • the refrigeration cycle apparatus includes a screw compressor including economizer ports to which the economizer pipe is connected.
  • the screw compressor includes a screw rotor, a casing to house the screw rotor, a bypass port to allow a low-pressure chamber and a suction side of a compression chamber to communicate, and a slide valve slid in a rotation axis direction of the screw rotor to close a part or the whole of bypass port and adjust the size of an opening port portion of the bypass port.
  • Some screw compressor includes at least two compression chambers among an inner surface of a casing, a screw rotor, and a gate rotor. In the conventional techniques, the economizer port described above is provided only in one compression chamber.
  • a controller moves, first, the slide valve of the other compression chamber in which the economizer port is not provided, adjusts the opening port portion of the bypass port, and adjusts the capacity of a compressor. At this time, the economizer gas does not flow into a suction side through the bypass port. Hindrance of refrigerant to be sucked is prevented (see, for example, Patent Literature 1).
  • GB 2528214 A discloses a screw compressor for a refrigerant system comprising a casing, a sliding valve for adjusting a discharge start timing, and an economizer flow path in the casing.
  • WO 2014/192898 A1 discloses a refrigerant system comprising a screw compressor having a case, a sliding valve for adjusting a discharge start timing, and an economizer flow path in the casing.
  • an economizer flow port is provided with the sliding valve so that the economizer flow port is correspond to the economizer flow path by moving the sliding valve to implement an economizer operation.
  • EP 2410182 A1 discloses a screw compressor having a slide valve in each fluid chamber for adjusting operating capacity of the screw compressor in a manner that the slide valve is moved to change the on/off status of a bypass passage connected with a low pressure area of the screw compressor and the corresponding fluid chamber finishing a suction phase from the low pressure area.
  • Patent Literature 1 Japanese Patent No. 1551204
  • a screw compressor that adjusts a capacity by inverter control a ratio of a leak to a discharge amount is large and performance is deteriorated during low-rotation speed operation. Therefore, the slide valve is moved relative to one compression chamber to adjust the area of opening of the bypass port.
  • Cylinder partial disuse operation that opens the bypass port to bring one compression chamber into a no-load state and reduces area of opening of a suction volume of the compressor to approximately a half is performed to reduce the suction volume and a seal length at which a refrigerant gas leaks.
  • an object of the present invention is to provide a screw compressor and a refrigeration cycle apparatus that can realize a high coefficient of performance in a wide operation range and improve performance.
  • a screw compressor includes: an electric motor configured to operate at a variable rotation speed; a screw rotor including a plurality of screw grooves on an outer circumferential surface; a screw shaft configured to transmit a driving force of the electric motor to the screw rotor and rotate the screw rotor; a first gate rotor and a second gate rotor, the first gate rotor being disposed on one side of the screw rotor, the second gate rotor being disposed on an other side of the screw rotor, the first gate rotor and the second gate rotor being disposed point-symmetrically with respect to the screw shaft and including, in outer circumferential portions, a plurality of teeth meshed with the screw grooves; a casing having a cylindrical shape to house the screw rotor inside a cylinder; the first gate rotor, the screw groove and the casing forming, by surrounding, a first compression chamber, the second gate rotor, the screw groove and the casing forming, by surrounding, a second compression chamber, a
  • a refrigeration cycle apparatus is a refrigeration cycle apparatus in which the screw compressor described above, a condenser, a high-pressure side channel of an intermediate cooler, a decompression device, and an evaporator are connected in order by refrigerant pipes to configure a refrigerant circuit that circulates refrigerant, which is fluid, the refrigeration cycle apparatus comprising an economizer pipe branching from a pipe between the intermediate cooler and the decompression device and connected to an economizer port included in the screw compressor via an expansion device for the intermediate cooler and an intermediate-pressure side channel of the intermediate cooler.
  • the economizer port and the bypass device are provided on the first compression chamber side. Therefore, for example, economizer operation is performed and an economizer effect is obtained during high-load operation.
  • the rotation speed can be increased by bringing the first compression chamber into the no-load state.
  • the economizer is switched to stop operation, it is possible to reduce a loss due to a dead volume. Therefore, it is possible to obtain a screw compressor and other devices that can realize a high coefficient of performance in a wide operation range and improve performance.
  • Fig. 1 is a diagram illustrating the configuration of a refrigeration cycle apparatus 100 including a screw compressor 102 according to Embodiment 1 of the present invention.
  • the screw compressor 102 is a device constituting a refrigerant circuit. Therefore, fluid sucked, compressed, and discharged by the screw compressor 102 in Embodiment 1 and other embodiments is explained as being refrigerant.
  • the refrigeration cycle apparatus 100 of Embodiment 1 includes a main refrigerant circuit configured by connecting, with refrigerant pipes, the screw compressor 102 supplied with electric power from an inverter device 101 to be driven, a condenser 103, a high-pressure side channel of an intermediate cooler 104, an expansion valve 105, which is a decompression device, and an evaporator 106 in order.
  • the refrigeration cycle apparatus 100 further includes an economizer pipe 108, one end of which branches from a pipe in which mainstream refrigerant flows between the intermediate cooler 104 and the expansion valve 105.
  • the other end of the economizer pipe 108 is connected to the screw compressor 102 via an intermediate-cooler expansion valve 107 and an intermediate-pressure side channel of the intermediate cooler 104.
  • a solenoid valve 109 serving as a valve that allows refrigerant to pass or prevents the refrigerant from passing the economizer pipe 108 is provided.
  • the inverter device 101 controls electric power supply to the screw compressor 102 and controls rotation speed of the screw compressor 102.
  • the screw compressor 102 will be explained below.
  • the condenser 103 cools and condenses a discharge gas, which is gaseous refrigerant, discharged from the screw compressor 102.
  • the expansion valve 105 decompresses and expands the mainstream refrigerant flowing out from the high-pressure side channel of the intermediate cooler 104. Further, the evaporator 106 evaporates the refrigerant flowing out from the expansion valve 105.
  • the intermediate cooler 104 causes high-pressure side refrigerant, which is the mainstream refrigerant, and intermediate-pressure refrigerant to exchange heat.
  • the high-pressure side refrigerant is refrigerant flowing in the high-pressure side channel between the condenser 103 and the expansion valve 105.
  • the intermediate-pressure refrigerant is refrigerant obtained by decompressing a part of the high-pressure side refrigerant by the intermediate-cooler expansion valve 107 and flowing in the intermediate-pressure side channel.
  • the high-pressure side refrigerant is cooled by the heat exchange.
  • the intermediate-pressure refrigerant is heated to be an economizer gas.
  • the refrigeration cycle apparatus 100 further includes a controller 110.
  • the controller 110 controls the inverter device 101, the expansion valve 105, the intermediate-cooler expansion valve 107, and other devices.
  • the controller 110 includes a bypass control device 111 and a valve control device 112.
  • the bypass control device 111 performs position control and other kinds of control of a slide valve 8 included in the screw compressor 102.
  • the valve control device 112 controls opening and closing of the solenoid valve 109.
  • Fig. 2 is a diagram for explaining the internal configuration in the screw compressor 102 according to Embodiment 1 of the present invention.
  • Fig. 3 is a diagram illustrating a relation between a casing 1, a screw rotor 3, and a gate rotor 6 and a compression chamber 5 in the screw compressor 102 according to Embodiment 1 of the present invention.
  • the screw compressor 102 according to Embodiment 1 of the present invention will be explained below with reference to Fig. 2 and Fig. 3 .
  • the screw compressor 102 of Embodiment 1 includes the casing 1, the screw rotor 3, the gate rotor 6, an electric motor 2 to drive to rotate the screw rotor 3, the slide valve 8 and other devices.
  • the casing 1 having a cylindrical shape houses the screw rotor 3, the gate rotor 6, the electric motor 2, the slide valve 8, and other devices inside a cylinder.
  • the electric motor 2 includes a stator 2a fixed in contact with the casing 1 and a motor rotor 2b disposed inside the stator 2a. The electric motor 2 is driven at rotation speed based on electric power supplied from the inverter device 101.
  • the screw rotor 3 is disposed in the casing 1. Both the screw rotor 3 and the motor rotor 2b are disposed and fixed around a screw shaft 4 serving as a rotating shaft. A plurality of spiral screw grooves 5a are formed on an outer circumferential surface of the screw rotor 3. The screw rotor 3 rotates by rotation of the motor rotor 2b fixed to the screw shaft 4.
  • the screw compressor 102 of Embodiment 1 includes two gate rotors 6.
  • the two gate rotors 6 are disposed in positions point-symmetrical with respect to the screw shaft 4 and on both sides of the screw rotor 3.
  • One of the gate rotors 6 is referred to as a first gate rotor 6b and the other is referred to as a second gate rotor 6c.
  • the gate rotors 6 are formed in a disk-like shape.
  • a plurality of teeth 6a are provided on outer circumferential surfaces of the gate rotors 6 along a circumferential direction.
  • the teeth 6a of the gate rotors 6 are meshed with the screw grooves 5a.
  • Spaces surrounded by the teeth 6a of the gate rotors 6, the screw grooves 5a, and a cylinder inner surface side of the casing 1 are the compression chambers 5.
  • a plurality of the compression chambers 5 are formed in positions point-symmetrical with respect to a radial direction center of the screw rotor 3.
  • the compression chamber 5 surrounded by the casing 1, the screw rotor 3, and the teeth 6a of the first gate rotor 6b is referred to as a first compression chamber 5b.
  • the compression chamber 5 surrounded by the casing 1, the screw rotor 3, and the teeth 6a of the second gate rotor 6c is referred to as a second compression chamber 5c.
  • the first compression chamber 5b and the second compression chamber 5c are explained as the compression chamber 5.
  • a low-pressure side serving as a suction side of the refrigerant and a high-pressure side serving as a discharge side of the refrigerant by a partition wall (not illustrated in the figure).
  • a space on the low-pressure side is a low-pressure chamber (not illustrated in the figure) configured to have atmosphere of a suction pressure.
  • a space on the high-pressure side is a high-pressure chamber having a discharge pressure atmosphere (not illustrated in the figure).
  • a discharge port 7 (see Fig. 4 referred to below) to cause the high-pressure chamber and the compression chamber 5 to communicate is provided in a position on the high-pressure side of the compression chamber 5.
  • a slide groove 1a extending in a rotation axis direction of the screw rotor 3 is formed in a position corresponding to the first compression chamber 5b.
  • the slide valve 8 serving as a bypass device is housed such that it can slide along the slide groove 1a.
  • a part of the wall of the slide valve 8 is integrated with a part of the casing 1 to form the first compression chamber 5b in conjunction with the casing 1.
  • the slide valve 8 is provided only on one compression chamber 5 of the two compression chambers 5.
  • the slide valve 8 serving as the bypass device is provided only in the first compression chamber 5b.
  • the screw compressor 102 in which the slide groove 1a and the slide valve 8 are provided only on the first compression chamber 5b side is explained.
  • the slide groove 1a and the slide valve 8 may be present only on the second compression chamber 5c side.
  • the second compression chamber 5c is a first compression chamber.
  • the slide valve 8 is connected to a bypass driving device 10 such as a piston via a coupling bar 9.
  • the bypass driving device 10 is driven, and thereby the slide valve 8 moves in the rotation axis direction of the screw rotor 3 in the slide groove 1a.
  • the bypass control device 111 of the controller 110 sends, to the bypass driving device 10, an instruction for locating the slide valve 8 in a position where a discharge amount of fluid discharged from the discharge port 7 provided to the first compression chamber 5b is smaller than a discharge amount of fluid discharged from a discharge port provided to the second compression chamber 5c and performs capacity control operation of the screw compressor 102.
  • a power source of driving of the bypass driving device 10 that drives the slide valve 8 is not limited.
  • the power source is, for example, a power source that drives the slide valve 8 with a gas pressure, a power source that drives the slide valve 8 with a hydraulic pressure, or a power source that drives the slide valve 8 with a motor or the like separately from a piston.
  • the casing 1 includes an economizer gas channel 1b for leading the economizer gas flowing out from the intermediate cooler 104 to the first compression chamber 5b.
  • the economizer gas channel 1b communicates with the first compression chamber 5b via an economizer port 1c.
  • the economizer pipe 108 is connected to the economizer gas channel 1b. The economizer gas flowing out and branching from the intermediate cooler 104 and cooling mainstream refrigerant liquid flows into the first compression chamber 5b through the economizer pipe 108, the economizer gas channel 1b, and the economizer port 1c.
  • the economizer gas channel 1b and the economizer port 1c for leading the economizer gas from the intermediate cooler 104 communicate with the first compression chamber 5b and are provided only on the first compression chamber 5b side as explained above.
  • Some economizer gas channel 1b in the casing 1 includes a space for preventing pulsation at the time when a refrigerant gas flows (not illustrated in the figure) is provided, and through this space, the economizer gas channel 1b communicates with the first compression chamber 5b.
  • the screw compressor 102 sucks and compresses a refrigerant gas, which is gaseous refrigerant, and thereafter discharges the refrigerant gas.
  • the discharge gas discharged from the screw compressor 102 is cooled by the condenser 103.
  • Refrigerant cooled by the condenser 103 flows into the high-pressure side channel of the intermediate cooler 104.
  • the intermediate cooler 104 causes high-pressure side refrigerant passing the high-pressure side channel and intermediate-pressure refrigerant branching after passing the intermediate cooler 104, decompressed by the intermediate-cooler expansion valve 107, and passing the intermediate-pressure side channel to exchange heat.
  • the high-pressure side refrigerant is supercooled by the heat exchange with the intermediate-pressure refrigerant.
  • the refrigerant is supercooled, a refrigeration effect in the evaporator 106 increases.
  • the supercooled refrigerant is heated by the evaporator 106 to be a refrigerant gas.
  • the refrigerant gas flowing out from the evaporator 106 is sucked by the screw compressor 102.
  • the intermediate-pressure refrigerant passing the intermediate-pressure side channel of the intermediate cooler 104 changes to an economizer gas after cooling the high-pressure side refrigerant and passes the economizer pipe 108 and the economizer gas channel 1b.
  • the economizer gas is injected into the first compression chamber 5b from the economizer port 1c provided in the casing 1.
  • the injected economizer gas is mixed with the refrigerant gas being compressed and is discharged from the screw compressor 102.
  • Fig. 4 is a diagram illustrating a compression principle of the screw compressor 102 according to Embodiment 1 of the present invention.
  • the operation of the screw compressor 102 according to Embodiment 1 will be explained.
  • the screw rotor 3 is rotated by the electric motor 2 illustrated in Fig. 2 via the screw shaft 4 illustrated in Fig. 2
  • the teeth 6a of the gate rotor 6 relatively move in the compression chamber 5 (the screw grooves 5a).
  • a suction stroke, a compression stroke, and a discharge stroke are sequentially performed.
  • the suction stroke, the compression stroke, and the discharge stroke together form one cycle of the compression operation and the cycle is repeated.
  • Each stroke will be explained focusing on the compression chamber 5 indicated by dot hatching in Fig. 4 .
  • Fig. 4(a) illustrates a state of the compression chamber 5 in the suction stroke.
  • the screw rotor 3 is driven by the electric motor 2 to rotate in a direction of a solid line arrow.
  • a volume of the compression chamber 5 decreases as illustrated in Fig. 4(b) .
  • the economizer port 1c is provided in only the compression chamber 5 on one side (in an example of Embodiment 1, the first compression chamber 5b).
  • the screw compressor 102 performs economizer operation.
  • the screw compressor 102 further has an object of preventing the economizer port 1c from becoming a dead volume during low-load operation for operation in a low-load state.
  • the screw compressor 102 will be explained in detail below.
  • operation during the compression stroke will be explained, by comparing the relation between suction bypass control and the economizer port 1c during the high-load operation and the relation between those during the low-load operation.
  • the low load is a predetermined load set by the controller 110 as a determination standard for operation of the screw compressor 102.
  • the screw compressor 102 is driven at low rotation speed of approximately 20 Hz to 30 Hz or less.
  • Low-pressure difference operation is often performed in the refrigerant circuit.
  • the low-load operation is operation under the low load.
  • the screw compressor 102 is driven at high rotation speed.
  • the inside of the refrigerant circuit is often in a high-pressure difference state.
  • the compression stroke and the economizer circuit in the case in which, in the high-load operation, the suction-side bypass port 1d present between the low-pressure chamber and the compression chambers 5 does not open and compression is performed in both of the compression chambers 5.
  • the suction-side bypass port 1d is closed not to be opened. The refrigerant is compressed in the two compression chambers 5.
  • Fig. 5 is a schematic diagram illustrating a state at the time when the suction-side bypass port 1d is not opened in the screw compressor 102 according to Embodiment 1 of the present invention.
  • Fig. 6 is a development of an inner cylinder surface of the casing 1 and the screw rotor 3 at the time when the suction-side bypass port 1d is not opened in the screw compressor 102 according to Embodiment 1 of the present invention.
  • the economizer operation is performed to improve a refrigeration effect, a coefficient of performance, and the like.
  • the bypass control device 111 of the controller 110 moves the slide valve 8 to the suction side (the right side in Fig. 5 and Fig. 6 ) as indicated by white arrows in Fig. 5 and Fig. 6 .
  • the slide valve 8 is moved to a position (a first position) where the suction-side bypass port 1d is not opened. Since the suction-side bypass port 1d is not opened, the economizer gas channel 1b provided in the casing 1 and the first compression chamber 5b communicate via the economizer port 1c but do not communicate with the low-pressure chamber.
  • the economizer gas passing through the economizer gas channel 1b is injected into the first compression chamber 5b from the economizer port 1c. While the economizer port 1c is positioned in the first compression chamber 5b, when a pressure (an intermediate pressure) of the refrigerant in the first compression chamber 5b rises, a capacity expansion effect by the economizer operation decreases.
  • the economizer port 1c is disposed in a position where the economizer gas flows as much as possible into a low-pressure portion of the first compression chamber 5b in a range in which the economizer gas does not hinder the refrigerant gas from flowing into the compression chamber 5.
  • the suction-side bypass port 1d that causes the low-pressure chamber and the first compression chamber 5b to communicate is not opened. Consequently, the two compression chambers 5 are formed in the screw compressor 102.
  • the economizer gas flows into the first compression chamber 5b via the economizer pipe 108 and other pipes. Therefore, it is possible to secure a necessary refrigeration capacity during the high-load operation. Further, it is possible to realize a high coefficient of performance with an economizer effect.
  • the compression stroke and the economizer circuit in the case in which the suction-side bypass port 1d of the first compression chamber 5b is opened will be explained.
  • the suction-side bypass port 1d When the suction-side bypass port 1d is in an opened state, the first compression chamber 5b and the low-pressure chamber communicate. Compression is not performed in the first compression chamber 5b. Therefore, a suction volume in the screw compressor 102 decreases to approximately a half (1/2).
  • Single chamber operation one-side operation in which the first compression chamber 5b is in a no-load state is performed.
  • Fig. 7 is a schematic diagram illustrating a state at the time when the suction-side bypass port 1d is opened in the screw compressor 102 according to Embodiment 1 of the present invention.
  • Fig. 8 is a development of the inner cylinder surface of the casing 1 and the screw rotor 3 at the time when the suction-side bypass port 1d is opened in the screw compressor 102 according to Embodiment 1 of the present invention.
  • the slide valve 8 is moved to the discharge side and moved to a position where the suction-side bypass port 1d of the low-pressure chamber and the first compression chamber 5b is opened. Since the suction-side bypass port 1d is opened, the compression stroke is not performed in the first compression chamber 5b. The first compression chamber 5b comes into a no-load state. Since the compression stroke is performed only in the second compression chamber 5c, a displacement volume is approximately a half (1/2) with respect to a case in which the suction-side bypass port 1d is not opened.
  • the screw compressor 102 is driven with an increased rotation speed. Since the rotation speed is increased, it is possible to prevent deterioration in the ratio of a leak to a discharge amount.
  • the economizer port 1c is a dead volume and a recompression loss and a leak loss occur.
  • the dead volume refers to a wastefully compressed volume portion.
  • the valve control device 112 closes the solenoid valve 109 present in the economizer pipe 108 and stops the economizer operation.
  • the economizer port 1c and the suction-side bypass port 1d are provided on the first compression chamber 5b side.
  • the bypass control device 111 moves the slide valve 8, opens the suction-side bypass port 1d, and performs cylinder partial disuse operation.
  • the bypass control device 111 of the controller 110 moves the slide valve 8 to the discharge side (the left side in Fig. 7 and Fig. 8 ) as indicated by white arrows in Fig. 7 and Fig. 8 .
  • the slide valve 8 moves to a position (a second position) where the suction-side bypass port 1d is opened. Since the first compression chamber 5b is disused for compression, the compression stroke is not performed in the first compression chamber 5b. Therefore, the economizer port 1c and the economizer gas channel 1b cannot be the dead volume.
  • the screw compressor 102 of Embodiment 1 is a compressor that achieves a high coefficient of performance.
  • the economizer port 1c and the economizer gas channel 1b are provided in the first compression chamber 5b, while the suction-side bypass port 1d and the slide valve 8 are provided in the first compression chamber 5b.
  • Fig. 9 is a diagram illustrating the configuration of the refrigeration cycle apparatus 100 including the screw compressor 102 according to Embodiment 2 of the present invention. Differences from the refrigeration cycle apparatus 100 of Embodiment 1 will be explained.
  • the refrigeration cycle apparatus 100 of Embodiment 2 is different from the refrigeration cycle apparatus 100 of Embodiment 1 in the configurations of the screw compressor 102 and the controller 110.
  • the screw compressor 102 in Embodiment 2 includes a first slide valve 8a and a second slide valve 8b.
  • the first slide valve 8a is set in the first compression chamber 5b.
  • the first slide valve 8a performs the operation of a bypass device.
  • the second slide valve 8b is set not only on the first compression chamber 5b side but also on the second compression chamber 5c side.
  • the second slide valve 8b is set to be movable in an axial direction of the screw rotor 3.
  • An internal-volume-ratio changing mechanism 11 to change a position of the second slide valve 8b is set.
  • the internal volume ratio means a ratio of a volume of the compression chamber 5 at suction completion (compression start) time and a volume of the compression chamber 5 immediately before discharge. A change of the internal volume ratio is performed by adjusting timing when the refrigerant is discharged from the discharge port 7.
  • the second slide valve 8b is positioned on the suction side.
  • the position of the second slide valve 8b is changed to set opening timing of the discharge port 7 to early timing and reduce a volume ratio.
  • the second slide valve 8b is positioned on the discharge side.
  • the position of the second slide valve 8b is changed to set the opening timing of the discharge port 7 to later timing and increase the volume ratio.
  • the second slide valve 8b configures a part of the discharge port 7. Therefore, the internal-volume-ratio changing mechanism 11 can adjust timing of discharge and change the internal volume ratio by moving the second slide valve 8b. Therefore, insufficient compression during the high-load operation and excessive compression during the low-load operation are prevented to improve performance.
  • the controller 110 of Embodiment 2 further includes an internal-volume-ratio control device 113.
  • the internal-volume-ratio control device 113 sends an instruction to the internal-volume-ratio changing mechanism 11 and performs control for locating the second slide valve 8b based on the internal volume ratio.
  • Embodiment 2 To clarify characteristics of Embodiment 2, as in Embodiment 1, position control of the first slide valve 8a and the second slide valve 8b and a relation of the economizer port 1c during the high-load operation and during the low-load operation are compared and operation during the compression stroke will be explained.
  • Fig. 10 is a schematic diagram illustrating a state at the time when the suction-side bypass port 1d is not opened in the screw compressor 102 according to Embodiment 2 of the present invention.
  • Fig. 11 is a development of the inner cylinder surface of the casing 1 and the screw rotor 3 at the time when the suction-side bypass port 1d is not opened in the screw compressor 102 according to Embodiment 2 of the present invention. The operation and the like of the screw compressor 102 during the high-load operation will be explained with reference to Fig. 10 and Fig. 11 .
  • the bypass control device 111 of the controller 110 moves the first slide valve 8a to the suction side (the right side in Fig. 10 and Fig. 11 ) as indicated by white arrows in Fig. 10 and Fig. 11 .
  • the first slide valve 8a moves to a position (a first position) for not opening the suction-side bypass port 1d.
  • the internal-volume-ratio control device 113 of the controller 110 sends an instruction to the internal-volume-ratio changing mechanism 11 and locates the second slide valve 8b such that an internal volume ratio is the same and timing when the refrigerant is discharged from the discharge port 7 is the same in the first compression chamber 5b and the second compression chamber 5c.
  • the internal-volume-ratio control device 113 moves, for example, the second slide valve 8b to the discharge side (the left side in Fig. 10 and Fig. 11 ).
  • the suction-side bypass port 1d to cause the low-pressure chamber and the first compression chamber 5b to communicate is not opened, whereby the two compression chambers 5 are formed in the screw compressor 102. Since the economizer gas flows into the first compression chamber 5b via the economizer pipe 108 and other pipes, it is possible to secure a necessary refrigeration capacity during the high-load operation. Further, it is possible to realize a high coefficient of performance to properly adjust the economizer effect and the internal volume ratio.
  • Fig. 12 is a schematic diagram illustrating a state at the time when the suction-side bypass port 1d is opened in the screw compressor 102 according to Embodiment 2 of the present invention.
  • Fig. 13 is a development of the inner cylinder surface of the casing 1 and the screw rotor 3 at the time when the suction-side bypass port 1d is opened in the screw compressor 102 according to Embodiment 2 of the present invention.
  • the valve control device 112 of the controller 110 closes the solenoid valve 109 to prevent an economizer gas from flowing into the first compression chamber 5b.
  • the bypass control device 111 of the controller 110 moves the slide valve 8 to the discharge side (the left side in Fig. 12 and Fig. 13 ) as indicated by white arrows in Fig. 12 and Fig. 13 .
  • the slide valve 8 moves to a position (a second position) where the suction-side bypass port 1d is opened. Since the first compression chamber 5b is halted, the compression stroke is not performed in the first compression chamber 5b.
  • the internal-volume-ratio control device 113 of the controller 110 sends an instruction to the internal-volume-ratio changing mechanism 11 to move the second slide valve 8b to a position suitable for operation. Specifically, as indicated by the white arrows in Fig. 12 and Fig. 13 , for example, the internal-volume-ratio control device 113 moves the second slide valve 8b to the suction side (the right side in Fig. 12 and Fig. 13 ), which is a direction in which the internal volume ratio is reduced.
  • the screw compressor 102 of Embodiment 2 in a state in which the first slide valve 8a is moved to open the suction-side bypass port 1d, the economizer port 1c and the economizer gas channel 1b are formed in the first compression chamber 5b in which the suction-side bypass port 1d is opened. Therefore, even during the low-load operation, by performing the single chamber operation, it is possible to secure a leak loss prevention effect according to an increase in the rotation speed. Since there is no influence of a space to be a dead volume, it is possible to reduce a recompression loss and a leak loss. Therefore, as the screw compressor 102 of Embodiment 2, it is possible to obtain the screw compressor 102 that realizes a high coefficient of performance.
  • timing for discharging the refrigerant from the discharge port 7 is adjusted by causing the internal-volume-ratio changing mechanism 11 to move the second slide valve 8b, it is possible to properly set the internal volume ratio in the second compression chamber 5c. Therefore, it is possible to prevent a power loss due to insufficient compression and excessive compression. It is possible to realize a higher coefficient of performance in a wide operation range.
  • control concerning the movement of the second slide valve 8b in the screw compressor 102 performed by the controller 110 may be continuous or may be stepwise.

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  • 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)

Claims (8)

  1. Compresseur à vis (102), comprenant :
    un moteur électrique (2) configuré pour fonctionner à une vitesse de rotation variable ;
    un rotor à vis (3) comprenant une pluralité de rainures de vis (5a) sur une surface circonférentielle extérieure ;
    un arbre à vis (4) configuré pour transmettre une force motrice du moteur électrique (2) au rotor à vis (3) et faire tourner le rotor à vis (3) ;
    un premier rotor femelle (6b) et un second rotor femelle (6c), le premier rotor femelle (6b) étant disposé d'un côté du rotor à vis (3), le second rotor femelle (6c) étant disposé d'un autre côté du rotor à vis (3), le premier rotor femelle (6b) et le second rotor femelle (6c) étant disposés de manière ponctuelle et symétrique par rapport à l'arbre de la vis (4) et comprenant, dans des parties circonférentielles extérieures, une pluralité de dents engrenées dans les rainures de la vis (5a) ;
    un boîtier (1) de forme cylindrique pour loger le rotor à vis (3) à l'intérieur d'un cylindre ;
    le premier rotor femelle (6b), la rainure de la vis (5a) et le boîtier (1) formant, en l'entourant, une première chambre de compression (5b),
    le second rotor femelle (6c), la rainure de la vis (5a) et le boîtier (1) formant, en l'entourant, une seconde chambre de compression (5c),
    un dispositif de dérivation comprenant un premier tiroir (8a), prévu uniquement sur la première chambre de compression (5b) des deux chambres de compression (5b, 5c) et configurée pour coulisser dans la direction de l'axe de rotation du rotor à vis (3) et pour permettre à la première chambre de compression (5b) et à une chambre à basse pression de communiquer l'une avec l'autre, la chambre à basse pression étant configurée pour avoir une atmosphère d'une pression d'aspiration ; et
    un orifice d'économiseur (1c) est fourni à l'enveloppe (1) uniquement du côté de la première chambre de compression (5b) pour communiquer avec la première chambre de compression (5b) et configuré pour permettre au fluide s'écoulant de l'extérieur de s'écouler à l'intérieur de l'enveloppe (1),
    le compresseur à vis (102) est configuré pour, lors d'une opération à faible charge, déplacer le premier tiroir (8a) dans une position où la première chambre de compression (5b) entre dans un état de non-charge dans lequel la pression du fluide dans la première chambre de compression (5b) n'augmente pas, tandis que le compresseur à vis 102 est entraîné avec une vitesse de rotation accrue.
  2. Compresseur à vis (102) selon la revendication 1, dans lequel
    le compresseur à vis
    comprend le premier tiroir (8a) configuré pour coulisser dans une direction longitudinale de l'arbre de la vis (4), et
    est configuré pour positionner le premier tiroir (8a) dans une position où une quantité de fluide évacuée d'un orifice de décharge inclus dans la première chambre de compression (5b) est inférieure à une quantité de fluide évacuée d'un orifice de décharge inclus dans la seconde chambre de compression (5c).
  3. Compresseur à vis (102) de l'une quelconque des revendications 1 à 2, dans lequel un orifice de dérivation côté aspiration (1d) est prévu entre la chambre basse pression et la première chambre de compression (5b).
  4. Compresseur à vis (102) selon la revendication 3, dans lequel le premier tiroir (8a) est commandé pour se déplacer vers une première position dans laquelle le premier tiroir (8a) ferme l'orifice de dérivation côté aspiration (1d), et une deuxième position dans laquelle le premier tiroir (8a) ouvre l'orifice de dérivation côté aspiration (1d).
  5. Compresseur à vis (102) selon l'une quelconque des revendications 1 à 4, comprenant en outre :
    un deuxième tiroir (83) fixé à une surface circonférentielle extérieure de la deuxième chambre de compression (5c) et de l'enveloppe (1), et configuré pour coulisser dans une direction longitudinale de l'arbre de la vis (4) ; et
    un mécanisme de changement de rapport de volume interne configuré pour faire coulisser le second tiroir.
  6. Appareil à cycle de réfrigération dans lequel le compresseur à vis (102) selon l'une quelconque des revendications 1 à 5, un condenseur, un canal latéral à haute pression d'un refroidisseur intermédiaire (104), un dispositif de décompression (105) et un évaporateur sont reliés dans l'ordre par des tuyaux de fluide frigorigène pour configurer un circuit de fluide frigorigène qui fait circuler le fluide frigorigène, qui est un fluide,
    l'appareil à cycle de réfrigération comprend un tuyau économiseur partant d'un tuyau entre le refroidisseur intermédiaire (104) et le dispositif de décompression (105) et relié à un orifice économiseur (1c) inclus dans le compresseur à vis (102) via un dispositif d'expansion (107) pour le refroidisseur intermédiaire (104) et un canal latéral à pression intermédiaire du refroidisseur intermédiaire (104).
  7. Appareil à cycle de réfrigération selon la revendication 6, dans lequel, lorsqu'une charge de l'appareil à cycle de réfrigération est inférieure à une charge prédéterminée, le mécanisme de modification du rapport de volume interne est configuré pour déplacer le second tiroir dans une direction dans laquelle un rapport de volume interne est réduit.
  8. Appareil à cycle de réfrigération selon la revendication 6 ou la revendication 7 comprenant en outre une soupape (109) qui empêche le fluide frigorigène de passer par le tuyau de l'économiseur lorsque l'appareil à cycle de réfrigération détermine qu'une charge de l'appareil à cycle de réfrigération est inférieure à une charge prédéterminée.
EP16892504.8A 2016-03-01 2016-03-01 Compresseur à vis et dispositif à cycle de réfrigération Active EP3425202B1 (fr)

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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
CN108644116A (zh) * 2018-07-13 2018-10-12 麦克维尔空调制冷(苏州)有限公司 螺杆压缩机系统以及包含该螺杆压缩机系统的换热系统
GB2581526A (en) * 2019-02-22 2020-08-26 J & E Hall Ltd Single screw compressor
CN109854509B (zh) * 2019-03-19 2024-04-26 福建雪人股份有限公司 一种燃料电池用空气压缩机的内建容积比的自动调节装置
US11802563B2 (en) * 2019-11-26 2023-10-31 Mitsubishi Electric Corporation Screw compressor
WO2021229743A1 (fr) * 2020-05-14 2021-11-18 三菱電機株式会社 Compresseur à vis
WO2022244219A1 (fr) * 2021-05-21 2022-11-24 三菱電機株式会社 Compresseur à vis

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US4610613A (en) * 1985-06-03 1986-09-09 Vilter Manufacturing Corporation Control means for gas compressor having dual slide valves
JP2576309B2 (ja) * 1991-07-02 1997-01-29 ダイキン工業株式会社 スクリュー冷凍装置
JP4374958B2 (ja) * 2003-09-16 2009-12-02 ダイキン工業株式会社 シングルスクリュー圧縮機
WO2010106787A1 (fr) * 2009-03-16 2010-09-23 ダイキン工業株式会社 Compresseur à vis
JP5445118B2 (ja) * 2009-12-24 2014-03-19 ダイキン工業株式会社 スクリュー圧縮機
JP5126402B2 (ja) * 2010-10-29 2013-01-23 ダイキン工業株式会社 スクリュー圧縮機
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JP5951125B2 (ja) * 2013-05-30 2016-07-13 三菱電機株式会社 スクリュー圧縮機及び冷凍サイクル装置
JP6058133B2 (ja) * 2013-05-30 2017-01-11 三菱電機株式会社 スクリュー圧縮機及び冷凍サイクル装置
JP6177450B2 (ja) * 2014-09-24 2017-08-09 三菱電機株式会社 スクリュー圧縮機および冷凍サイクル装置

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EP3425202A1 (fr) 2019-01-09
JP6685379B2 (ja) 2020-04-22
JPWO2017149659A1 (ja) 2018-09-20
EP3425202A4 (fr) 2019-01-09
WO2017149659A1 (fr) 2017-09-08

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