WO2018088154A1 - Compresseur à spirale - Google Patents

Compresseur à spirale Download PDF

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Publication number
WO2018088154A1
WO2018088154A1 PCT/JP2017/037758 JP2017037758W WO2018088154A1 WO 2018088154 A1 WO2018088154 A1 WO 2018088154A1 JP 2017037758 W JP2017037758 W JP 2017037758W WO 2018088154 A1 WO2018088154 A1 WO 2018088154A1
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WO
WIPO (PCT)
Prior art keywords
scroll
pressure
bypass
orbiting scroll
compression chamber
Prior art date
Application number
PCT/JP2017/037758
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English (en)
Japanese (ja)
Inventor
遼太 飯島
田村　和巳
Original Assignee
日立ジョンソンコントロールズ空調株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by 日立ジョンソンコントロールズ空調株式会社 filed Critical 日立ジョンソンコントロールズ空調株式会社
Publication of WO2018088154A1 publication Critical patent/WO2018088154A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • 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
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present invention relates to a scroll compressor.
  • a scroll compressor as one of refrigerant compressors used in refrigeration cycles such as refrigeration and air conditioning, or gas compressors that compress air and other gases.
  • a compressor having a capacity control mechanism is known in order to achieve high efficiency over a wide load range.
  • a method of controlling the compressor capacity by making the frequency of the motor current of the compressor variable by using an inverter and electrically controlling the rotational speed is one of commonly used capacity control techniques.
  • Patent Document 1 states that “at least one of the first scroll member and the second scroll member provided with a spiral wrap meshing with each other on the end plate performs an eccentric rotational motion, and between the inner surfaces of both end plates.
  • An operating capacity control mechanism including an opening formed in the end plate of the first scroll member and communicating with the compression chamber, and a piston that opens and closes the opening.
  • a scroll compressor provided, wherein the piston is formed on the basis of a dimensional tolerance that protrudes from an inner surface of an end plate of the first scroll member in a state in which the opening is closed. When the portion protruding from the inner surface of the end plate of the first scroll member with the opening closed is used as the tip portion, at least the tip portion should wrap.
  • Scroll compressor characterized in that it is formed by wear-resistant material having low. "It is also disclosed (see claim 1).
  • the tip end portion of the bypass valve is formed of a material having lower wear resistance than that of the orbiting scroll, so that the tip end surface of the bypass valve wears out on the same plane as the fixed scroll tooth bottom surface when operated for a certain period of time. It is stated that it will be located.
  • this method generates wear powder of the bypass valve. This wear powder is caught between fixed and orbiting scroll wraps and between bearings, etc., and these are damaged, or the back pressure control valve is clogged. There is a risk of being.
  • the present invention has been devised in view of the above circumstances, and an object thereof is to provide a highly efficient scroll compressor that does not generate wear powder and has high reliability of a bypass valve.
  • a scroll compressor is a closed space formed by a turning scroll having a turning wrap, a fixed scroll having a fixed wrap, and the turning scroll and the fixed scroll.
  • a compression chamber for compressing the working fluid an open space formed by the orbiting scroll and the fixed scroll; a suction chamber into which the working fluid to be compressed is sucked; an electric motor for driving the orbiting scroll; and the compression
  • a bypass mechanism that communicates the chamber with the suction chamber, and a sealed container that houses the orbiting scroll, the fixed scroll, the compression chamber, the suction chamber, the electric motor, and the bypass mechanism. Is a bypass port formed in the fixed scroll and capable of communicating the compression chamber and the suction chamber.
  • a bypass valve disposed in the bypass port, biased away from the orbiting scroll by an elastic member, and capable of opening and closing between the compression chamber and the suction chamber; the compression chamber and the pressure switching device; A pressure-separating seal member, and the bypass valve is driven by a pressure switching device that selectively supplies a high pressure and a low pressure working fluid having a pressure lower than the high pressure, and the bypass valve has teeth of the fixed scroll. It has a shape that can protrude from the bottom surface, and is pressed against the orbiting scroll by the working fluid at the high pressure during full load operation to close the space between the compression chamber and the suction chamber, and the bypass valve
  • the tip portion that contacts the orbiting scroll has wear resistance equal to or higher than that of the orbiting scroll.
  • a scroll compressor is a closed space formed by a turning scroll having a turning wrap, a fixed scroll having a fixed wrap, and the turning scroll and the fixed scroll, and compresses the working fluid.
  • a bypass port formed and capable of communicating with the compression chamber and the suction chamber; and in the bypass port A bypass valve that is disposed and biased away from the orbiting scroll by an elastic member, and that can open and close between the compression chamber and the suction chamber; and the compression chamber and the outside of the bypass port are separated in pressure.
  • the bypass valve has a shape capable of projecting from the tooth bottom surface of the fixed scroll, and is pressed against the orbiting scroll during full load operation, so that it is between the compression chamber and the suction chamber.
  • the tip of the bypass valve that contacts the orbiting scroll has wear resistance equal to or greater than that of the orbiting scroll.
  • FIG. 2B is an enlarged view of a portion II in FIG.
  • FIG. 2B is an enlarged view of a portion II in FIG. 2A showing a state where the bypass valve is in contact with the orbiting scroll and performing full load operation.
  • the compressor which concerns on 1st Embodiment WHEREIN The figure which showed the refrigerant
  • the compressor which concerns on 1st Embodiment WHEREIN The state when the refrigerant
  • the longitudinal cross-sectional view of the compressor which concerns on 2nd Embodiment.
  • the longitudinal cross-sectional view of the compressor which concerns on 3rd Embodiment.
  • FIG. The longitudinal cross-sectional view which shows the bypass valve periphery of the modification 3.
  • FIG. 1 is a longitudinal sectional view of a compressor 1 according to the first embodiment.
  • 2A is an enlarged vertical sectional view of the compression mechanism 3 of the compressor 1 of FIG. 1, that is, an enlarged view of a portion I in FIG. 1
  • FIG. 2B is an enlarged view of a portion II in FIG. 2A
  • FIG. It is the II section enlarged view of Drawing 2A showing the state where bypass valve 11 is in contact with turning scroll 6, and performing full load operation.
  • the compressor 1 is a scroll compressor.
  • the compressor 1 bypasses the gas refrigerant (working fluid) supplied from the suction port 5a to the suction side without compressing part of the gas refrigerant in the compression chamber 10 by compressing the gas refrigerant (working fluid) by the compression mechanism unit 3.
  • Capacity control is performed by switching between partial load operation for compressing a gas refrigerant (hereinafter referred to as a refrigerant).
  • the compressor 1 includes a compression mechanism unit 3 that compresses refrigerant, an electric motor 4 that is a driving source of the compression mechanism unit 3, an airtight container 2 that houses the compression mechanism unit 3 and the electric motor 4, and control units (18 and 19). Is provided.
  • the compression mechanism unit 3 includes a fixed scroll 5 in which a spiral wrap 5c is erected on the lower side and a turning scroll 6 in which a spiral wrap 6a is erected on the upper side.
  • the orbiting scroll 6 is disposed below the fixed scroll 5.
  • the hermetic container 2 is constructed by vertically welding an upper lid chamber 2b and a lower bottom chamber 2c to a vertical central cylindrical case 2a.
  • a compression mechanism unit 3 is disposed in the upper part of the sealed container 2, and an electric motor 4 is disposed in the lower part through a crankshaft 9.
  • a lubricating oil 16 is stored at the bottom of the sealed container 2. The lubricating oil 16 is supplied to the mechanism portion via the oil supply passage 9c of the crankshaft 9 (details will be described later).
  • the upper lid chamber 2b is provided with a suction pipe 2d for sucking the refrigerant to be compressed.
  • the inside of the hermetic container 2 constitutes a discharge pressure chamber 2f into which the refrigerant compressed by the compression mechanism unit 3 is discharged.
  • a discharge pipe 2e that discharges the compressed refrigerant is provided on the side surface of the central case 2a.
  • the compression mechanism unit 3 includes an upper fixed scroll 5, a lower orbiting scroll 6, and a frame 7 that supports the orbiting scroll 6 from below.
  • the fixed scroll 5 is formed with a spiral wrap 5c facing downward on the end plate surface 5f side of the base plate 5d constituting the main body.
  • the orbiting scroll 6 has a spiral wrap 6 a formed upward on a base plate 6 b constituting the main body.
  • the frame 7 is integrated with the fixed scroll 5 by bolts 8 and supports the orbiting scroll 6 slidably from below.
  • a compression chamber 10 for compressing the refrigerant is formed.
  • the fixed scroll 5 is formed with a suction port 5a connected to the suction pipe 2d.
  • the suction port 5a is a suction port for the refrigerant to be compressed, and is provided coaxially with the suction pipe 2d.
  • a discharge port 5 e that communicates between the compression chamber 10 and the non-wrapping side (upper side) of the fixed scroll 5 is provided in the approximate center of the base plate 5 d of the fixed scroll 5.
  • the discharge port 5 e is a discharge port for the refrigerant compressed by the compression mechanism unit 3.
  • a bypass port 5 b is provided in the base plate 5 d of the fixed scroll 5 so as to penetrate from the compression chamber 10 to the opposite side of the fixed scroll 5 (upward side).
  • the bypass port 5b is a port used for capacity control, and is fully closed during full load operation and opened during partial load operation. That is, the pressure chamber 10 and the suction chamber 10a are closed during full load operation (see FIG. 2C), and the pressure chamber 10 and the suction chamber 10a are communicated during partial load operation (see FIG. 2B).
  • the bypass port 5b is formed, for example, by connecting two cylindrical grooves that are coaxial and have different diameters. As shown in FIG. 2B, the bypass port 5b is provided such that the diameter of the upper anti-wrap side cylindrical groove 5b1 is larger than the diameter of the lower wrap 6c side cylindrical groove 5b2.
  • the diameter t1 of the wrap-side cylindrical groove 5b2 below the bypass port 5b only needs to be larger than the thickness dimension t2 of the wrap 6a of the orbiting scroll 6. That is, the opening of the lap side cylindrical groove 5b2 only needs to exist across the wrap 6a of the orbiting scroll 6.
  • the bypass valve 11 has a shape in which two cylinders that are coaxial and have different diameters are connected so as to be fitted into the bypass port 5b. As shown in FIG. 2A, the bypass valve 11 is fitted into the bypass port 5b so that the port insertion portion 11a, which is a lower cylindrical portion having a smaller diameter than the upper portion, faces the wrap 5c side (lower side) of the fixed scroll 5. Yes.
  • the port insertion portion 11a is formed of a material having wear resistance equal to or higher than that of the orbiting scroll 6.
  • the port insertion portion 11a is characterized in that it has a dimension s2 longer than the depth s1 (see FIG. 2B) of the wrap-side cylindrical groove 5b2 of the bypass port 5b. This is because the upper surface of the orbiting scroll 6 is pressed by the port insertion portion 11a, and the pressure chamber 10 and the suction chamber 10a are surely blocked and closed. In other words, the port insertion portion 11a of the bypass valve 11 protrudes below the tooth bottom surface 5s (see FIG. 2A) of the fixed scroll 5 so that there is sufficient movement allowance when contacting the orbiting scroll 6. .
  • the port insertion portion 11a can protrude below the tooth bottom surface 5s (see FIG. 2A) of the fixed scroll 5 when it does not contact the orbiting scroll 6. Since the port insertion portion 11a of the bypass valve 11 is formed of a material having wear resistance equal to or higher than that of the orbiting scroll 6, the lower surface of the port insertion portion 11a of the bypass valve 11 is the upper surface of the wrap 6a of the orbiting scroll 6. It can suppress that it wears by contacting.
  • a flat plate-like retainer 20 is attached above the fixed scroll 5 on the side opposite to the wrap.
  • the bypass valve 11 is prevented from jumping out of the fixed scroll 5 by the contact of the bypass valve 11 with the retainer 20.
  • a ring-shaped rubber seal member 11 b is attached to the side surface of the bypass valve 11.
  • the seal member 11b of the bypass valve 11 abuts against the non-wrap side cylindrical groove 5b1 of the bypass port 5b and elastically deforms, thereby sealing between the bypass valve 11 and the bypass port 5b.
  • the seal member 11b is provided at a position where it does not come off from the non-wrap side cylindrical groove 5b1 of the bypass port 5b even if the bypass valve 11 moves up and down.
  • the bypass valve 11 does not come off the anti-wrap side cylindrical groove 5 b 1 of the bypass port 5 b even when the bypass valve 11 presses the orbiting scroll 6.
  • the bypass valve 11 does not come off from the anti-wrap side cylindrical groove 5b1 of the bypass port 5b.
  • the space inside the bypass port 5b is separated into two by the seal member 11b, and a control pressure space 11d (see FIG. 2A) is formed as a space communicating with the compression chamber 10 and a space not communicating with the compression chamber 10. .
  • a spring 11c is provided in the bypass port 5b so as to contact the bypass valve 11.
  • the spring 11c urges the bypass valve 11 away from the orbiting scroll 6, and presses the bypass valve 11 against the upper retainer 20. Thereby, even if the bypass valve 11 moves up and down, the refrigerant in the compression chamber 10 can be prevented from leaking from between the bypass valve 11 and the bypass port 5b.
  • the pressure switching device 18 shown in FIG. 1 is installed outside the sealed container 2 and communicates with the control pressure space 11 d via the control pipe 17. Further, the pressure switching device 18 includes a high-pressure side passage 18a connected to the discharge pipe 2e for discharging the compressed refrigerant, and a low-pressure side passage 18b connected to the refrigerant suction pipe 2d before compression. Yes.
  • the pressure switching device 18 can take in the refrigerant having the low suction pressure and the high discharge pressure, and selectively introduces the refrigerant having the two-stage pressure into the control pipe 17.
  • the pressure switching device 18 may include a pressure reducing mechanism, and at least one of the two-stage pressures may be configured to be a pressure between the suction pressure and the discharge pressure generated by the pressure reducing mechanism.
  • the refrigerant pressure introduced into the control pipe 17 is switched and controlled by the pressure switching device 18 at an arbitrary timing based on a signal from the pressure control device 19.
  • a crankshaft 9 for turning the orbiting scroll 6 by the electric motor 4 extends in the vertical direction at the center of the sealed container 2.
  • the frame 7 fixed to the sealed container 2 includes a main bearing 7 a that rotatably supports the crankshaft 9.
  • an orbiting bearing 6 c At the lower part of the orbiting scroll 6, there is provided an orbiting bearing 6 c to which the eccentric part 9 b of the crankshaft 9 is connected.
  • a back pressure chamber 14 is formed between the anti-wrap 6 a side on the lower side of the orbiting scroll 6 and the frame 7.
  • the back pressure in the back pressure chamber 14 is for bringing the orbiting scroll 6 into contact with the fixed scroll 5 from below.
  • An Oldham ring 13 is disposed inside the back pressure chamber 14. The Oldham ring 13 functions to revolve by receiving the eccentric rotation of the eccentric portion 9 b of the crankshaft 9 without rotating the orbiting scroll 6.
  • the Oldham ring 13 is attached to a groove (not shown) formed on the side of the orbiting scroll 6 opposite to the wrap 6a (lower side) and a groove (not shown) formed at the center upper portion of the frame 7.
  • the fixed scroll 5 is formed with oil supply holes 5 g and 5 h that allow the back pressure chamber 14 and the compression chamber 10 to communicate with each other.
  • a back pressure control valve 12 is provided in the middle of the oil supply holes 5g and 5h.
  • the electric motor 4 includes a stator 4a and a rotor 4b.
  • the stator 4a is fixed to the sealed container 2 by press-fitting and welding.
  • a crankshaft 9 is fixed to the rotor 4b and is rotatably supported in the stator 4a.
  • the crankshaft 9 includes a main shaft 9 a and an eccentric portion 9 b, and is supported by an upper main bearing 7 a provided in the frame 7 and a lower lower bearing 15 provided in the sealed container 2.
  • the eccentric portion 9 b is formed integrally with the main shaft 9 a of the crankshaft 9 so as to be eccentric, and is fitted to the orbiting bearing 6 c provided at the lower portion of the orbiting scroll 6. Thereby, the turning scroll 6 is rotatable with respect to the eccentric part 9b.
  • the crankshaft 9 is rotationally driven by the electric motor 4. Then, the eccentric portion 9b of the crankshaft 9 is eccentrically rotated with respect to the main shaft 9a, and the orbiting scroll 6 is orbitally moved. Further, the crankshaft 9 is provided with an oil supply passage 9 c that guides the lubricating oil 16 to the main bearing 7 a of the frame 7, the lower bearing 15, and the orbiting bearing 6 c of the orbiting scroll 6.
  • the lubricating oil 16 supplied from the oil supply passage 9c (see FIG. 1) to the orbiting bearing 6c passes through the back pressure chamber 14 and the oil supply holes 5h and 5g, and the wrap 5c of the fixed scroll 5 and the orbiting scroll 6 forming the compression chamber 10. Supplied to the wrap 6a.
  • the compressor 1 closes the bypass valve 11 so as to compress the refrigerant sucked from the suction port 5a, and opens the bypass valve 11 so that a part of the refrigerant in the compression chamber 10 is removed.
  • the capacity control is performed by switching to the partial load operation in which the refrigerant is circulated to the suction side through the bypass port 5b without being compressed and the other part of the refrigerant is compressed.
  • ⁇ Full load operation The operation of full load operation in which the bypass valve 11 is closed and the compression operation is performed will be described.
  • a high-pressure refrigerant is supplied from the pressure switching device 18 to the control pressure space 11d via the high-pressure channel 18a, and the bypass valve 11 is closed. That is, the port insertion portion 11a of the bypass valve 11 contacts the lap 6a of the orbiting scroll 6 (see FIG. 2C), and the pressure chamber 10 and the suction chamber 10a are closed and blocked. In this case, the scroll compressor 1 performs full load operation.
  • the suction chamber 10 a eventually becomes a closed space to form the compression chamber 10, and the refrigerant gas is compressed by reducing the volume of the compression chamber 10 as it moves toward the center of the orbiting scroll 6 and the fixed scroll 5. Is done.
  • the compression chamber 10 is formed by meshing the spiral wrap 5c of the fixed scroll 5 and the spiral wrap 6a of the orbiting scroll 6.
  • the port insertion portion 11a of the bypass valve 11 is longer than the wrap-side cylindrical groove 5b2 of the bypass port 5b, the port insertion portion 11a completely closes the wrap-side cylindrical groove 5b2 of the bypass port 5b. At the same time, it contacts the upper surface of the wrap 6a of the orbiting scroll 6. At this time, the load applied to the bypass valve 11 by the refrigerant pressure in the control pressure space 11d (see FIG. 2A) is all orbiting scroll except for the spring 11c having a relatively small load (spring force), that is, subtracting the spring force. 6, that is, supported by the upper surface of the wrap 6 a.
  • the pressure in the control pressure space 11d is optimized so that the seal pressure is optimized by conducting experiments in advance, friction between the port insertion portion 11a of the bypass valve 11 and the wrap 6a of the orbiting scroll 6 is achieved. It is possible to realize an operation with less refrigerant leakage while further suppressing loss.
  • the refrigerant in the compression chamber 10 is discharged from the discharge port 5e (see FIG. 1) provided at the approximate center of the base plate 5d of the fixed scroll 5 to the discharge pressure chamber 2f in the sealed container 2, and is discharged from the discharge pipe 2e. It is leaked outside.
  • FIG. 3 shows the refrigerant flow in the compression chamber 10 during partial load operation in the compressor 1 according to the first embodiment, and is a view of the cross section of the compression chamber 10 as viewed from below to above.
  • FIG. 4 shows a state when the refrigerant in the compression chamber 10 starts to be compressed during partial load operation in the compressor 1 according to the first embodiment, and the cross section of the compression chamber 10 is viewed from above from below.
  • FIG. 3 shows the refrigerant flow in the compression chamber 10 during partial load operation in the compressor 1 according to the first embodiment, and is a view of the cross section of the compression chamber 10 as viewed from below to above.
  • FIG. 4 shows a state when the refrigerant in the compression chamber 10 starts to be compressed during partial load operation in the compressor 1 according to the first embodiment, and the cross section of the compression chamber 10 is viewed from above from below.
  • control pressure space 11d When the control pressure space 11d communicates with the suction pressure space via the low pressure side flow path 18b and the pressure switching device 18 shown in FIG. 1, the pressure in the control pressure space 11d (see FIG. 2A) is in the compression chamber communicating with the bypass port 5b.
  • the pressure is equal to or less than the pressure of 10, and the gas load in the direction of closing the valve does not act on the bypass valve 11.
  • the refrigerant When the orbiting scroll 6 turns through the eccentric portion 9b of the crankshaft 9 driven by the electric motor 4, the refrigerant is introduced into the compression chamber 10 through the suction pipe 2d and the suction port 5a shown in FIG. .
  • the refrigerant tends to be compressed as the volume of the compression chamber 10 decreases.
  • the compression chamber 10 becomes completely in communication with the bypass port 5b. It becomes a closed space and starts to compress the refrigerant. After the refrigerant is compressed, the compressed refrigerant is discharged from the discharge port 5e to the discharge pressure chamber 2f (see FIG. 1) and flows out from the discharge pipe 2e to the outside in the same way as during full load operation.
  • the compressor 1 can be operated with a more appropriate partial load.
  • the said structure has the sealing member 11b which isolates the compression chamber 10 and the exterior of the bypass port 5b in pressure, and the bypass valve 11 has a shape which can protrude rather than the tooth bottom 5s of the fixed scroll 5.
  • the port insertion portion 11a at the tip of the bypass valve 11 that is pressed against the orbiting scroll 6 by a high-pressure refrigerant and closes the space between the compression chamber 10 and the suction chamber 10a in contact with the orbiting scroll 6 in the bypass valve 11 during full load operation.
  • the bypass port 5 b is more preferably provided at a position communicating with the oil supply hole 5 g via the compression chamber 10. At this time, oil is more easily supplied to the bypass port 5b from the oil supply hole 5g via the compression chamber 10, and at the time of full load operation, the distal end portion of the port insertion portion 11a of the bypass valve 11 and the wrap 6a of the orbiting scroll 6 are provided. An oil film between the two is more easily formed. Therefore, a scroll compressor with higher reliability can be realized. As described above, by using an appropriate rotational speed in accordance with the state of the mechanical capacity control, a highly efficient scroll compressor can be provided in a wide operation range.
  • FIG. 5 is a longitudinal sectional view of the compressor 21 according to the second embodiment.
  • the compressor 21 according to the second embodiment has a high-pressure channel 18a connected to the pressure switching device 19 from the discharge pipe 2e connected to the back pressure chamber 14 in the first embodiment. It is characterized in that it has been changed to.
  • the back pressure can be supplied from the pressure switching device 19 to the control pressure space 11d as a pressure between the discharge pressure and the suction pressure without providing a special mechanism such as a decompression device in the pressure switching device 19. It becomes possible. Therefore, it is possible to reduce the force for pressing the bypass valve 11 against the orbiting scroll 6 with a simpler structure. Therefore, it is possible to realize a highly efficient operation with less friction loss.
  • FIG. 6 is a longitudinal sectional view of the compressor 31 according to the third embodiment. Compared with the compressor 1 according to the first embodiment, the compressor 31 according to the third embodiment is characterized in that a throttle portion 17a is provided in the control pipe 17.
  • FIG. 7 is a longitudinal sectional view showing the periphery of the bypass valve 41 of the first modification.
  • the bypass valve 41 (corresponding to the bypass valve 11 in FIG. 1) of Modification 1 is provided with a ring-shaped seal member 41b such as rubber or the like in the non-wrap side cylindrical groove 5b1 of the bypass port 5b.
  • the seal member 41b may be provided on the fixed scroll 5 side.
  • the seal member 41b is provided at a position where contact with the bypass valve 41 is not removed even when the bypass valve 41 is moved up and down.
  • FIG. 8 is a longitudinal sectional view showing the periphery of the bypass valve 51 of the second modification.
  • a bypass valve 51 (corresponding to the bypass valve 11 in FIG. 1) of Modification 2 is provided with a ring-shaped seal member 51 b made of rubber or the like in the port insertion portion 51 a of the bypass valve 51.
  • the seal member may be provided in the port insertion portion 51a of the bypass valve 51.
  • the seal member 51b is provided at a position that does not come off from the lap side cylindrical groove 5b2 of the fixed scroll 5 even if the bypass valve 51 is moved up and down.
  • FIG. 9 is a longitudinal sectional view showing the periphery of the bypass valve 61 of the third modification.
  • the bypass valve 61 (corresponding to the bypass valve 11 in FIG. 1) of Modification 3 is provided with a ring-shaped seal member 61b such as rubber or the like in the wrap side cylindrical groove 5b2 of the bypass port 5b. That is, the sealing member 61b may be provided in the wrap-side cylindrical groove 5b2 on the fixed scroll 5 side so as to be sealed by the port insertion portion 61a.
  • the seal member 61b is provided at a position where it does not come off the port insertion portion 61a of the bypass valve 61 even if the bypass valve 61 moves up and down.
  • the sealing member 61b of the lap side cylindrical groove 5b2 is brought into close contact with the port insertion portion 61a of the bypass valve 61. Therefore, even when the bypass valve 61 moves up and down, the refrigerant in the pressure chamber 10 can be prevented from leaking from between the bypass port 5 b and the bypass valve 61.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne un compresseur à spirale (1) pourvu d'un récipient fermé (2) dans lequel sont logés des spirales orbitale et fixe (6, 5), une chambre de compression (10), une chambre d'aspiration (10a), un moteur électrique (4) et un mécanisme de dérivation. Le mécanisme de dérivation comprend : un orifice de dérivation (5b) formé dans la spirale fixe (5) et apte à assurer une communication entre les chambres de compression et d'aspiration (10, 10a) ; une soupape de dérivation (11) qui est disposée à l'intérieur de l'orifice de dérivation (5b), est pressée par un élément élastique (11c) dans la direction opposée à la spirale fixe (5), et peut ouvrir et fermer la communication entre les chambres de compression et d'aspiration (10, 10a) ; et un élément d'étanchéité (11b) destiné à séparer la chambre de compression (10) et un dispositif de commutation de pression (18) l'un de l'autre en termes de pression. La soupape de dérivation (11) est formée pour faire saillie plus loin que la surface inférieure de dent (5s) de la spirale fixe (5) et est pressée contre la spirale orbitale (6) pendant une opération à pleine charge pour fermer la communication entre la chambre de compression (10) et la chambre d'aspiration (10a). L'extrémité avant (11a) de la soupape de dérivation (11), qui vient en contact avec la spirale orbitale (6), a une résistance à l'usure supérieure ou égale à celle de la spirale orbitale (6).
PCT/JP2017/037758 2016-11-08 2017-10-18 Compresseur à spirale WO2018088154A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016217758A JP2018076791A (ja) 2016-11-08 2016-11-08 スクロール圧縮機
JP2016-217758 2016-11-08

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WO2018088154A1 true WO2018088154A1 (fr) 2018-05-17

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PCT/JP2017/037758 WO2018088154A1 (fr) 2016-11-08 2017-10-18 Compresseur à spirale

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JPS6078997U (ja) * 1983-11-07 1985-06-01 サンデン株式会社 スクロ−ル型圧縮機
JPH025917B2 (fr) * 1983-10-03 1990-02-06 Hitachi Ltd
JPH0381588A (ja) * 1989-08-23 1991-04-05 Hitachi Ltd スクロール圧縮機の容量制御装置
JPH09170573A (ja) * 1995-12-19 1997-06-30 Daikin Ind Ltd スクロール形流体機械
JP2553033Y2 (ja) * 1989-12-08 1997-11-05 株式会社豊田自動織機製作所 容量可変スクロール型圧縮機
JP2007154762A (ja) * 2005-12-05 2007-06-21 Daikin Ind Ltd スクロール圧縮機

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH025917B2 (fr) * 1983-10-03 1990-02-06 Hitachi Ltd
JPS6078997U (ja) * 1983-11-07 1985-06-01 サンデン株式会社 スクロ−ル型圧縮機
JPH0381588A (ja) * 1989-08-23 1991-04-05 Hitachi Ltd スクロール圧縮機の容量制御装置
JP2553033Y2 (ja) * 1989-12-08 1997-11-05 株式会社豊田自動織機製作所 容量可変スクロール型圧縮機
JPH09170573A (ja) * 1995-12-19 1997-06-30 Daikin Ind Ltd スクロール形流体機械
JP2007154762A (ja) * 2005-12-05 2007-06-21 Daikin Ind Ltd スクロール圧縮機

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