WO2017006454A1 - Compresseur et dispositif à cycle de réfrigération - Google Patents

Compresseur et dispositif à cycle de réfrigération Download PDF

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Publication number
WO2017006454A1
WO2017006454A1 PCT/JP2015/069614 JP2015069614W WO2017006454A1 WO 2017006454 A1 WO2017006454 A1 WO 2017006454A1 JP 2015069614 W JP2015069614 W JP 2015069614W WO 2017006454 A1 WO2017006454 A1 WO 2017006454A1
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WO
WIPO (PCT)
Prior art keywords
discharge port
compression mechanism
compressor
piston
refrigerant
Prior art date
Application number
PCT/JP2015/069614
Other languages
English (en)
Japanese (ja)
Inventor
勝俊 辰己
宏樹 長澤
寿史 柬理
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2017527029A priority Critical patent/JP6407432B2/ja
Priority to PCT/JP2015/069614 priority patent/WO2017006454A1/fr
Priority to CN201620384435.5U priority patent/CN205618364U/zh
Priority to CN201610285600.6A priority patent/CN106337814B/zh
Publication of WO2017006454A1 publication Critical patent/WO2017006454A1/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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • 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
    • 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 compressor and a refrigeration cycle apparatus.
  • the hermetic rotary compressor includes a hermetic container, a compression mechanism that is housed in the lower part of the hermetic container, and an electric motor that is housed in the upper part of the hermetic container and drives the compression mechanism.
  • the compression mechanism includes a cylindrical cylinder, a bearing that closes the upper and lower ends of the cylinder, and a ring-shaped piston accommodated in the cylinder.
  • the bearing supports a crankshaft that transmits the rotational force of the electric motor to the compression mechanism.
  • the bearing is provided with a discharge port for discharging compressed gas.
  • the piston is fitted into the eccentric part of the crankshaft.
  • the crankshaft rotates in synchronization with the rotation of the rotor of the electric motor, whereby the piston rotates eccentrically, and the volume of the compression chamber in the cylinder changes.
  • the refrigerant is sucked into the compression chamber and compressed.
  • the compressed refrigerant is discharged from the outlet of the bearing.
  • the discharged refrigerant passes through the upper part of the sealed container and is discharged as a high-pressure refrigerant to the outside of the sealed container.
  • the outlet of the bearing be arranged so as to satisfy the following conditions.
  • Condition 1 The discharge port does not interfere with a plurality of bolts used for fastening the cylinder and the bearing and a hole into which the plurality of bolts are inserted.
  • Condition 2 When the compression chamber is formed in the cylinder, the space inside the inner periphery of the piston and the discharge port are not connected.
  • Condition 3 The area of the discharge port is the optimum area.
  • condition 1 If the condition 1 is not satisfied, the cylinder and the bearing are fastened with only some bolts, and the reliability of the compression mechanism is lowered.
  • condition 2 If condition 2 is not satisfied, the high-pressure refrigerant will flow into the low-pressure space through the inside of the piston, causing a compression loss.
  • condition 3 If the condition 3 is not satisfied, the flow path resistance at the discharge port increases and overcompression occurs. As a result, the work of the compression operation increases and the performance of the compression mechanism decreases.
  • the cylinder is flattened and the piston of the piston is flattened in order to achieve high efficiency of the compression mechanism and large capacity in a small-diameter sealed container while maintaining the reliability of the compression mechanism.
  • the amount of eccentricity tends to increase.
  • the discharge port is enlarged in a circular or oval shape, the seal length with the piston is reduced, making it difficult to satisfy the condition 2.
  • the efficiency of the hermetic rotary compressor is reduced. If the center of the discharge port is moved outward, the seal length with the piston can be secured, but it becomes difficult to satisfy the condition 1. As a result, the reliability of the hermetic rotary compressor is lowered.
  • the “seal length with the piston” is the distance between the discharge port and the inner periphery of the piston.
  • the possibility of breakage of the discharge valve which is a valve attached to the discharge port, increases. Specifically, when the discharge valve is raised, stress concentrates on a part of the discharge valve, or the impact stress increases when the discharge valve is seated, and thus the discharge valve may be damaged. As a result, the reliability of the hermetic rotary compressor is lowered.
  • An object of the present invention is to enable an increase in capacity of a compressor while maintaining the reliability and efficiency of the compressor.
  • a compressor according to an aspect of the present invention is provided.
  • a compression mechanism in which a space for compressing the refrigerant and a discharge port for discharging the refrigerant compressed in the space are formed;
  • the discharge valve which consists of these.
  • the width of the opening region of the discharge port at a position facing the intermediate portion of the compression mechanism is smaller than the width of the opening region of the discharge port at a position facing the tip portion of the compression mechanism.
  • the capacity of the compressor can be increased.
  • the fact that the discharge port is closed by the middle part of the discharge valve means that the stress concentration on a part of the discharge valve and the increase of impact stress when the discharge valve is seated are suppressed, and the discharge valve is less likely to break. That's what it means. Therefore, the reliability of the compressor can be maintained.
  • the width of the opening area of the discharge port is reduced at the position blocked by the intermediate portion of the discharge valve, the seal length with the piston can be ensured. Therefore, the efficiency of the compressor can also be maintained.
  • FIG. 1 is a circuit diagram of a refrigeration cycle apparatus according to Embodiment 1.
  • FIG. 1 is a circuit diagram of a refrigeration cycle apparatus according to Embodiment 1.
  • FIG. 1 is a longitudinal sectional view of a compressor according to Embodiment 1.
  • FIG. 2 is a plan view of a discharge valve of the compressor according to Embodiment 1.
  • FIG. 3 is a partial cross-sectional view of the compressor according to the first embodiment. 2 is a cross-sectional view of the compressor according to the first embodiment, taken along the line AA.
  • FIG. 4 is a partial cross-sectional view of a compressor according to a second embodiment.
  • Embodiment 1 FIG. The configuration of the apparatus and the device according to the present embodiment, the operation of the device according to the present embodiment, and the effects of the present embodiment will be described in order.
  • FIG. 1 shows the refrigerant circuit 11 during the cooling operation.
  • FIG. 2 shows the refrigerant circuit 11 during heating operation.
  • the refrigeration cycle apparatus 10 is an air conditioner in the present embodiment, but may be an apparatus other than an air conditioner such as a refrigerator or a heat pump cycle apparatus.
  • the refrigeration cycle apparatus 10 includes a refrigerant circuit 11 in which a refrigerant circulates.
  • the refrigerant circuit 11 includes a compressor 12, a four-way valve 13, a first heat exchanger 14 that is an outdoor heat exchanger, an expansion mechanism 15 that is an expansion valve, and a second heat exchanger that is an indoor heat exchanger. 16 is connected.
  • the compressor 12 compresses the refrigerant.
  • the four-way valve 13 switches the direction in which the refrigerant flows between the cooling operation and the heating operation.
  • the first heat exchanger 14 operates as a condenser during the cooling operation, and dissipates the refrigerant compressed by the compressor 12.
  • the first heat exchanger 14 operates as an evaporator during the heating operation, and heats the refrigerant by exchanging heat between the outdoor air and the refrigerant expanded by the expansion mechanism 15.
  • the expansion mechanism 15 expands the refrigerant radiated by the condenser.
  • the second heat exchanger 16 operates as a condenser during the heating operation, and dissipates heat from the refrigerant compressed by the compressor 12.
  • the second heat exchanger 16 operates as an evaporator during the cooling operation, and heats the refrigerant by exchanging heat between the indoor air and the refrigerant expanded by the expansion mechanism 15.
  • the refrigeration cycle apparatus 10 further includes a control device 17.
  • the control device 17 is specifically a microcomputer. 1 and 2 show only the connection between the control device 17 and the compressor 12, the control device 17 is connected not only to the compressor 12 but also to each element connected to the refrigerant circuit 11. The control device 17 monitors and controls the state of each element.
  • any refrigerant such as R32 refrigerant, R290 (propane) refrigerant, R407C refrigerant, R410A refrigerant, R744 (CO2) refrigerant, R1234yf refrigerant, or the like can be used.
  • FIG. 3 shows a longitudinal section of the compressor 12. In FIG. 3, hatching representing a cross section is omitted.
  • the compressor 12 is a two-cylinder rotary compressor in the present embodiment, but may be a one-cylinder rotary compressor, a three-cylinder or more rotary compressor, or a scroll compressor.
  • the compressor 12 includes a sealed container 20, a compression mechanism 30, an electric motor 40, a crankshaft 50, and a discharge valve 60.
  • the sealed container 20 is provided with a suction pipe 21 for sucking refrigerant and a discharge pipe 22 for discharging refrigerant.
  • the compression mechanism 30 is housed inside the sealed container 20. Specifically, the compression mechanism 30 is installed in the lower part inside the sealed container 20. The compression mechanism 30 is driven by the electric motor 40. The compression mechanism 30 compresses the refrigerant sucked into the suction pipe 21.
  • the electric motor 40 is also housed inside the sealed container 20. Specifically, the electric motor 40 is installed at the upper part inside the sealed container 20. In this embodiment, the electric motor 40 is a concentrated winding motor, but may be a distributed winding motor.
  • Refrigerator oil for lubricating the sliding portions of the compression mechanism 30 is stored at the bottom of the sealed container 20. As the crankshaft 50 rotates, the refrigeration oil is pumped up by an oil pump provided at the lower portion of the crankshaft 50 and supplied to each sliding portion of the compression mechanism 30.
  • synthetic oils such as POE (polyol ester), PVE (polyvinyl ether), and AB (alkylbenzene) are used.
  • the electric motor 40 is a brushless DC (Direct Current) motor, but may be a motor other than a brushless DC motor, such as an induction motor.
  • DC Direct Current
  • the electric motor 40 includes a cylindrical stator 41 and a columnar rotor 42.
  • the stator 41 is fixed in contact with the inner peripheral surface of the sealed container 20.
  • the rotor 42 is installed inside the stator 41 with a gap of about 0.3 to 1.0 millimeter.
  • the stator 41 includes a stator core 43 and a winding 44.
  • the stator core 43 is formed by punching a plurality of electromagnetic steel sheets having a thickness of 0.1 to 1.5 millimeters, each having a thickness of 0.1 to 1.5 mm, laminated in the axial direction, and fixed by caulking or welding. Produced.
  • the winding 44 is wound around the stator core 43 in a concentrated manner through an insulating member.
  • the winding 44 is composed of a core wire and at least one layer of a coating covering the core wire.
  • the material of the core wire is copper.
  • the material of the coating is AI (amidoimide) / EI (ester imide).
  • the material of the insulating member is PET (polyethylene terephthalate).
  • the material of the core wire may be aluminum.
  • the insulating member is made of PBT (polybutylene terephthalate), FEP (tetrafluoroethylene / hexafluoropropylene copolymer), PFA (tetrafluoroethylene / perfluoroalkyl vinyl ether copolymer), PTFE (polytetrafluoroethylene), LCP (liquid crystal polymer), PPS (polyphenylene sulfide), or phenol resin may be used.
  • One end of a lead wire (not shown) is connected to the winding 44.
  • the rotor 42 includes a rotor core 46 and a permanent magnet (not shown).
  • the rotor core 46 is formed by punching a plurality of electromagnetic steel sheets with a thickness of 0.1 to 1.5 millimeters into a fixed shape and laminating them in the axial direction. However, it is manufactured by fixing by caulking or welding.
  • the permanent magnet is inserted into a plurality of insertion holes formed in the rotor core 46.
  • the permanent magnet forms a magnetic pole.
  • a ferrite magnet or a rare earth magnet is used as the permanent magnet.
  • a shaft hole into which the main shaft portion 52 of the crankshaft 50 is shrink-fitted or press-fitted is formed at the center of the rotor core 46 in plan view.
  • a plurality of through holes penetrating in the axial direction are formed around the shaft hole of the rotor core 46. Each through hole serves as one of the passages of the gas refrigerant that is discharged from the discharge muffler 36 to the space in the sealed container 20.
  • the motor 40 when configured as an induction motor, a plurality of slots formed in the rotor core 46 are filled or inserted with a conductor formed of aluminum, copper, or the like. A squirrel-cage winding in which both ends of the conductor are short-circuited by end rings is formed.
  • a terminal 24 connected to an external power source such as an inverter device is attached to the top of the sealed container 20.
  • the terminal 24 is specifically a glass terminal.
  • the terminal 24 is fixed to the sealed container 20 by welding.
  • the terminal 24 is connected to the other end of the lead wire described above. Thereby, the terminal 24 and the winding 44 of the electric motor 40 are electrically connected.
  • a discharge pipe 22 having both axial ends opened is attached at the top of the sealed container 20.
  • the gas refrigerant discharged from the compression mechanism 30 is discharged from the space in the sealed container 20 through the discharge pipe 22 to the external refrigerant circuit 11.
  • the discharge valve 60 includes a fixed part 61, an intermediate part 62, and a tip part 63.
  • the discharge valve 60 is integrally formed of a longitudinal plate member, one end in the longitudinal direction is a fixed portion 61, the middle in the longitudinal direction is an intermediate portion 62, and the other end in the longitudinal direction is This is the tip 63.
  • the fixing unit 61 is fixed to the compression mechanism 30.
  • a through hole 64 is provided in the fixing portion 61, and the fixing portion 61 is fixed to the compression mechanism 30 by a fixing tool such as a screw inserted into the through hole 64.
  • the intermediate part 62 connects the fixing part 61 and the tip part 63.
  • the width x of the intermediate portion 62 is smaller than the width w of the fixed portion 61.
  • the distal end portion 63 has a neck portion 65 which is a portion connected to the intermediate portion 62.
  • the width direction dimension of the tip portion 63 gradually increases from the side connected to the intermediate portion 62 toward the opposite side, and gradually decreases from the middle.
  • the portion in which the width direction dimension gradually decreases has a semicircular shape in plan view. The length of the diameter of this portion is equal to the maximum value in the width direction dimension of the tip portion 63, that is, the width y of the tip portion 63.
  • FIG. 5 shows a partial cross section of the compressor 12.
  • hatching representing a cross section is omitted.
  • the fastener 37 and the discharge valve 60 are omitted, and only a part of the compression mechanism 30 and the crankshaft 50 are shown.
  • FIG. 6 shows a cut surface when the compression mechanism 30 is cut along the line AA shown in FIG.
  • hatching representing a cross section is omitted except for a part.
  • the crankshaft 50 is also omitted.
  • the compression mechanism 30 includes a suction port 71 for sucking gas refrigerant from the refrigerant circuit 11, a space 72 for compressing the refrigerant sucked from the suction port 71, and a refrigerant compressed in the space 72 as a refrigerant circuit. 11 is formed.
  • the compression mechanism 30 includes a cylinder 31, a piston 32, a vane 33, a main bearing 34, and a sub bearing 35.
  • the compressor 12 is a two-cylinder rotary compressor, there are one cylinder 31, one piston 32, and one vane 33 at each of the upper part and the lower part.
  • the inner circumference 75 of the cylinder 31 is circular in plan view.
  • a cylinder chamber 76 that is a circular space in plan view is formed inside the cylinder 31.
  • the cylinder 31 is open at both axial ends.
  • the cylinder 31 is provided with a vane groove 77 that is connected to the cylinder chamber 76 and extends in the radial direction.
  • a back pressure chamber that is a circular space in plan view connected to the vane groove 77 is formed outside the vane groove 77.
  • the piston 32 has a ring shape. Therefore, the inner periphery 78 and the outer periphery 79 of the piston 32 are circular in plan view.
  • the piston 32 rotates eccentrically in the cylinder chamber 76.
  • the piston 32 is slidably fitted to the eccentric shaft portion 51 of the crankshaft 50 that serves as the rotation shaft of the piston 32.
  • the vane 33 has a plate shape with a rounded tip.
  • the vane 33 is installed in the vane groove 77 of the cylinder 31.
  • the vane 33 is always pressed against the piston 32 by a vane spring provided in the back pressure chamber. Since the inside of the sealed container 20 is at a high pressure, when the operation of the compressor 12 is started, a difference between the pressure in the sealed container 20 and the pressure in the cylinder chamber 76 is caused on the back surface of the vane 33 on the back pressure chamber side. Force acts.
  • the vane spring is used mainly for the purpose of pressing the vane 33 against the piston 32 at the time of starting the compressor 12 in which there is no difference in pressure between the sealed container 20 and the cylinder chamber 76.
  • the main bearing 34 has an inverted T shape when viewed from the side.
  • the main bearing 34 is slidably fitted to a main shaft portion 52 that is a portion above the eccentric shaft portion 51 of the crankshaft 50.
  • the main bearing 34 closes the upper side of the cylinder chamber 76 and the vane groove 77 of the cylinder 31.
  • the secondary bearing 35 is T-shaped when viewed from the side.
  • the sub-bearing 35 is slidably fitted to a sub-shaft portion 53 that is a portion below the eccentric shaft portion 51 of the crankshaft 50.
  • the secondary bearing 35 closes the cylinder chamber 76 and the lower side of the vane groove 77 of the cylinder 31.
  • the suction port 71 is connected to the cylinder chamber 76 from the outer peripheral surface of the cylinder 31.
  • a space 72 for compressing the refrigerant is formed inside the inner periphery 75 of the cylinder 31 and outside the outer periphery 79 of the piston 32. That is, the space 72 for compressing the refrigerant is formed between the inner periphery 75 of the cylinder 31 and the outer periphery 79 of the piston 32.
  • the vane 33 partitions the space 72 into a low-pressure suction chamber and a high-pressure compression chamber at a ratio corresponding to the rotational position of the piston 32.
  • the discharge port 73 is formed in two bearings, a main bearing 34 and a sub bearing 35. In each bearing, the discharge port 73 is formed on the side opposite to the side where the suction port 71 is located across the center line of the vane 33. That is, the discharge port 73 is formed at a position connected to the compression chamber when the space 72 of the compression mechanism 30 is partitioned by the vane 33 into the suction chamber and the compression chamber.
  • a circular fastening hole 81 is further formed in each bearing.
  • Each bearing is fixed to the cylinder 31 by a fastener 37 inserted into the fastening hole 81, and supports a crankshaft 50 that is a rotation shaft of the piston 32.
  • the main bearing 34 is fixed to the upper cylinder 31.
  • the sub bearing 35 is fixed to the lower cylinder 31.
  • the fastener 37 is a combination of a bolt and a nut.
  • the number of fastening holes 81 may be adjusted as appropriate, but a plurality of fastening holes 81 are required for each bearing.
  • a valve groove 82 is also formed in each bearing.
  • the valve groove 82 includes a shallow groove portion 83 and a deep groove portion 84.
  • the fixing portion 61 of the discharge valve 60 is housed and fixed.
  • a discharge port 73 is provided at the bottom of the deep groove portion 84.
  • the deep groove portion 84 accommodates the intermediate portion 62 and the tip portion 63 of the discharge valve 60.
  • the distal end portion 63 closes the discharge port 73 so as to be freely opened and closed.
  • the intermediate part 62 closes the discharge port 73 together with the tip part 63 so as to be freely opened and closed.
  • the intermediate part 62 and the tip part 63 contact the end surface of the peripheral wall part 74 of the discharge port 73 when the discharge port 73 is closed.
  • the thickness of the peripheral wall 74 of the discharge port 73 is constant.
  • the height of the peripheral wall portion 74 of the discharge port 73 is equal to the difference in depth between the shallow groove portion 83 and the deep groove portion 84. That is, the end surface of the peripheral wall portion 74 of the discharge port 73 is at the same position as the bottom surface of the deep groove portion 84 in the height direction of the peripheral wall portion 74.
  • the intermediate portion 62 may be disposed across the shallow groove portion 83 and the deep groove portion 84.
  • a discharge muffler 36 is attached to the outside of each bearing.
  • the high-temperature and high-pressure gas refrigerant discharged through the discharge valve 60 once enters the discharge muffler 36 and is then discharged from the discharge muffler 36 into the space in the sealed container 20.
  • the discharge valve 60 and the discharge muffler 36 may be provided only in one of the main bearing 34 and the sub-bearing 35.
  • the material of the cylinder 31, the main bearing 34, and the sub bearing 35 is sintered steel, but may be gray cast iron or carbon steel.
  • the material of the piston 32 is alloy steel containing chromium or the like.
  • the material of the vane 33 is high-speed tool steel.
  • a suction muffler 23 is provided beside the sealed container 20.
  • the suction muffler 23 sucks low-pressure gas refrigerant from the refrigerant circuit 11.
  • the suction muffler 23 prevents the liquid refrigerant from directly entering the cylinder chamber 76 of the cylinder 31 when the liquid refrigerant returns.
  • the suction muffler 23 is connected to the suction port 71 via the suction pipe 21.
  • the main body of the suction muffler 23 is fixed to the side surface of the sealed container 20 by welding or the like.
  • the discharge port 73 is so large that it is blocked not only by the tip portion 63 of the discharge valve 60 but also by the intermediate portion 62 of the discharge valve 60. Therefore, the capacity of the compressor 12 can be increased.
  • the discharge port 73 is made circular or oval and is made large enough to be blocked by the intermediate portion 62, not only the seal length f with the piston 32 is reduced, but also a compression chamber is formed in the cylinder 31. At this time, the space inside the inner periphery 78 of the piston 32 and the discharge port 73 may be connected.
  • the width a of the opening region of the discharge port 73 at the position facing the intermediate portion 62 of the compression mechanism 30 is equal to the opening region of the discharge port 73 at the position facing the tip portion 63 of the compression mechanism 30. It is smaller than the width b. Therefore, the seal length f with the piston 32 can be ensured. Therefore, the efficiency of the compressor 12 can also be maintained.
  • the width a is smaller than the width x of the intermediate portion 62.
  • the width b is smaller than the width y of the tip portion 63.
  • the opening area of the discharge port 73 at a position facing the intermediate portion 62 of the compression mechanism 30 gradually decreases toward a position facing the fixed portion 61 of the compression mechanism 30. Therefore, the discharge port 73 can be enlarged while ensuring the seal length f with the piston 32. When the cylinder 31 is flattened, the thickness of the piston 32 is reduced.
  • the area of the opening region of the discharge port 73 can be optimized while avoiding structural limitations. .
  • the opening region of the discharge port 73 has a shape in which two circles having different diameters are connected by two lines having contact points on both of the two circles. Of the two circles, the larger circle is at a position facing the tip portion 63 of the compression mechanism 30, and the smaller circle is at a position facing the intermediate portion 62 of the compression mechanism 30.
  • a part of the opening region of the discharge port 73 is curved in an arc shape concentric with the inner periphery 78 of the piston 32 when the entire space 72 of the compression mechanism 30 is in a rotational position where it becomes a suction chamber.
  • one of the two lines is an arc concentric with the inner periphery 78 of the piston 32 when the entire space 72 of the compression mechanism 30 is in a rotational position that serves as a suction chamber.
  • the entire vane 33 is accommodated in the vane groove 77.
  • the opening region of the discharge port 73 has a shape in which another part is curved in an arc shape concentric with the circumference of the fastening hole 81. That is, the other of the two lines is an arc concentric with the circumference of the fastening hole 81.
  • the fastening hole 81 is outside the inner periphery 75 of the cylinder 31 and avoids the valve groove 82 including the suction port 71, the vane groove 77, and the discharge port 73. Must be placed in a different position.
  • the main bearing 34 and the upper cylinder 31 are fastened, the upper cylinder 31 and the lower cylinder 31 are fastened, and the lower cylinder 31 and the sub-bearing 35 are fastened. It is necessary to ensure. Therefore, it is desirable that the fastening holes 81 are provided at an equal pitch.
  • the fastening hole 81 is provided as close to the inner periphery 75 of the cylinder 31 as possible.
  • the fastening hole 81 is arranged so as to satisfy all of the above requirements, it does not interfere with the fastening hole 81, the seal length f with the piston 32 can be secured, and the opening A discharge port 73 in which the area of the region is the optimum area can be provided in each bearing. That is, the discharge port 73 can be disposed so as to satisfy all of the above-described condition 1, condition 2, and condition 3.
  • the discharge port 73 is disposed inside the piston 32 when the circumference of one fastening hole 81 and the entire space 72 of the compression mechanism 30 are in a rotational position that becomes a suction chamber. It can be arranged between the circumference 78.
  • One side of the opening region of the discharge port 73 is curved along the circumference of the adjacent fastening hole 81 while maintaining a certain distance from the circumference of the adjacent fastening hole 81.
  • Another side of the opening region is along the inner periphery 78 of the piston 32 while maintaining a certain distance from the inner periphery 78 of the piston 32 when the entire space 72 of the compression mechanism 30 is in the rotational position to be the suction chamber. Is curved.
  • the amount g applied to the portion of the discharge port 73 on the inner side of the inner periphery 75 of the cylinder 31 is g ⁇ D It is necessary to satisfy the condition / 2 ⁇ (e + d / 2).
  • This condition is a condition for the discharge port 73 to ensure the seal length f with the piston 32. By satisfying this condition, the high-pressure refrigerant can be prevented from flowing into the low-pressure space inside the inner periphery 78 of the piston 32.
  • Electric power is supplied from the terminal 24 to the stator 41 of the electric motor 40 via the lead wire.
  • a current flows through the winding 44 of the stator 41 and a magnetic flux is generated from the winding 44.
  • the rotor 42 of the electric motor 40 rotates by the action of the magnetic flux generated from the winding 44 and the magnetic flux generated from the permanent magnet of the rotor 42.
  • the crankshaft 50 fixed to the rotor 42 rotates.
  • the piston 32 of the compression mechanism 30 rotates eccentrically in the cylinder chamber 76 of the cylinder 31 of the compression mechanism 30.
  • a space 72 between the cylinder 31 and the piston 32 is divided into a suction chamber and a compression chamber by a vane 33 of the compression mechanism 30.
  • the crankshaft 50 rotates, the volume of the suction chamber and the volume of the compression chamber change.
  • the volume gradually increases, whereby low-pressure gas refrigerant is sucked from the suction muffler 23.
  • the compression chamber the gas refrigerant therein is compressed by gradually reducing the volume.
  • the compressed, high-pressure and high-temperature gas refrigerant is discharged from the discharge muffler 36 into the space in the sealed container 20.
  • the discharged gas refrigerant further passes through the electric motor 40 and is discharged out of the sealed container 20 from the discharge pipe 22 at the top of the sealed container 20.
  • the refrigerant discharged to the outside of the sealed container 20 returns to the suction muffler 23 again through the refrigerant circuit 11.
  • the vane 33 is provided integrally with the piston 32.
  • the crankshaft 50 is driven, the vane 33 enters and exits along a receiving groove of a support that is rotatably attached to the piston 32.
  • the vane 33 moves in the radial direction while swinging according to the rotation of the piston 32, thereby dividing the inside of the cylinder chamber 76 into a compression chamber and a suction chamber.
  • the support is composed of two columnar members having a semicircular cross section.
  • the support body is rotatably fitted in a circular holding hole formed in an intermediate portion between the suction port 71 and the discharge port 73 of the cylinder 31.
  • the discharge port 73 formed in the compression mechanism 30 is large enough to be blocked not only by the distal end portion 63 of the discharge valve 60 but also by the intermediate portion 62 of the discharge valve 60, so that the capacity of the compressor 12 is increased. Is possible.
  • the fact that the discharge port 73 is closed by the intermediate portion 62 of the discharge valve 60 means that stress concentration on the neck 65 of the discharge valve 60 and an increase in impact stress when the discharge valve 60 is seated are suppressed. 60 is difficult to break. Therefore, the reliability of the compressor 12 can be maintained.
  • the seal length f with the piston 32 can be secured. Therefore, the efficiency of the compressor 12 can also be maintained.
  • the discharge port 73 having a shape formed by connecting two circles is formed to extend toward the fixed portion 61 of the discharge valve 60. For this reason, compared with a circular discharge port, the area where the discharge valve 60 receives the pressure of the discharged refrigerant increases on the fixed portion 61 side. Therefore, the discharge valve 60 rises smoothly, and it is possible to reduce stress concentration on the neck 65 caused by the difference in rigidity between the intermediate portion 62 and the tip portion 63 of the discharge valve 60. Further, the peripheral length of the discharge port 73 is longer than that of the circular discharge port. Therefore, when the discharge valve 60 is seated, the area where the discharge valve 60 comes into contact with the peripheral wall portion 74 of the discharge port 73 increases, and the impact stress can be reduced.
  • the discharge port 73 as a whole extends along the inner periphery 75 of the cylinder 31 to a position corresponding to the intermediate portion 62 of the discharge valve 60. Therefore, the area of the discharge port 73 can be easily secured even in the compression mechanism 30 that is housed in the small-diameter sealed container 20, the cylinder 31 is flattened, and the eccentric amount of the piston 32 is increased. Therefore, the performance of the compressor 12 is improved.
  • the opening area of the discharge port 73 formed in the compression mechanism 30 is such that an arbitrary first graphic and a non-circular second graphic are in contact with both the first graphic and the second graphic instead of two circles having different diameters. You may have the shape connected with two lines which have. The size of the first graphic is different from the size of the second graphic. Each of the first graphic and the second graphic may be a polygon or other shapes. The shape of the discharge valve 60 is appropriately changed according to the shape of the discharge port 73 so that the discharge port 73 can be closed.
  • Embodiment 2 FIG. In the present embodiment, differences from the first embodiment will be mainly described.
  • FIG. 7 corresponds to FIG.
  • the opening region of the discharge port 73 formed in the compression mechanism 30 has a shape in which two circles having different diameters are connected by two lines having contact points on both of the two circles. .
  • the larger circle is at a position facing the tip portion 63 of the compression mechanism 30, and the smaller circle is at a position facing the intermediate portion 62 of the compression mechanism 30.
  • the two lines are tangents of the two circles.
  • One side of the opening area of the discharge port 73 extends linearly away from the circumference of the adjacent fastening hole 81.
  • the other side of the open region extends linearly away from the inner periphery 78 of the piston 32 when the entire space 72 of the compression mechanism 30 is in the rotational position serving as the suction chamber.
  • the fastening hole 81 is provided near the inner periphery 75 of the cylinder 31, interference between the discharge port 73 and the fastening hole 81 can be avoided, the seal length f with the piston 32 can be secured, and the discharge port
  • the opening area 73 can be sufficiently large although not as large as that of the first embodiment.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)

Abstract

La présente invention concerne un compresseur doté d'un mécanisme de compression et d'une soupape de refoulement. La soupape de refoulement comprend : une section fixe fixée au mécanisme de compression ; une section d'extrémité avant pour fermer un orifice d'évacuation (73) de manière ouvrable et fermable, l'orifice d'évacuation (73) évacuant un réfrigérant ayant été comprimé dans un espace (72) dans le mécanisme de compression ; et une section intermédiaire pour connecter la section fixe et la section d'extrémité avant et fermer, conjointement avec la section d'extrémité avant, l'orifice d'évacuation (73) de manière ouvrable et fermable. La largeur a de la région d'ouverture de l'orifice d'évacuation (73) au niveau d'une position faisant face à la section intermédiaire de la soupape de refoulement du mécanisme de compression est inférieure à la largeur b de la région d'ouverture de l'orifice d'évacuation (73) au niveau d'une position faisant face à la section d'extrémité avant de la soupape de refoulement du mécanisme de compression.
PCT/JP2015/069614 2015-07-08 2015-07-08 Compresseur et dispositif à cycle de réfrigération WO2017006454A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2017527029A JP6407432B2 (ja) 2015-07-08 2015-07-08 圧縮機及び冷凍サイクル装置
PCT/JP2015/069614 WO2017006454A1 (fr) 2015-07-08 2015-07-08 Compresseur et dispositif à cycle de réfrigération
CN201620384435.5U CN205618364U (zh) 2015-07-08 2016-04-29 压缩机以及制冷循环装置
CN201610285600.6A CN106337814B (zh) 2015-07-08 2016-04-29 压缩机以及制冷循环装置

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023153704A1 (fr) * 2022-02-10 2023-08-17 삼성전자주식회사 Compresseur rotatif et appareil ménager le comprenant

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6407432B2 (ja) * 2015-07-08 2018-10-17 三菱電機株式会社 圧縮機及び冷凍サイクル装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05133363A (ja) * 1991-11-07 1993-05-28 Sanyo Electric Co Ltd 密閉型圧縮機
JPH06193574A (ja) * 1992-10-29 1994-07-12 Mitsubishi Electric Corp 可逆回転式圧縮機及び可逆冷凍サイクル
JP2009174522A (ja) * 2007-12-26 2009-08-06 Mitsubishi Electric Corp ロータリー圧縮機
JP2012255370A (ja) * 2011-06-08 2012-12-27 Toshiba Carrier Corp 回転式圧縮機及び冷凍サイクル装置
WO2013140912A1 (fr) * 2012-03-23 2013-09-26 東芝キヤリア株式会社 Compresseur rotatif et appareil de cycle de congélation

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN203962387U (zh) * 2014-07-02 2014-11-26 广东美芝制冷设备有限公司 制冷循环装置及其旋转式压缩机
CN204239263U (zh) * 2014-07-04 2015-04-01 广东美芝制冷设备有限公司 旋转式压缩机及具有其的制冷循环装置
JP6407432B2 (ja) * 2015-07-08 2018-10-17 三菱電機株式会社 圧縮機及び冷凍サイクル装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05133363A (ja) * 1991-11-07 1993-05-28 Sanyo Electric Co Ltd 密閉型圧縮機
JPH06193574A (ja) * 1992-10-29 1994-07-12 Mitsubishi Electric Corp 可逆回転式圧縮機及び可逆冷凍サイクル
JP2009174522A (ja) * 2007-12-26 2009-08-06 Mitsubishi Electric Corp ロータリー圧縮機
JP2012255370A (ja) * 2011-06-08 2012-12-27 Toshiba Carrier Corp 回転式圧縮機及び冷凍サイクル装置
WO2013140912A1 (fr) * 2012-03-23 2013-09-26 東芝キヤリア株式会社 Compresseur rotatif et appareil de cycle de congélation

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023153704A1 (fr) * 2022-02-10 2023-08-17 삼성전자주식회사 Compresseur rotatif et appareil ménager le comprenant

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JPWO2017006454A1 (ja) 2017-09-07
CN106337814B (zh) 2019-06-04
JP6407432B2 (ja) 2018-10-17
CN106337814A (zh) 2017-01-18

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