WO2021214913A1 - Compresseur - Google Patents

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Publication number
WO2021214913A1
WO2021214913A1 PCT/JP2020/017328 JP2020017328W WO2021214913A1 WO 2021214913 A1 WO2021214913 A1 WO 2021214913A1 JP 2020017328 W JP2020017328 W JP 2020017328W WO 2021214913 A1 WO2021214913 A1 WO 2021214913A1
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WO
WIPO (PCT)
Prior art keywords
discharge
notch
discharge hole
refrigerant
cylinder
Prior art date
Application number
PCT/JP2020/017328
Other languages
English (en)
Japanese (ja)
Inventor
明人 及川
勝俊 辰己
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 PCT/JP2020/017328 priority Critical patent/WO2021214913A1/fr
Publication of WO2021214913A1 publication Critical patent/WO2021214913A1/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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • This disclosure relates to a compressor that compresses a refrigerant.
  • a rotary compressor is known as a compressor that compresses and discharges a fluid such as a refrigerant.
  • a rotary type compressor an electric motor portion is provided in the upper part inside the closed container, and a compression mechanism portion is provided in the lower part inside the inside of the container.
  • the motor unit has a stator fixed to a container and a rotor that rotates when electric power is supplied to the stator. Then, the rotational force of the motor unit is transmitted to the compression mechanism unit by the rotating shaft fixed to the rotor.
  • the compression mechanism unit mainly has a cylinder fixed to the container and a piston attached to the inside of the cylinder and rotating eccentrically.
  • the compressor has a bearing that supports the rotating shaft. Then, the rotation of the rotating shaft causes the piston to rotate eccentrically, and the volume of the compression chamber formed between the cylinder and the piston is reduced, so that the refrigerant is compressed. Further, the refrigerating machine oil is stored in the bottom of the container, and the rotation of the rotating shaft takes the function of the centrifugal pump, and the refrigerating machine oil is sucked up into the oil passage formed in the axial direction inside the rotating shaft. Then, the refrigerating machine oil is supplied to each sliding portion of the compressor through an oil supply hole formed in the radial direction inside the rotating shaft.
  • the bearing is covered with a discharge muffler, and the compressed refrigerant is discharged from the discharge port provided in the bearing into the space between the bearing and the discharge muffler, and then from the gas hole formed in the discharge muffler. , Is discharged inside the container.
  • Patent Document 1 discloses a rotary compressor in which a discharge hole for discharging a refrigerant from a compression chamber formed in a cylinder is formed in a bearing.
  • the discharge hole of Patent Document 1 is inclined so that the edge portion of the communication portion communicating with the compression chamber extends along the axial direction, and the edge portion of the valve seat portion connected to the communication portion extends from the communication portion. That is, the inner peripheral generatrix from the inner bottom to the top of the valve seat is a straight line inclined from the inside to the outside in the radial direction.
  • Patent Document 1 attempts to facilitate the discharge of the refrigerant from the discharge holes.
  • a discharge notch connected to a discharge hole is cut out on the inner peripheral surface of the cylinder.
  • the notch direction of the discharge notch is inclined from the inner wall of the cylinder toward the discharge hole.
  • This disclosure is made to solve the above-mentioned problems, and provides a compressor that reduces pressure loss and suppresses a decrease in compression efficiency.
  • the compressor according to the present disclosure is fixed to the container, an electric motor portion provided inside the container, a rotating shaft fixed to the electric motor portion and driven to rotate by the electric motor portion, and fixed to the inner wall of the container to be formed inside.
  • An annular cylinder with a notch for discharging the refrigerant compressed by the compression chamber and an annular cylinder mounted on the cylinder to support the rotating shaft, and a compression chamber is formed together with the cylinder and connected to the discharge notch.
  • a bearing having a discharge hole extending along the notch direction of the discharge notch for discharging the refrigerant is provided.
  • the discharge hole extends along the notch direction of the discharge notch. Therefore, the refrigerant flowing along the discharge notch smoothly flows out into the discharge hole without colliding. Therefore, the pressure loss can be reduced and the decrease in compression efficiency can be suppressed.
  • FIG. 5 is an enlarged cross-sectional view showing a state in which the discharge hole in the first embodiment is viewed in the direction of the rotation axis. It is sectional drawing which shows the discharge notch and the discharge hole in the comparative example. FIG. 5 is an enlarged cross-sectional view showing a state in which the discharge hole in the comparative example is viewed in the direction of the rotation axis. It is sectional drawing which shows the discharge notch and the discharge hole in Embodiment 2.
  • FIG. FIG. 5 is an enlarged cross-sectional view showing a state in which the discharge hole in the second embodiment is viewed in the direction of the rotation axis.
  • FIG. 1 is a circuit diagram showing an air conditioner 1 according to the first embodiment.
  • the air conditioner 1 is a device for adjusting the air in the indoor space, and includes an outdoor unit 2 and an indoor unit 3 capable of communicating with the outdoor unit 2.
  • the outdoor unit 2 is provided with a compressor 6, a flow path switching device 7, an outdoor heat exchanger 8, an outdoor blower 9, and an expansion unit 10.
  • the indoor unit 3 is provided with an indoor heat exchanger 11 and an indoor blower 12.
  • the compressor 6, the flow path switching device 7, the outdoor heat exchanger 8, the expansion unit 10, and the indoor heat exchanger 11 are connected by a refrigerant pipe 5, and a refrigerant circuit 4 through which the refrigerant flows is configured.
  • the compressor 6 sucks in the refrigerant in a low temperature and low pressure state, compresses the sucked refrigerant into a refrigerant in a high temperature and high pressure state, and discharges the refrigerant.
  • the flow path switching device 7 switches the direction in which the refrigerant flows in the refrigerant circuit 4, and is, for example, a four-way valve.
  • the outdoor heat exchanger 8 exchanges heat between, for example, outdoor air and a refrigerant.
  • the outdoor heat exchanger 8 acts as a condenser during the cooling operation and as an evaporator during the heating operation.
  • the outdoor blower 9 is a device that sends outdoor air to the outdoor heat exchanger 8.
  • the expansion unit 10 is a pressure reducing valve or an expansion valve that decompresses and expands the refrigerant.
  • the expansion unit 10 is, for example, an electronic expansion valve whose opening degree is adjusted.
  • the indoor heat exchanger 11 exchanges heat between, for example, indoor air and a refrigerant.
  • the indoor heat exchanger 11 acts as an evaporator during the cooling operation and as a condenser during the heating operation.
  • the indoor blower 12 is a device that sends indoor air to the indoor heat exchanger 11.
  • cooling operation Next, the operation mode of the air conditioner 1 will be described.
  • the cooling operation In the cooling operation, the refrigerant sucked into the compressor 6 is compressed by the compressor 6 and discharged in a high temperature and high pressure gas state.
  • the high-temperature and high-pressure gas-state refrigerant discharged from the compressor 6 passes through the flow path switching device 7 and flows into the outdoor heat exchanger 8 acting as a condenser, and in the outdoor heat exchanger 8, the outdoor blower. It exchanges heat with the outdoor air sent by No. 9 and condenses and liquefies.
  • the condensed liquid refrigerant flows into the expansion section 10 and is expanded and depressurized in the expansion section 10 to become a low-temperature and low-pressure gas-liquid two-phase state refrigerant. Then, the refrigerant in the gas-liquid two-phase state flows into the indoor heat exchanger 11 that acts as an evaporator, and in the indoor heat exchanger 11, heat is exchanged with the indoor air sent by the indoor blower 12 to evaporate and gasify. do. At this time, the indoor air is cooled, and cooling is performed indoors. The evaporated low-temperature and low-pressure gas-like refrigerant passes through the flow path switching device 7 and is sucked into the compressor 6.
  • the heating operation In the heating operation, the refrigerant sucked into the compressor 6 is compressed by the compressor 6 and discharged in a high-temperature and high-pressure gas state.
  • the high-temperature and high-pressure gas-state refrigerant discharged from the compressor 6 passes through the flow path switching device 7 and flows into the indoor heat exchanger 11 acting as a condenser, and in the indoor heat exchanger 11, the indoor blower It exchanges heat with the indoor air sent by No. 12 and condenses and liquefies. At this time, the indoor air is warmed and heating is performed in the room.
  • the condensed liquid refrigerant flows into the expansion section 10 and is expanded and depressurized in the expansion section 10 to become a low-temperature and low-pressure gas-liquid two-phase state refrigerant. Then, the refrigerant in the gas-liquid two-phase state flows into the outdoor heat exchanger 8 that acts as an evaporator, and in the outdoor heat exchanger 8, heat is exchanged with the outdoor air sent by the outdoor blower 9 and evaporates to gasify. do.
  • the evaporated low-temperature and low-pressure gas-like refrigerant passes through the flow path switching device 7 and is sucked into the compressor 6.
  • FIG. 2 is a cross-sectional view showing the compressor 6 in the first embodiment.
  • the compressor 6 compresses the refrigerant, and as shown in FIG. 2, the container 20, the discharge pipe 22, the suction unit 23, the motor unit 24, the compression mechanism unit 30, the rotary shaft 25, and the like. It includes an oil separator 26, a bearing 40, a sub-bearing 50, a discharge muffler 27, and a sub-discharge muffler 28.
  • the compressor 6 is a rotary type compressor, and is a two-cylinder type compressor having two cylinders 31.
  • the container 20 is a hermetically sealed container that constitutes the outer shell of the compressor 6, and an oil sump 21 for collecting refrigerating machine oil is formed at the lower portion.
  • the refrigerating machine oil is supplied to each sliding portion of the compressor 6 to lubricate each sliding portion.
  • the discharge pipe 22 is provided in the upper part of the container 20 and discharges the compressed refrigerant to the outside of the container 20.
  • the suction unit 23 sucks the refrigerant into the container 20, and has a suction pipe 23a, a suction muffler 23b, and two outlet pipes 23c.
  • the suction pipe 23a is connected to an accumulator (not shown) or the like, and introduces the refrigerant flowing in from the accumulator or the like into the suction muffler 23b.
  • the suction muffler 23b is connected to the suction pipe 23a, separates and stores the liquid-state refrigerant among the refrigerants flowing in from the suction pipe 23a, and distributes the gas-state refrigerant to each outlet pipe 23c.
  • the two outlet pipes 23c are each connected to the suction muffler 23b, and the refrigerant flowing in from the suction muffler 23b is introduced into the compression mechanism unit 30.
  • the electric motor unit 24 is provided in the upper part of the inside of the container 20, and the rotation frequency is changed by inverter control or the like, and has a stator 24a and a rotor 24b.
  • the stator 24a has a cylindrical shape, and its outer peripheral surface is fixed to the inner wall of the container 20.
  • a coil (not shown) to which power is supplied from an external power source (not shown) is wound around the stator 24a.
  • the rotor 24b has a cylindrical shape and is arranged at intervals on the inner peripheral portion of the stator 24a. The rotor 24b rotates by supplying electric power to the stator 24a.
  • FIG. 3 is a cross-sectional view showing the compression mechanism portion 30 according to the first embodiment.
  • the compression mechanism unit 30 is provided in the lower part inside the container 20 and compresses the refrigerant.
  • the compression mechanism unit 30 connects the upper first compression unit 30a, the lower second compression unit 30b, the first compression unit 30a, and the second compression unit 30b. It has an intermediate partition plate 34. Since the first compression unit 30a and the second compression unit 30b have the same configuration, the first compression unit 30a will be described with reference to FIG. As shown in FIG. 3, the first compression unit 30a has a cylinder 31, a piston 32, and a vane 33.
  • FIG. 4 is a cross-sectional view showing the discharge notch 31d and the discharge hole 47 according to the first embodiment, and is an enlarged view of the vicinity of the discharge portion 43 in FIG.
  • the cylinder 31 is fixed to the inner wall of the container 20 and has an annular shape in which a suction hole 31a through which the sucked refrigerant passes and a compression hole 31c connected to the suction hole 31a are formed. It is a member. Further, the cylinder 31 is formed with a vane groove 31b to which the vane 33 is attached. Further, the cylinder 31 is formed with a discharge notch 31d for discharging the compressed refrigerant.
  • the discharge notch 31d is inclined by, for example, 45 ° with respect to the axial direction of the rotating shaft 25.
  • the discharge notch 31d is formed at a position at an angle ⁇ with respect to the extending direction of the vane 33 (see FIG. 5).
  • the piston 32 is an annular member that is inserted into the compression hole 31c of the cylinder 31 and has an insertion hole 32a into which the rotating shaft 25 is inserted.
  • the piston 32 forms a compression chamber 35 for compressing the refrigerant with the cylinder 31.
  • the axial end of the peripheral edge of the insertion hole 32a of the piston 32 is a chamfered chamfered portion 32b.
  • the eccentric portion 25b of the rotating shaft 25 is inserted into the insertion hole 32a of the piston 32. As a result, the piston 32 rotates eccentrically with the rotation of the rotation shaft 25.
  • the vane 33 is a rod-shaped member extending in the longitudinal direction.
  • the vane 33 is attached to the vane groove 31b formed in the cylinder 31 and presses the piston 32 to partition the compression chamber 35.
  • the intermediate partition plate 34 is a plate-shaped member that connects the first compression portion 30a and the second compression portion 30b.
  • the rotating shaft 25 is a columnar member provided in the center of the container 20 inside the container 20, and connects the motor unit 24 and the compression mechanism unit 30.
  • the rotating shaft 25 has an eccentric portion 25b that is inserted into the insertion hole 32a of the piston 32.
  • the eccentric portion 25b is composed of a first eccentric portion 25c and a second eccentric portion 25d.
  • the first eccentric portion 25c and the second eccentric portion 25d are columnar members thicker than the rotating shaft 25, respectively, and the center point is eccentric from the center point of the rotating shaft 25. That is, when the rotation shaft 25 rotates, the first eccentric portion 25c and the second eccentric portion 25d rotate eccentrically around the center point of the rotation shaft 25. In this way, the rotating shaft 25 is connected to the electric motor unit 24 and driven to rotate, and the rotational force of the electric motor unit 24 is transmitted to the piston 32 via the eccentric portion 25b.
  • the first eccentric portion 25c and the second eccentric portion 25d are arranged at positions symmetrical with respect to the center point of the rotation axis 25 in the top view.
  • An oil passage 25a extending in the axial direction is formed inside the rotating shaft 25.
  • the oil suctioned from the oil sump 21 flows through the oil passage 25a.
  • a plurality of oil supply holes (not shown) connected to the oil passage 25a and extending in the radial direction from the oil passage 25a are formed. Refrigerating machine oil is introduced into each sliding portion through the oil supply hole and lubricates each sliding portion.
  • the oil separator 26 is a disk-shaped member having a diameter larger than that of the rotating shaft 25, and is fitted in the upper part of the rotating shaft 25.
  • the oil separator 26 closes the flow path to collide and separate the refrigerant and the refrigerating machine oil.
  • the oil separator 26 drops the separated refrigerating machine oil to the lower part of the container 20 and guides only the refrigerant to the discharge pipe 22.
  • the oil separator 26 includes an upper oil separator 26a provided at the uppermost end of the rotating shaft 25 and a lower oil separator provided below the upper oil separator 26a. It has 26b and.
  • the bearing 40 is a cylindrical member, and has a base 41 mounted on the upper surface of the cylinder 31 of the first compression portion 30a and a base 41 having a diameter smaller than that of the base 41. It has a cylindrical portion 42 extending in the axial direction from the inner peripheral edge portion of the above.
  • a discharge portion 43 is provided at the base portion 41 of the bearing 40.
  • the discharge unit 43 has a valve seat 44, a discharge valve 45, and a stationary valve 46.
  • the valve seat 44 is a portion where a discharge hole 47 connected to the discharge notch 31d formed in the cylinder 31 is formed.
  • the discharge valve 45 is a leaf spring provided on the valve seat 44 and opens and closes the discharge hole 47.
  • the discharge valve 45 opens the discharge hole 47 when the pressure in the discharge hole 47 becomes equal to or higher than a predetermined pressure.
  • the stationary valve 46 presses the discharge valve 45. When the pressure in the discharge hole 47 of the static valve 46 becomes equal to or higher than a predetermined pressure, the force pushed by the discharge valve 45 is strengthened to release the holding of the discharge valve 45.
  • FIG. 5 is an enlarged cross-sectional view showing a state in which the discharge hole 47 according to the first embodiment is viewed in the direction of the rotation axis. Next, the discharge hole 47 will be described in detail.
  • FIG. 5 is a diagram showing a discharge hole 47 when the center of the piston 32 is closest to the center of the discharge hole 47 in the eccentric rotation of the piston 32.
  • the outer wire on the discharge valve 45 side in the discharge hole 47 is referred to as the valve side outer wire 48
  • the outer wire on the cylinder 31 side in the discharge hole 47 is referred to as the cylinder side outer wire 49.
  • the valve-side outer line 48 is displaced outward from the cylinder-side outer line 49.
  • the discharge hole 47 is formed at a position at an angle ⁇ with respect to the extending direction of the vane 33.
  • both the outer edge portion 47a and the inner edge portion 47b of the discharge hole 47 are inclined at an inclination angle ⁇ with respect to the axial direction of the rotation shaft 25.
  • the inclination angle ⁇ is in a range of 15 ° or more and 45 ° or less in the phase direction in which the center of the piston 32 is closest to the center of the discharge hole 47.
  • the discharge notch 31d is inclined by, for example, 45 ° with respect to the axial direction of the rotating shaft 25. That is, the discharge hole 47 is connected to the discharge notch 31d and extends in the notch direction of the discharge notch 31d.
  • the cylinder-side outer wire 49 of the discharge hole 47 overlaps with the chamfered portion 32b of the piston 32. That is, the discharge portion 43 is formed with a communication portion 247c in which the chamfered portion 32b of the piston 32 and the discharge hole 247 communicate with each other.
  • the sub-bearing 50 is a cylindrical member, and has a sub-base 51 provided below the piston 32 of the second compression portion 30b and a sub-base 51 having a diameter smaller than that of the sub-base 51. It has a sub-cylinder portion 52 extending in the axial direction from the inner peripheral edge portion of the above. By inserting the rotating shaft 25 into the inner peripheral portions of the sub-base portion 51 and the sub-cylinder portion 52, the rotating shaft 25 is rotatably supported.
  • the sub-bearing 50 is also provided with the sub-discharge unit 53, but since the configuration of the sub-discharge unit 53 is the same as that of the discharge unit 43, the description thereof will be omitted.
  • the discharge muffler 27 is a dome-shaped member having a hollow portion, which is attached to the upper surface of the base portion 41 which is a part of the bearing 40 and suppresses noise amplified by resonance generated in the space inside the container 20. Is. A hole into which the rotating shaft 25 is inserted is formed in the center of the discharge muffler 27.
  • the sub-discharge muffler 28 is a dome-shaped member that covers the sub-base 51 and the bottom of the rotating shaft 25, which are a part of the sub-bearing 50, and emits noise amplified by resonance generated in the space inside the container 20. It suppresses.
  • the first eccentric portion 25c and the second eccentric portion 25d are arranged at positions symmetrical with respect to the center point of the rotation axis 25 in the top view. Therefore, the phase angle between the piston 32 into which the first eccentric portion 25c is inserted and the piston 32 into which the second eccentric portion 25d is inserted is 180 ° out of phase. Therefore, the shaft load is reduced, the reliability of the compressor 6 is improved, the torque fluctuation is reduced, and the vibration in the rotational direction is reduced.
  • the compressed refrigerant which is in a high temperature and high pressure state, reaches the discharge hole 47 of the bearing 40 through the discharge notch 31d of the cylinder 31.
  • the discharge valve 45 presses the static valve 46, and when the static valve 46 opens, the refrigerant flows out from the discharge valve 45 into the space between the discharge muffler 27 and the bearing 40. do.
  • the outflowing refrigerant flows from the discharge muffler 27 into the container 20 and reaches the discharge pipe 22 through the gap of the motor unit 24.
  • the refrigerant that has reached the discharge pipe 22 is discharged into the refrigerant circuit 4 through the discharge pipe 22.
  • the sliding portion is, for example, a portion where the rotating shaft 25 and the piston 32 are in contact, a portion where the rotating shaft 25 and the bearing 40 are in contact, and the like.
  • the sliding portion is a portion where the rotating shaft 25 and the auxiliary bearing 50 are in contact with each other, a portion where the rotating shaft 25 and the intermediate plate 6c are in contact with each other, and the like.
  • the sliding portion includes a portion where the piston 32 and the cylinder 31 contact, a portion where the piston 32 and the bearing 40 contact, a portion where the piston 32 and the auxiliary bearing 50 contact, and the piston 32 and the intermediate partition plate 34. It is the part that comes into contact. As a result, damage to the members due to direct contact between the members is prevented, and leakage of the refrigerant is also prevented.
  • the discharge hole 47 extends along the notch direction of the discharge notch 31d. Therefore, the refrigerant flowing along the discharge notch 31d smoothly flows out into the discharge hole 47 without colliding. Therefore, the pressure loss can be reduced and the decrease in compression efficiency can be suppressed. As described above, the discharge hole 47 and the discharge notch 31d have the effect of rectifying the refrigerant.
  • the discharge hole 47 is inclined at an inclination angle ⁇ in a range of 15 ° or more and 45 ° or less toward the phase direction in which the center of the piston 32 is closest to the center of the discharge hole 47 with respect to the axial direction of the rotation shaft 25. ing.
  • the inclination angle ⁇ is less than 15 °, the effect of reducing the pressure loss cannot be sufficiently obtained.
  • the inclination angle ⁇ is larger than 45 °, the flow field is separated and a loss due to pressure resistance occurs.
  • the inclination angle ⁇ is 15 ° or more and 45 ° or less, the pressure loss at the bending position where the discharge notch 31d and the discharge hole 47 are connected can be reduced. Therefore, it is possible to suppress a decrease in the compression efficiency of the compressor 6.
  • FIG. 6 is a cross-sectional view showing a discharge notch 31d and a discharge hole 247 in a comparative example.
  • the compressor 206 in the comparative example of the compressor 6 of the first embodiment will be described.
  • the cylinder 31 is formed with a discharge notch 31d for discharging the compressed refrigerant.
  • the discharge notch 31d is inclined by, for example, 45 ° with respect to the axial direction of the rotating shaft 25.
  • the bearing 40 is a cylindrical member, and has a base portion 41 attached to the upper surface of the cylinder 31 of the first compression portion 30a and an inner peripheral edge portion of the base portion 41 having a diameter smaller than that of the base portion 41. It has a cylinder portion 42 extending in the axial direction from the cylinder portion 42.
  • a discharge portion 43 is provided at the base 41 of the bearing 40.
  • the discharge unit 43 has a valve seat 44, a discharge valve 45, and a stationary valve 46.
  • the valve seat 44 is a portion where a discharge hole 247 connected to a discharge notch 31d formed in the cylinder 31 is formed.
  • the discharge valve 45 is a leaf spring provided on the valve seat 44 and opens and closes the discharge hole 247.
  • the discharge valve 45 opens the discharge hole 247 when the pressure of the discharge hole 247 becomes equal to or higher than a predetermined pressure.
  • the stationary valve 46 presses the discharge valve 45. When the pressure of the discharge hole 247 of the stationary valve 46 becomes equal to or higher than a predetermined pressure, the force pushed by the discharge valve 45 is increased, and the holding of the discharge valve 45 is released.
  • FIG. 7 is an enlarged cross-sectional view showing a state in which the discharge hole 247 in the comparative example is viewed in the direction of the rotation axis.
  • FIG. 7 is a diagram showing a discharge hole 247 when the center of the piston 32 is closest to the center of the discharge hole 247 in the eccentric rotation of the piston 32.
  • the outer wire on the discharge valve 45 side in the discharge hole 247 is referred to as the valve side outer wire 48
  • the outer wire on the cylinder 31 side in the discharge hole 247 is referred to as the cylinder side outer wire 49.
  • the valve-side outer line 48 coincides with the cylinder-side outer line 49.
  • the discharge hole 247 extends in the axial direction of the rotating shaft 25 as shown in FIGS. 6 and 7.
  • the discharge notch 31d is inclined by, for example, 45 ° with respect to the axial direction of the rotating shaft 25.
  • the portion where the discharge notch 31d and the discharge hole 247 are connected is bent. Therefore, the refrigerant flowing along the inclined discharge notch 31d collides with the inner surface of the discharge hole 247 along the axial direction. Therefore, a pressure loss occurs and the compression efficiency is lowered.
  • the discharge hole 47 extends along the notch direction of the discharge notch 31d. Therefore, the refrigerant flowing along the discharge notch 31d smoothly flows out into the discharge hole 47 without colliding. Therefore, the pressure loss can be reduced and the decrease in compression efficiency can be suppressed.
  • FIG. 8 is a cross-sectional view showing the discharge notch 31d and the discharge hole 147 according to the second embodiment.
  • the shape of the discharge hole 147 in the compressor 106 is different from that of the first embodiment.
  • the same parts as those in the first embodiment are designated by the same reference numerals, the description thereof will be omitted, and the differences from the first embodiment will be mainly described.
  • the outer edge portion 147a extends along the notch direction of the discharge notch 31d
  • the inner edge portion 147b extends in the notch direction of the discharge notch 31d with respect to the center line of the discharge hole 147. It extends in the direction of line symmetry.
  • FIG. 9 is an enlarged cross-sectional view showing a state in which the discharge hole 147 in the second embodiment is viewed in the direction of the rotation axis.
  • FIG. 9 is a diagram showing a discharge hole 147 when the center of the piston 32 is closest to the center of the discharge hole 147 in the eccentric rotation of the piston 32.
  • the outer wire on the discharge valve 45 side in the discharge hole 147 is referred to as the valve side outer wire 48
  • the outer wire on the cylinder 31 side in the discharge hole 147 is referred to as the cylinder side outer wire 49.
  • the valve-side outer wire 48 is located on the outer side of the entire circumference of the cylinder-side outer wire 49.
  • the outer edge portion 147a is in the axial direction of the rotating shaft 25, and the center of the piston 32 is in the phase direction closest to the center of the discharge hole 147. It is tilted at an inclination angle ⁇ in the range of 15 ° or more and 45 ° or less. Further, the discharge hole 147 is inclined at an inclination angle ⁇ in a range of 15 ° or more and 45 ° or less with respect to the axial direction of the rotation shaft 25 in a direction in which the inner edge portion 147b is line-symmetrical with the notch direction of the discharge notch 31d. There is. That is, the discharge hole 147 has a shape in which the diameter is tapered from the discharge notch 31d.
  • the outer edge portion 147a extends along the notch direction of the discharge notch 31d, and the inner edge portion 147b is the discharge notch 31d with respect to the center line of the discharge hole 147. It extends in the direction of line symmetry with the notch direction. Therefore, as shown in FIG. 9, a communication portion 247c in which the chamfered portion 32b of the piston 32 and the discharge hole 147 communicate with each other is not formed.
  • the communication unit 247c will be described.
  • the cylinder-side outer wire 49 of the discharge hole 247 of the compressor 206 according to the comparative example overlaps with the chamfered portion 32b of the piston 32. That is, the discharge portion 43 is formed with a communication portion 247c in which the chamfered portion 32b of the piston 32 and the discharge hole 247 communicate with each other. Since the chamfered portion 32b has the same pressure as the pressure inside the container 20, the pressure is relatively lower than that inside the compression chamber 35 after the compression step. Therefore, the refrigerant discharged from the compression chamber 35 through the discharge hole 247 may leak through the communication portion 247c. Therefore, it is desired to reduce the leakage loss by making the area of the communication portion 247c as small as possible in order to secure the compression efficiency of the compressor 206.
  • the outer edge portion 147a extends along the notch direction of the discharge notch 31d
  • the inner edge portion 147b extends in the notch direction of the discharge notch 31d with respect to the center line of the discharge hole 147. Since it extends in the direction of line symmetry with, the communication portion 247c is not formed. Therefore, the leakage loss of the refrigerant can be reduced. Therefore, it is possible to suppress a decrease in the compression efficiency of the compressor 106 due to refrigerant leakage.
  • the discharge hole 147 is inclined in a range of 15 ° or more and 45 ° or less in the phase direction in which the outer edge portion 147a is closest to the center of the discharge hole 147 with respect to the axial direction of the rotation shaft 25. It is tilted at an angle ⁇ .
  • the inclination angle ⁇ is less than 15 °, the effect of reducing the pressure loss cannot be sufficiently obtained.
  • the inclination angle ⁇ is larger than 45 °, the flow field is separated and a loss due to pressure resistance occurs.
  • the inclination angle ⁇ is 15 ° or more and 45 ° or less, the pressure loss at the bending position where the discharge notch 31d and the discharge hole 147 are connected can be reduced. Therefore, it is possible to suppress a decrease in the compression efficiency of the compressor 106.
  • the outer edge portion 47a of the discharge hole 47 extends along the notch direction of the discharge notch 31d, so that the refrigerant flowing along the discharge notch 31d is smooth without collision. Can flow out into the discharge hole 47. Further, since the inner edge portion 47b of the discharge hole 47 extends in a direction line-symmetrical with the notch direction of the discharge cutout 31d, a communication portion 247c in which the chamfered portion 32b of the piston 32 and the discharge hole 47 communicate with each other is formed. Not done. Therefore, in the second embodiment, it is possible to suppress the occurrence of the communication portion 247c that may occur when the discharge hole 47 extends in the notch direction of the discharge notch 31d.

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

Abstract

Compresseur comportant : un contenant ; un moteur électrique disposé à l'intérieur du contenant ; un arbre rotatif fixé au moteur électrique et entraîné en rotation par le moteur électrique ; un cylindre annulaire qui est fixé à une paroi interne du contenant et présente une découpe de décharge qui est formée dans le cylindre et à travers laquelle un réfrigérant comprimé par une chambre de compression formée à l'intérieur du contenant est évacué ; et un palier qui est placé sur le cylindre pour supporter l'arbre rotatif et former la chambre de compression conjointement avec le cylindre et présente un orifice de décharge formé en son sein qui est raccordé à la découpe de décharge et s'étend le long de la direction de découpe de la découpe de décharge dans laquelle le réfrigérant est évacué.
PCT/JP2020/017328 2020-04-22 2020-04-22 Compresseur WO2021214913A1 (fr)

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Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6134380A (ja) * 1984-07-27 1986-02-18 Toshiba Corp ロ−タリコンプレツサ
JPS62156181U (fr) * 1986-03-27 1987-10-03
JPS63183292A (ja) * 1987-01-23 1988-07-28 Hitachi Ltd 密閉形回転圧縮機
JPH03217686A (ja) * 1990-01-23 1991-09-25 Mitsubishi Heavy Ind Ltd ロータリ圧縮機
JP2005188421A (ja) * 2003-12-26 2005-07-14 Daikin Ind Ltd 圧縮機
WO2011135817A1 (fr) * 2010-04-28 2011-11-03 パナソニック株式会社 Compresseur rotatif
JP2014040827A (ja) * 2012-07-25 2014-03-06 Daikin Ind Ltd 圧縮機
JP2019027372A (ja) * 2017-07-31 2019-02-21 ダイキン工業株式会社 圧縮機

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6134380A (ja) * 1984-07-27 1986-02-18 Toshiba Corp ロ−タリコンプレツサ
JPS62156181U (fr) * 1986-03-27 1987-10-03
JPS63183292A (ja) * 1987-01-23 1988-07-28 Hitachi Ltd 密閉形回転圧縮機
JPH03217686A (ja) * 1990-01-23 1991-09-25 Mitsubishi Heavy Ind Ltd ロータリ圧縮機
JP2005188421A (ja) * 2003-12-26 2005-07-14 Daikin Ind Ltd 圧縮機
WO2011135817A1 (fr) * 2010-04-28 2011-11-03 パナソニック株式会社 Compresseur rotatif
JP2014040827A (ja) * 2012-07-25 2014-03-06 Daikin Ind Ltd 圧縮機
JP2019027372A (ja) * 2017-07-31 2019-02-21 ダイキン工業株式会社 圧縮機

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