Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
  • F04C18/30—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

• the turbine supercharger of Patent Document 1 includes a casing, a motor, a rotor, a rotating blade, a supercharger, a shaft, and a discharge pipe.
• the casing includes a main casing in which the motor, the rotating blade, the supercharger, and the shaft are arranged, and an auxiliary casing in which the rotor is arranged.
• the main casing and the auxiliary casing are fixed to each other, and a partition wall is provided inside the main casing. By providing the partition wall inside the main casing, a motor chamber and a storage chamber are formed inside the main casing.
• a shaft is rotatably supported by the partition wall, and a rotating blade housed in the storage chamber is fixed to one end of the shaft, and a supercharger housed in the motor chamber is fixed to the other end of the shaft.
• the motor chamber houses a motor
• the auxiliary casing houses a rotor.
• An exhaust port provided in the auxiliary casing and a communication hole provided to communicate with the storage chamber of the main casing are connected via a discharge pipe.
• the main casing has a discharge hole that communicates with the storage chamber and discharges compressed gas, and a suction hole that communicates with the motor chamber and draws in intake gas from outside the main casing.
• a turbine supercharger configured in this manner, the rotor rotates due to the rotation of the motor, and gas compressed by the rotor inside the sub-casing flows from the exhaust port of the sub-casing through the discharge pipe and into the accommodation chamber of the main casing via the communication hole.
• the gas that flows into the accommodation chamber of the main casing via the communication hole then drives the rotating impeller to rotate, and the gas is discharged from the exhaust hole of the main casing.
• intake gas flows in through the intake hole, is pressurized by the supercharger rotating with the rotating impeller, becomes dense, and is sucked into the sub-casing.
• the turbocharger in Patent Document 1 is structured so that gas compressed by the rotor inside the sub-casing is introduced into the main casing's housing through a discharge pipe installed outside the main casing, and then sprayed onto the rotor blades. This causes a pressure loss as the gas compressed by the rotor passes through the discharge pipe, which creates the problem of being unable to rotate the rotor blades efficiently.
• This disclosure has been made to solve the problems described above, and aims to provide a rotary compressor and a refrigeration cycle device that can reduce pressure loss by providing a supercharging mechanism in the compression mechanism that is driven by the refrigerant discharged from the compression mechanism.
• the turbocharging mechanism includes a bearing that closes one side of the chamber and has a discharge flow passage formed therein that discharges the compressed refrigerant out of the compression chamber, a closing member that is fixed to the other side of the cylinder in the height direction and closes the other side of the cylinder chamber, and a discharge valve that is provided on the bearing and closes the discharge flow passage and opens the discharge flow passage when the refrigerant compressed in the compression chamber of the cylinder chamber reaches a preset pressure.
• the turbocharging mechanism includes a connecting shaft that is rotatably supported by the cylinder, a turbine that is connected to one end of the connecting shaft and rotates with the refrigerant discharged from the open discharge flow passage, and an impeller that is connected to the other end of the connecting shaft and rotates with the rotation of the turbine to promote the flow of the refrigerant flowing through the suction flow passage.
• the discharge pipe 4 is a pipe that discharges the refrigerant compressed by the compression mechanism 20 to the outside of the sealed container 10.
• the discharge pipe 4 is a pipe that discharges the high-temperature and high-pressure refrigerant in the sealed container 10 to the outside of the sealed container 10.
• the high-temperature, high-pressure gaseous refrigerant that has been discharged into the space within the sealed container 10 moves to the upper part of the space within the sealed container 10 through gaps, etc., of the rotating electric machine 30, and is discharged from the discharge piping 4.
• the remainder of the gaseous refrigerant that flows into the compression mechanism 20 is compressed by the second cylinder 21B and the second piston 22B to become a high-temperature, high-pressure gaseous refrigerant.
• This high-temperature, high-pressure gaseous refrigerant flows into the second discharge muffler 23B through the second discharge valve 26B of the lower bearing 24B.
• the high-temperature, high-pressure gaseous refrigerant that flows into the second discharge muffler 23B is sent from the second discharge muffler 23B through the inter-muffler refrigerant flow path 59 (see Figure 25) described below to the first discharge muffler 23A.
• FIG. 4 is a schematic diagram showing a refrigeration cycle apparatus 200 including a rotary compressor 1 according to the first embodiment.
• the refrigeration cycle apparatus 200 including the rotary compressor 1 will be described with reference to FIG. 4.
• the refrigeration cycle apparatus 200 is used for various purposes such as an air conditioner, a hot water supply apparatus, and a refrigeration apparatus.
• FIG. 4 shows an example in which the refrigeration cycle apparatus 200 is used as an air conditioner.
• the refrigeration cycle apparatus 200 shown in FIG. 4 includes an indoor heat exchanger 204 that functions as a radiator during heating operation, and an outdoor heat exchanger 202 that functions as an evaporator during heating operation.
• the refrigeration cycle apparatus 200 shown in FIG. 4 is also capable of cooling operation.
• the outdoor heat exchanger 202 functions as an evaporator or a radiator, and exchanges heat between the air and the refrigerant to evaporate and gasify the refrigerant or condense and liquefy it.
• the outdoor heat exchanger 202 functions as an evaporator during heating operation and as a radiator during cooling operation.
• the indoor heat exchanger 204 functions as an evaporator or a radiator, and exchanges heat between the air and the refrigerant to evaporate and gasify the refrigerant or condense and liquefy the refrigerant.
• the indoor heat exchanger 204 functions as a radiator during heating operation and as an evaporator during cooling operation.
• the indoor heat exchanger 204 is mounted in an indoor device.
• the flow path switching valve 201, the outdoor heat exchanger 202, and the pressure reducer 203 are mounted in an outdoor device.
• the low-temperature, low-pressure two-phase gas-liquid refrigerant that flows into the outdoor heat exchanger 202 absorbs heat from the outdoor air and evaporates, and flows out from the outdoor heat exchanger 202 as a low-pressure gaseous refrigerant or two-phase gas-liquid refrigerant.
• the low-pressure gaseous refrigerant or two-phase gas-liquid refrigerant that flows out from the outdoor heat exchanger 202 is sucked into the suction muffler 3 of the rotary compressor 1.
• the low-pressure gaseous refrigerant among the refrigerants sucked into the suction muffler 3 of the rotary compressor 1 is compressed by the compression mechanism 20 of the rotary compressor 1 to become a high-temperature, high-pressure gaseous refrigerant.
• This high-temperature, high-pressure gaseous refrigerant is discharged again from the rotary compressor 1. That is, when the refrigeration cycle device 200 performs heating operation, the refrigerant circulates as shown by the solid arrows in FIG. 4.
• the flow path switching valve 201 switches to the flow path shown by the dashed line in FIG. 4.
• the discharge pipe 4 of the rotary compressor 1 is connected to the outdoor heat exchanger 202
• the suction muffler 3 of the rotary compressor 1 is connected to the indoor heat exchanger 204.
• the outdoor heat exchanger 202 functions as a radiator
• the indoor heat exchanger 204 functions as an evaporator.
• the high-temperature, high-pressure gaseous refrigerant compressed by the rotary compressor 1 is discharged from the rotary compressor 1, this high-temperature, high-pressure gaseous refrigerant flows into the outdoor heat exchanger 202.
• the high-temperature, high-pressure gaseous refrigerant that flows into the outdoor heat exchanger 202 condenses while releasing heat to the outdoor air, and flows out of the outdoor heat exchanger 202 as a high-pressure liquid refrigerant.
• the high-pressure liquid refrigerant flowing out from the outdoor heat exchanger 202 flows into the pressure reducer 203.
• the high-pressure liquid refrigerant that flows into the pressure reducer 203 is then depressurized by the pressure reducer 203 to become a low-temperature, low-pressure two-phase gas-liquid refrigerant, which flows out from the pressure reducer 203.
• the low-temperature, low-pressure two-phase gas-liquid refrigerant that flows out from the pressure reducer 203 flows into the indoor heat exchanger 204.
• the low-temperature, low-pressure two-phase gas-liquid refrigerant that flows into the indoor heat exchanger 204 absorbs heat from the indoor air and evaporates, and flows out from the indoor heat exchanger 204 as a low-pressure gaseous refrigerant or two-phase gas-liquid refrigerant. At this time, the air in the room is cooled.
• the low-pressure gaseous refrigerant or two-phase gas-liquid refrigerant that flows out from the indoor heat exchanger 204 is sucked into the suction muffler 3 of the rotary compressor 1.
• FIG. 5 is a top perspective view showing the upper bearing 24A, first cylinder 21A, and first turbine 28A of the rotary compressor 1 according to embodiment 1.
• FIG. 6 is a vertical cross-sectional view showing the upper bearing 24A, first cylinder 21A, and first turbine 28A of the rotary compressor 1 according to embodiment 1.
• FIG. 7 is a top perspective view showing the upper bearing 24A, first cylinder 21A, and first turbine 28A of the rotary compressor 1 according to embodiment 1.
• FIG. 8 is a top perspective view showing the upper bearing 24A of the rotary compressor 1 according to embodiment 1.
• FIG. 9 is a bottom perspective view showing the upper bearing 24A of the rotary compressor 1 according to embodiment 1.
• FIG. 10 is a bottom perspective view showing the lower bearing 24B, second cylinder 21B, and second turbine 28B of the rotary compressor 1 according to embodiment 1.
• FIG. 11 is a vertical cross-sectional view showing the lower bearing 24B, second cylinder 21B, and second turbine 28B of the rotary compressor 1 according to embodiment 1.
• FIG. 12 is a bottom view showing the lower bearing 24B, the second cylinder 21B, and the second turbine 28B of the rotary compressor 1 according to the first embodiment.
• FIG. 13 is a bottom perspective view showing the lower bearing 24B of the rotary compressor 1 according to the first embodiment.
• FIG. 14 is a top view showing the lower bearing 24B of the rotary compressor 1 according to the first embodiment.
• FIG. 15 is a vertical cross-sectional view showing the first cylinder 21A of the rotary compressor 1 according to the first embodiment.
• FIG. 16 is a top view showing the first cylinder 21A of the rotary compressor 1 according to the first embodiment.
• FIG. 17 is a bottom view showing the first cylinder 21A of the rotary compressor 1 according to the first embodiment.
• FIG. 18 is a top view showing the first cylinder 21A and the first impeller 29A of the rotary compressor 1 according to the first embodiment.
• FIG. 19 is an arrow view of the A-A cross section of FIG. 18.
• FIG. 20 is a vertical cross-sectional view showing the second cylinder 21B of the rotary compressor 1 according to the first embodiment.
• a first support wall portion 150A is provided on the upper surface of the first cylinder 21A.
• This first support wall portion 150A is provided between the upper bearing 24A and the first communication chamber 21Ab, which is a part of the first intake passage 52A.
• a first through hole 21Ac is formed in the first support wall portion 150A, which penetrates in the axial direction.
• a first connecting shaft 27A is rotatably attached to the first through hole 21Ac formed in this first support wall portion 150A.
• first connecting shaft 27A protrudes above the upper surface of the first cylinder 21A, and the other end protrudes below the upper surface of the first cylinder 21A.
• first support wall portion 150A in which the first through hole 21Ac is formed on the upper surface of the first cylinder 21A, the first connecting shaft 27A can be rotatably supported.
• the first impeller 29A connected to the first connecting shaft 27A can be preferably positioned within the first communicating chamber 21Ab, which is part of the first intake passage 52A.
• the first turbine 28A is attached to one end of the first connecting shaft 27A and is arranged above the top surface of the first cylinder 21A.
• the first impeller 29A is attached to the other end of the first connecting shaft 27A and is arranged below the top surface of the first cylinder 21A. As shown in Figures 6, 15 to 19, the first impeller 29A is arranged in the first communicating chamber 21Ab, which is part of the first intake passage 52A.
• the refrigerant discharged into the first discharge muffler 23A is blown onto the first turbine 28A attached to one end of the first connecting shaft 27A, which is rotatably attached to the first cylinder 21A, causing the first turbine 28A to rotate.
• the first impeller 29A attached to the other end of the first connecting shaft 27A rotates, promoting the flow of refrigerant through the first intake passage 52A and supercharging the refrigerant to the first intake chamber 57A.
• the first turbine 28A, the first connecting shaft 27A, and the first impeller 29A form a supercharging mechanism T1.
• a second support wall portion 150B is provided on the lower surface of the second cylinder 21B.
• This second support wall portion 150B is provided between the lower bearing 24B and the second communication chamber 21Bb, which is a part of the second intake passage 52B.
• a second through hole 21Bc is formed in the second support wall portion 150B, penetrating in the axial direction.
• the second connecting shaft 27B is rotatably attached to the second through hole 21Bc formed in this second support wall portion 150B.
• one end of the second connecting shaft 27B protrudes below the lower surface of the second cylinder 21B, and the other end protrudes above the lower surface of the second cylinder 21B.
• a second recess 124B recessed in the height direction is provided on the underside of the lower bearing 24B.
• a second turbine arrangement through hole 151B for arranging the second turbine 28B is formed in the second recess 124B.
• the second turbine 28B is arranged in the second turbine arrangement through hole 151B.
• the second turbine arrangement through hole 151B which is a through hole, is formed in the lower bearing 24B and the second turbine 28B is arranged in the second turbine arrangement through hole 151B.
• the strength of the outer periphery of the lower bearing 24B can be increased compared to, for example, a configuration in which a notch is provided on the outer periphery of the lower bearing 24B and the second turbine 28B is arranged in the notch.
• a second turbine 28B is attached to one end of the second connecting shaft 27B and is disposed below the bottom surface of the second cylinder 21B.
• a second impeller 29B is attached to the other end of the second connecting shaft 27B and is disposed above the bottom surface of the second cylinder 21B. As shown in Figures 11 and 20 to 24, the second impeller 29B is disposed in the second communicating chamber 21Bb, which is part of the second intake passage 52B.
• the refrigerant discharged into the second discharge muffler 23B is blown onto the second turbine 28B attached to one end of the second connecting shaft 27B, which is rotatably attached to the second cylinder 21B, causing the second turbine 28B to rotate.
• the second impeller 29B attached to the other end of the second connecting shaft 27B rotates, promoting the flow of refrigerant through the second intake passage 52B and supercharging the refrigerant to the second intake chamber 57B.
• the second turbine 28B, the second connecting shaft 27B, and the second impeller 29B form a supercharging mechanism T2.
• the first discharge valve 26A, the first valve retainer 15A, and the first turbine 28A are disposed in the first recess 124A of the upper bearing 24A.
• the first discharge flow path 53A is formed in the first bottom surface 124Aa of the first recess 124A.
• the first discharge flow path 53A is formed in the first cylinder 21A and the upper bearing 24A.
• the side surface of the first recess 124A forms a first guide surface 124Ab that guides the refrigerant discharged from the first discharge flow path 53A to the first turbine 28A.
• the second discharge valve 26B, the second valve retainer 15B, and the second turbine 28B are disposed in the second recess 124B of the lower bearing 24B.
• the second discharge flow path 53B is formed in the second bottom surface 124Ba of the second recess 124B.
• the second discharge flow path 53B is formed in the second cylinder 21B and the lower bearing 24B.
• the side surface of the second recess 124B forms a second guide surface 124Bb that guides the refrigerant discharged from the second discharge flow path 53B to the second turbine 28B.
• two second guide surfaces 124Bb are formed by the side surface of the second recess 124B, and the two second guide surfaces 124Bb are configured to approach each other as they approach the second turbine 28B. Therefore, when the refrigerant discharged from the second discharge passage 53B to the outside of the second compression chamber 58B is guided along the second guide surface 124Bb to the second turbine 28B, the density of the refrigerant guided from the second discharge passage 53B to the second turbine 28B can be increased, and the second turbine 28B can be rotated efficiently.
• the first discharge valve 26A moves in a cantilever manner. Therefore, when the refrigerant compressed in the first compression chamber 58A of the first cylinder chamber 55A reaches a preset pressure, the cantilever-shaped first tip 26Aa of the first discharge valve 26A is lifted and the first discharge flow passage 53A is opened. Then, the refrigerant discharged from the opened first discharge flow passage 53A is blown out toward the first turbine 28A, and the pressure energy of the blown out refrigerant efficiently rotates the first turbine 28A. Similarly, the second discharge valve 26B moves in a cantilever manner.
• the cantilever-shaped second tip 26Ba of the second discharge valve 26B is lifted and the second discharge flow passage 53B is opened.
• the refrigerant discharged from the open second discharge passage 53B is blown out toward the second turbine 28B, and the pressure energy of the blown out refrigerant efficiently rotates the second turbine 28B.
• a discharge muffler that covers the discharge valve is provided to reduce the discharge sound of the refrigerant discharged from the discharge flow path that is opened when the discharge valve is opened, and a configuration is known in which the refrigerant discharged from the discharge flow path is made to collide with the discharge muffler instead of colliding with a sealed container, thereby silencing the sound.
• a pressure loss occurs when the refrigerant discharged from the discharge flow path is made to collide with the discharge muffler.
• the refrigerant discharged from the first discharge flow path 53A and the second discharge flow path 53B is configured to collide with the first turbine 28A and the second turbine 28B, respectively, before colliding with the first discharge muffler 23A and the second discharge muffler 23B. Therefore, the pressure energy of the refrigerant can be used to efficiently rotate the first turbine 28A and the second turbine 28B.
• the refrigerant compressed by the second cylinder 21B and the second piston 22B is discharged into the second discharge muffler 23B and then flows into the first discharge muffler 23A via the inter-muffler refrigerant flow path 59.
• the refrigerant that flows into the first discharge muffler 23A is discharged into the sealed container 10 through the discharge hole 23Aa of the first discharge muffler 23A.
• the pressure energy of the refrigerant discharged from the first discharge passage 53A and the second discharge passage 53B to the outside of the first compression chamber 58A and the outside of the second compression chamber 58B is used to rotate the first impeller 29A and the second impeller 29B.
• the refrigerant is supercharged to the first suction chamber 57A and the second suction chamber 57B, increasing the capacity of the rotary compressor 1.
• by increasing the pressure in the first suction chamber 57A and the second suction chamber 57B it is possible to reduce the amount of work per rotation of the rotary compressor 1.
• FIG. 29(a) shows a top view
• FIG. 29(b) shows a side view
• FIG. 29(c) shows a perspective view
• FIG. 27 shows the first impeller 29A, but the second impeller 29B is not shown because it has the same shape
• FIG. 28 shows the first turbine 28A, but the second turbine 28B is not shown because it has the same shape
• FIG. 29 shows the first connecting shaft 27A, but the second connecting shaft 27B is not shown because it has the same shape.
• the second turbine 28B also has a second turbine blade group 28Ba consisting of a plurality of blades that allow the refrigerant to flow in from the radial outside and flow out in the axial direction.
• the second impeller 29B has a second impeller blade group 29Ba consisting of a plurality of blades that allow the refrigerant to flow in from the axial direction and flow out in the radial outside.
• the compression mechanism 20 of the rotary compressor 1 according to the first embodiment has two cylinder chambers, a first cylinder chamber 55A and a second cylinder chamber 55B, and shares the partition plate 25 that constitutes the first cylinder chamber 55A with the partition plate 25 that constitutes the second cylinder chamber 55B.
• the rotary compressor 1 according to the first embodiment is a twin rotary type rotary compressor. Therefore, the rotary compressor 1 according to the first embodiment can increase the refrigerant compression capacity compared to a single rotary type rotary compressor that has one cylinder chamber.
• the rotary compressor 1 includes a sealed container 10 forming an outer shell, a rotating electric machine 30 housed within the sealed container 10, a rotating shaft 40 housed within the sealed container 10 and rotated by the rotating electric machine 30, the rotating shaft 40 having an eccentric shaft portion, a compression mechanism 20 housed within the sealed container 10 and having a cylinder chamber that compresses a refrigerant by eccentric motion of the eccentric shaft portion, and supercharging mechanisms T1 and T2 housed within the sealed container 10.
• the compression mechanism 20 includes a cylinder having an intake passage formed therein that draws low-pressure refrigerant into the cylinder chamber from outside the sealed container 10, a piston fitted to the eccentric shaft portion, a vane that separates the cylinder chamber, which is formed by the inner circumference of the cylinder and the outer circumference of the piston, into a suction chamber and a compression chamber, and a cylinder height
• the turbocharging mechanisms T1 and T2 are equipped with a bearing fixed to one side of the cylinder in the height direction to close one side of the cylinder chamber and a discharge flow path formed to discharge the compressed refrigerant out of the compression chamber, a blocking member fixed to the other side of the cylinder in the height direction to block the other side of the cylinder chamber, and a discharge valve provided on the bearing to block the discharge flow path and open the discharge flow path when the refrigerant compressed in the compression chamber of the cylinder chamber reaches a preset pressure.
• the turbocharging mechanisms T1 and T2 are equipped with a connecting shaft rotatably supported by the cylinder, a turbine connected to one end of the connecting shaft and rotated by the refrigerant discharged from the open discharge flow path, and an impeller connected to the other end of the connecting shaft and rotating with the rotation of the turbine to promote the flow of the refrigerant flowing through the suction flow path.
• the supercharging mechanisms T1 and T2 include a connecting shaft rotatably supported on a cylinder, a turbine connected to one end of the connecting shaft and rotated by the refrigerant discharged from the open discharge passage, and an impeller connected to the other end of the connecting shaft and rotating with the rotation of the turbine to promote the flow of the refrigerant through the suction passage.
• the supercharging mechanisms T1 and T2 driven by the refrigerant discharged from the compression mechanism 20 are provided in the compression mechanism 20, no pressure loss occurs as in the conventional technology, and the pressure loss can be reduced.
• the turbine is provided with a group of turbine blades made up of a plurality of blades that allow the refrigerant to flow in from the radially outer side and flow out in the axial direction
• the impeller is provided with a group of impeller blades made up of a plurality of blades that allow the refrigerant to flow in from the axial direction and flow out in the radially outer direction.
• the turbine has a group of turbine blades, so that the discharge valve can be arranged radially outside the turbine.
• the impeller has a group of impeller blades, so that the suction chamber can be arranged radially outside the impeller.
• the connecting shaft can be supported in a suitable manner so as to be freely rotatable by providing a support wall portion with a through hole formed in the cylinder.
• the impeller connected to the connecting shaft can be suitably positioned within the intake passage (communication chamber).
• the surface of the bearing opposite the cylinder is provided with a recess in which the discharge valve and turbine are disposed, and the recess has a discharge flow passage formed on the bottom surface and a guide surface formed on the side surface that guides the refrigerant discharged from the discharge flow passage to the turbine.
• the refrigerant discharged from the discharge passage to the outside of the compression chamber can be guided along the guide surface to the turbine, allowing the turbine to rotate efficiently.
• the rotary compressor 1 by forming a turbine placement through hole in which the turbine is placed, it is possible to increase the strength of the outer peripheral portion of the bearing, compared to a configuration in which, for example, a notch is provided on the outer periphery of the bearing and the turbine is placed within the notch.
• the recess has two guide surfaces, and the two guide surfaces are configured to approach each other as they approach the turbine.
• the rotary compressor 1 when the refrigerant discharged from the discharge passage to the outside of the compression chamber is guided along the guide surface to the turbine, the density of the refrigerant guided from the discharge passage to the turbine can be increased, and the turbine can be rotated efficiently.

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

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Citations (3)

• 2024
  • 2024-01-15 WO PCT/JP2024/000744 patent/WO2025154121A1/ja active Pending
  • 2024-01-15 JP JP2025570368A patent/JPWO2025154121A1/ja active Pending

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