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.
• the turbocharging mechanism includes a bearing that closes one side of the intake chamber, a closing member that is fixed to the other side of the cylinder in the height direction to close the other side of the cylinder chamber and has a discharge flow path formed therein that discharges the compressed refrigerant out of the compression chamber, and a discharge valve that is provided on the closing member to close 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 bottom 13 constituting the lower part of the sealed container 10 has, for example, a roughly bowl shape as shown in FIG. 1.
• Refrigeration oil 6, which is a lubricating oil, is stored in the bottom 13. That is, refrigeration oil 6 is stored inside the sealed container 10. This refrigeration oil 6 is then supplied to the compression mechanism 20 etc., reducing friction at the sliding parts of the compression mechanism 20 etc.
• the rotating shaft 40 includes a first eccentric shaft portion 40A and a second eccentric shaft portion 40B.
• the compression mechanism 20 includes a first cylinder 21A, a first piston 22A, a first vane 50A, a first spring 51A, an upper bearing 24A, a second cylinder 21B, a second piston 22B, a second vane 50B, a second spring 51B, a lower bearing 24B, a first partition plate 25A, and a second partition plate 25B.
• the first partition plate 25A and the second partition plate 25B are also referred to as bearings or blocking members.
• the second cylinder 21B is cylindrical and is disposed below the first cylinder 21A, forming a second cylinder chamber 55B in the center.
• the second cylinder 21B is formed with a second intake passage 52B through which the refrigerant is drawn from the second intake pipe 2B, and a second discharge passage 53B through which the refrigerant is discharged to the discharge pipe 4 via the internal space of the sealed container 10.
• the second intake pipe 2B is press-fitted into the second intake passage 52B on the outer circumferential surface of the second cylinder 21B.
• the second piston 22B is fitted into the second eccentric shaft portion 40B of the rotating shaft 40, and rotates eccentrically together with the second eccentric shaft portion 40B to compress the refrigerant.
• the second vane 50B is located between the second intake passage 52B and the second discharge passage 53B, and is arranged in a second vane groove 56B formed to extend radially of the second cylinder 21B, separating the second cylinder chamber 55B into a second intake chamber 57B and a second compression chamber 58B.
• the second intake chamber 57B is connected to the second intake passage 52B
• the second compression chamber 58B is connected to the second discharge passage 53B.
• the second spring hole 54B is formed at the radially outer end of the second vane groove 56B of the second cylinder 21B, and passes axially through the second cylinder 21B, communicating with the second vane groove 56B.
• the second spring 51B is housed in the second spring hole 54B, and presses the second vane 50B attached to the tip of the second spring 51B against the outer circumferential surface of the second piston 22B.
• the lower bearing 24B is disposed so as to abut against the lower end surface of the second cylinder 21B, and closes the second cylinder chamber 55B.
• the lower bearing 24B rotatably supports the rotating shaft 40.
• the first partition plate 25A is positioned so as to abut against the lower end surface of the first cylinder 21A, and closes the first cylinder chamber 55A.
• the second partition plate 25B is positioned so as to abut against the upper end surface of the second cylinder 21B, and closes the second cylinder chamber 55B.
• the lower end surface of the first partition plate 25A and the upper end surface of the second partition plate 25B are configured to abut against each other.
• the first piston 22A rotates slidably within the first cylinder 21A.
• This first piston 22A is configured to be able to perform eccentric rotational motion within the first cylinder 21A with respect to the center of rotation of the rotating shaft 40.
• rotational motion eccentric to the center of rotation of the rotating shaft 40 will be referred to as eccentric rotational motion.
• the second piston 22B rotates slidably within the second cylinder 21B.
• This second piston 22B is configured to be able to perform eccentric rotational motion within the second cylinder 21B.
• first piston 22A is connected to the rotating shaft 40 so that it can rotate within the first cylinder 21A with a phase shift of 180 degrees relative to the rotational phase when the second piston 22B rotates within the second cylinder 21B.
• second piston 22B is connected to the rotating shaft 40 so that it can rotate within the second cylinder 21B with a phase shift of -180 degrees relative to the rotational phase when the first piston 22A rotates within the first cylinder 21A.
• the upper bearing 24A is provided with a first discharge valve 26A (see FIG. 6) described below, which discharges the refrigerant compressed by the first cylinder 21A and the first piston 22A.
• first discharge valve 26A opens, it is possible to connect the first discharge flow path 53A to the first discharge muffler 23A described below.
• the lower bearing 24B is provided with a second discharge valve 26B (see FIG. 11) described below, which discharges the refrigerant compressed by the second cylinder 21B and the second piston 22B.
• the second discharge valve 26B opens, it is possible to connect the second discharge flow path 53B to the second discharge muffler 23B described below.
• the rotating electric machine 30 has a rotor 31 that transmits its own rotation to a rotating shaft 40, and a stator 32 that is configured by mounting a multi-phase winding on a laminated core.
• the rotating shaft 40 is connected to the rotating electric machine 30 and rotates by the power of the rotating electric machine 30.
• the rotating shaft 40 also transmits the power of the rotating electric machine 30 to the compression mechanism 20.
• the upper end side of the rotating shaft 40 is connected to the rotor 31 of the rotating electric machine 30.
• the rotating shaft 40 rotates together with the rotation of the rotor 31.
• the rotating shaft 40 shown in FIG. 1 rotates around an axis extending in the vertical direction of the paper.
• the lower end side of the rotating shaft 40 is connected to the compression mechanism 20. More specifically, the lower end side of the rotating shaft 40 is rotatably supported by the upper bearing 24A and the lower bearing 24B of the compression mechanism 20.
• the first eccentric shaft portion 40A and the second eccentric shaft portion 40B are provided on the rotating shaft 40 between the portion rotatably supported by the upper bearing 24A and the portion rotatably supported by the lower bearing 24B.
• the rotating shaft 40 is connected so that the first piston 22A fitted to the first eccentric shaft portion 40A and the second piston 22B fitted to the second eccentric shaft portion 40B can rotate eccentrically.
• the rotating shaft 40 rotates with the rotation of the rotor 31, and the first piston 22A and the second piston 22B rotate eccentrically.
• the refrigerant is compressed by the first cylinder 21A and the first piston 22A, and the refrigerant is compressed by the second cylinder 21B and the second piston 22B.
• the compression mechanism 20 compresses the refrigerant sucked in from the outside using the power of the rotating electric machine 30 transmitted by the rotating shaft 40.
• the refrigeration cycle apparatus 200 is provided with a flow path switching valve 201.
• the refrigeration cycle device 200 comprises a multi-cylinder rotary compressor 1 equipped with a suction muffler 3 connected to the suction side of the multi-cylinder rotary compressor 1, a flow path switching valve 201 connected to the discharge side of the multi-cylinder rotary compressor 1, an outdoor heat exchanger 202, a pressure reducer 203, and an indoor heat exchanger 204, which are connected in sequence via piping to form a refrigerant circuit through which the refrigerant circulates.
• the refrigerant discharged from the first discharge passage 53A to the outside of the first compression chamber 58A can be guided along the first guide surface 124Ab to the first turbine 28A, allowing the first turbine 28A to rotate efficiently.
• the refrigerant discharged from the second discharge passage 53B to the outside of the second compression chamber 58B can be guided along the second guide surface 124Bb to the second turbine 28B, allowing the second turbine 28B to rotate efficiently.
• 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 is movable like a cantilever and has a first tip portion 26Aa whose tip side closes or opens the first discharge flow path 53A, and a first base end portion 26Ab whose base end side is fixed to the first partition plate 25A.
• the first discharge valve 26A is supported by a first valve retainer 15A.
• the first valve retainer 15A is a long plate-like member that is thicker than the first discharge valve 26A, and protects the first discharge valve 26A from deformation while restricting the movable range of the first discharge valve 26A.
• the first turbine 28A is positioned on the opposite side of the first base end portion 26Ab of the first discharge valve 26A based on the first tip portion 26Aa of the first discharge valve 26A.
• the second discharge valve 26B has a second tip portion 26Ba that moves like a cantilever and closes or opens the second discharge flow passage 53B at its tip end, and a second base end portion 26Bb that is fixed to the second partition plate 25B at its base end.
• the second discharge valve 26B is supported by a second valve stopper 15B.
• the second valve stopper 15B is a long plate-like member that is thicker than the second discharge valve 26B, and protects the second discharge valve 26B from deformation while restricting the movable range of the second discharge valve 26B.
• the second turbine 28B is disposed on the opposite side of the second base end portion 26Bb of the second discharge valve 26B with respect to the second tip portion 26Ba of the second discharge valve 26B.
• FIG. 25 is a vertical cross-sectional view showing the compression mechanism 20 of the multi-cylinder rotary compressor 1 according to the first embodiment.
• a first discharge muffler 23A is fixed to the upper bearing 24A on the side opposite the first cylinder 21A.
• a discharge hole 23Aa is formed in the first discharge muffler 23A.
• a second discharge muffler 23B is fixed to the lower bearing 24B on the side opposite the second cylinder 21B.
• 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, it is possible to efficiently rotate the first turbine 28A and the second turbine 28B by utilizing the pressure energy of the refrigerant.
• 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 rotate the first turbine 28A and the second turbine 28B efficiently.
• a first blocking member wall portion 25Aa is formed around the entire outer periphery of the surface of the first partition plate 25A opposite the first cylinder 21A.
• a second blocking member wall portion 25Ba is formed around the entire outer periphery of the surface of the second partition plate 25B opposite the second cylinder 21B. The entire periphery of the first blocking member wall portion 25Aa of the first partition plate 25A and the entire periphery of the second blocking member wall portion 25Ba of the second partition plate 25B are configured to abut against each other.
• the first partition plate 25A has a first outlet hole 151 that penetrates from the side opposite to the first cylinder 21A toward the first cylinder 21A and discharges the refrigerant.
• the first cylinder 21A has a second outlet hole 152 that communicates with the first outlet hole 151 and penetrates from the first partition plate 25A toward the upper bearing 24A.
• the upper bearing 24A has a third outlet hole 153 that communicates with the second outlet hole 152 and penetrates from the first cylinder 21A toward the side opposite to the first cylinder 21A.
• the refrigerant discharged from the first discharge flow path 53A and the second discharge flow path 53B can be discharged from the first blocking member wall portion 25Aa and the second blocking member wall portion 25Ba through the first outlet hole 151, the second outlet hole 152, and the third outlet hole 153.
• the first discharge muffler 23A has a discharge hole 23Aa.
• the refrigerant compressed by the first cylinder 21A and the first piston 22A is discharged into the first discharge muffler 23A and then discharged from the discharge hole 23Aa into the inside of the sealed container 10.
• the refrigerant compressed by the second cylinder 21B and the second piston 22B flows into the first discharge muffler 23A through the first outlet hole 151, the second outlet hole 152, and the third outlet hole 153.
• the refrigerant that flows into the first discharge muffler 23A is discharged into the inside of the sealed container 10 from the discharge hole 23Aa of the first discharge muffler 23A.
• the first eccentric shaft portion 40A and the second eccentric shaft portion 40B of the rotating shaft 40 perform eccentric motion within the first cylinder chamber 55A and the second cylinder chamber 55B, respectively.
• the refrigerant compressed in the first compression chamber 58A of the first cylinder chamber 55A and the refrigerant compressed in the second compression chamber 58B of the second cylinder chamber 55B reach their respective preset pressures, they lift the first tip portion 26Aa of the first discharge valve 26A and the second tip portion 26Ba of the second discharge valve 26B.
• the refrigerant discharged outside the first compression chamber 58A and outside the second compression chamber 58B rotates the first turbine 28A and the second turbine 28B, respectively.
• the rotation of the first turbine 28A and the second turbine 28B rotates the first impeller 29A and the second impeller 29B.
• the rotation of the first impeller 29A and the second impeller 29B promotes the flow of the refrigerant through the first intake passage 52A and the second intake passage 52B.
• gas is guided from an exhaust port provided in the sub-casing to the rotor blades via a discharge pipe provided outside the main casing, and power is recovered.
• refrigerant is guided from the first discharge flow passage 53A and the second discharge flow passage 53B provided in the first partition plate 25A and the second partition plate 25B to the first turbine 28A and the second turbine 28B of the supercharging mechanisms T1 and T2 provided in the first partition plate 25A and the second partition plate 25B, and power is recovered. Therefore, no pressure loss occurs as in the conventional case, and power recovery can be performed efficiently. In this way, pressure loss can be reduced by providing the supercharging mechanisms T1 and T2 driven by the refrigerant discharged from the compression mechanism 20 in the compression mechanism 20.
• FIG. 26 is a side view of the supercharging mechanisms T1 and T2 of the multi-cylinder rotary compressor 1 according to embodiment 1.
• FIG. 27 is a view of the impeller alone of the multi-cylinder rotary compressor 1 according to embodiment 1.
• FIG. 28 is a view of the turbine alone of the multi-cylinder rotary compressor 1 according to embodiment 1.
• FIG. 29 is a view of the connecting shaft alone of the multi-cylinder rotary compressor 1 according to embodiment 1.
• FIG. 26 shows a side view of the supercharging mechanism T1
• FIG. 29 is a view of the connecting shaft alone of the multi-cylinder rotary compressor 1 according to embodiment 1.
• FIG. 26 shows a side view of the supercharging mechanism T1
• FIG. 29 is a view of the connecting shaft alone of the multi-cylinder rotary compressor 1 according to embodiment 1.
• FIG. 26 shows a side view of the supercharging mechanism T1
• FIG. 29 shows a side view of the supercharging mechanism T2.
• FIG. 27 and FIG. 28 shows a top view
• FIG. 29 shows a top view
• FIG. 28 shows the first turbine 28A
• 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 first turbine 28A has a circular shape in plan view.
• the first turbine 28A also has a first turbine blade group 28Aa 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 first impeller 29A has a first impeller blade group 29Aa 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 second turbine 28B has a circular shape in plan view.
• 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 turbocharging mechanisms T1 and T2 are equipped with a bearing fixed to one side in the height direction to close one side of the cylinder chamber, a blocking member fixed to the other side in the height direction of the cylinder to close the other side of the cylinder chamber and having a discharge flow path formed therein for discharging the compressed refrigerant out of the compression chamber, and a discharge valve provided on the blocking member 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 turbine has 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 has 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.
• a blocking member wall is formed around the entire outer periphery of the surface of the blocking member opposite the cylinder, the blocking member is formed with a first outlet hole 151 that communicates with the discharge flow path and penetrates from the side opposite the cylinder side toward the cylinder side, the cylinder is formed with a second outlet hole 152 that communicates with the first outlet hole 151 and penetrates from the blocking member side toward the bearing side, and the bearing is formed with a third outlet hole 153 that communicates with the second outlet hole 152 and penetrates from the cylinder side toward the surface opposite the cylinder.
• the refrigerant discharged from the discharge passage can be discharged from within the blocking member wall through the first discharge hole 151, the second discharge hole 152, and the third discharge hole 153.
• 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 recess has two guide surfaces, and the two guide surfaces are configured to approach each other as they approach the turbine.
• the multi-cylinder 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.
• the discharge valve has a tip end that moves like a cantilever and closes or opens the discharge flow passage, and a base end that is fixed to the closing member, and the turbine is provided on the opposite side of the base end of the discharge valve with respect to the tip end of the discharge valve.
• the discharge valve moves in a cantilever manner, so that when the refrigerant compressed in the compression chamber of the cylinder chamber reaches a preset pressure, the cantilever-shaped tip of the discharge valve is lifted to open the discharge flow passage, and the refrigerant discharged from the open discharge flow passage is blown out toward the turbine.
• the pressure energy of the blown out refrigerant can be used to rotate the turbine efficiently.
• a discharge muffler is provided on the opposite side of the bearing from the cylinders, and a discharge hole 23Aa is formed in the discharge muffler.
• the multi-cylinder rotary compressor 1 can reduce the discharge noise of the refrigerant discharged from the discharge flow path by the discharge muffler.
• the pressure energy of the refrigerant can be used to rotate the impeller efficiently.
• the refrigeration cycle device 200 includes the multi-cylinder rotary compressor 1, a radiator in which the refrigerant compressed by the multi-cylinder rotary compressor 1 radiates heat, a pressure reducer 203 that reduces the pressure of the refrigerant flowing out of the radiator, and an evaporator in which the refrigerant flowing out of the pressure reducer 203 evaporates.
• the refrigeration cycle device 200 uses a single refrigerant selected from the group consisting of R1234yf, R1234ze, R32, and R290, or a mixture of two or more of these refrigerants, or a mixture of any of these with another refrigerant, or a mixture containing R1132(E), or a mixture containing R1123.
• the refrigeration cycle device 200 according to the first embodiment can achieve the same effects as the multi-cylinder rotary compressor 1 described above.

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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/JP2024/000745 patent/WO2025154122A1/ja active Pending
  • 2024-01-15 JP JP2025570369A patent/JPWO2025154122A1/ja active Pending

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