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

• This disclosure relates to a rotary compressor and a refrigeration cycle device.
• 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.
• the rotary compressor comprises a sealed container forming an outer shell, a rotating electric machine housed within the sealed container, a rotating shaft housed within the sealed container and rotated by the rotating electric machine and having an eccentric shaft portion, a compression mechanism housed within the sealed container and having a cylinder chamber that compresses a refrigerant by eccentric motion of the eccentric shaft portion, and a supercharging mechanism housed within the sealed container, the compression mechanism comprising a cylinder having an intake passage formed therein for drawing low-pressure refrigerant into the cylinder chamber from outside the sealed container, 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 an intake chamber and a compression chamber, and a cylinder pressure chamber fixed to one side in the height direction of the cylinder.
• the suction muffler 3 is connected to the first suction pipe 2A and the second suction pipe 2B.
• the compression mechanism 20 is connected to the first suction pipe 2A and the second suction pipe 2B, and compresses the refrigerant.
• the rotating electric machine 30 includes a rotor 31 and a stator 32.
• the rotating shaft 40 is connected to the rotor 31 of the rotating electric machine 30 and rotates together with the rotor 31.
• the discharge pipe 4 discharges the refrigerant compressed by the compression mechanism 20 to the outside of the sealed container 10.
• the configuration of the rotary compressor 1 will be described in detail below.
• the sealed container 10 constituting the outer shell of the rotary compressor 1 houses a compression mechanism 20, a rotating electric machine 30, a rotating shaft 40, etc.
• the sealed container 10 includes a head 11, a bottom 13, and a body 12.
• the head 11 constitutes the outer shell of the upper part of the rotary compressor 1.
• the bottom 13 constitutes the outer shell of the lower part of the rotary compressor 1.
• the body 12 constitutes the outer shell of the middle part of the rotary compressor 1, with the head 11 attached to its upper part and the bottom 13 attached to its lower part.
• First intake pipe 2A and second intake pipe 2B As described above, the first intake pipe 2A and the second intake pipe 2B are connected to the body 12 of the sealed container 10. One end of the first intake pipe 2A is connected to the first intake passage 52A (see FIG. 2) of the first cylinder 21A of the compression mechanism 20 described later. The other end of the first intake pipe 2A is connected to the intake muffler 3. One end of the second intake pipe 2B is connected to the second intake passage 52B (see FIG. 3) of the second cylinder 21B of the compression mechanism 20 described later. The other end of the second intake pipe 2B is connected to the intake muffler 3.
• the names beginning with “first” and “second” may be referred to as names without "first” and "second”.
• the "first cylinder 21A" and the "second cylinder 21B" are collectively referred to as "cylinder".
• the suction muffler 3 functions as a muffler that reduces refrigerant noise and the like generated when the refrigerant flows into the rotary compressor 1.
• the suction muffler 3 also functions as an accumulator that can store liquid refrigerant.
• the suction muffler 3 is connected to the first suction passage 52A of the first cylinder 21A and the second suction passage 52B of the second cylinder 21B via the first suction pipe 2A and the second suction pipe 2B.
• compression mechanism 20 The compression mechanism 20 is connected to the rotating shaft 40, and compresses the refrigerant sucked in from the outside by the power of the rotating electric machine 30 transmitted by the rotating shaft 40.
• the refrigerant flowing into the suction muffler 3 is supplied to the compression mechanism 20 via the first suction pipe 2A and the second suction pipe 2B. That is, the compression mechanism 20 sucks in the external refrigerant via the first suction pipe 2A and the second suction pipe 2B, and compresses the refrigerant.
• the refrigerant compressed by the compression mechanism 20 is released into the sealed container 10.
• a rolling piston type compression mechanism is adopted as the compression mechanism 20.
• 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, and a partition plate 25.
• the upper bearing 24A, the lower bearing 24B, and the partition plate 25 are also referred to as bearings or blocking members.
• the first cylinder 21A is cylindrical and forms a first cylinder chamber 55A in the center.
• the first cylinder 21A is formed with a first intake passage 52A through which the refrigerant is drawn from the first intake pipe 2A, and a first discharge passage 53A through which the refrigerant is discharged to the discharge pipe 4 via the internal space of the sealed container 10.
• the first intake pipe 2A is press-fitted into the first intake passage 52A on the outer circumferential surface of the first cylinder 21A.
• the first piston 22A is fitted into the first eccentric shaft portion 40A of the rotating shaft 40, and rotates eccentrically together with the first eccentric shaft portion 40A to compress the refrigerant.
• the first vane 50A is located between the first intake passage 52A and the first discharge passage 53A, and is arranged in a first vane groove 56A formed to extend radially of the first cylinder 21A, separating the first cylinder chamber 55A into a first intake chamber 57A and a first compression chamber 58A.
• the first intake chamber 57A is connected to the first intake passage 52A
• the first compression chamber 58A is connected to the first discharge passage 53A.
• 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 partition plate 25 is positioned so as to abut against the lower end surface of the first cylinder 21A and the upper end surface of the second cylinder 21B, closing off the first cylinder chamber 55A and the second cylinder chamber 55B.
• 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 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 rotating shaft 40 is formed with an oil supply hole 42 that opens at the lower end 41 of the rotating shaft 40.
• the oil supply hole 42 extends along the rotation center of the rotating shaft 40.
• the rotating shaft 40 is also formed with a first oil supply port 43 and a second oil supply port 44.
• the first oil supply port 43 and the second oil supply port 44 serve as flow paths for supplying the refrigeration oil 6 sucked into the oil supply port 42 to the sliding parts of the compression mechanism 20.
• One end of the first oil supply port 43 and the second oil supply port 44 communicates with the oil supply hole 42.
• the other end of the first oil supply port 43 and the second oil supply port 44 opens at a location on the outer circumferential surface of the rotating shaft 40 that faces the compression mechanism 20.
• the other end of the first oil supply port 43 opens at a location that faces the upper bearing 24A of the compression mechanism 20.
• the other end of the second oil supply port 44 opens at a location facing the lower bearing 24B of the compression mechanism 20.
• a centrifugal pump 45 is provided inside the oil supply hole 42 of the rotating shaft 40.
• the centrifugal pump 45 is formed by twisting a plate-shaped member.
• the centrifugal pump 45 is a fluid machine that uses centrifugal force generated by the rotational motion of the rotating shaft 40 to suck up the refrigeration oil 6 stored in the bottom 13 of the sealed container 10 as a lubricant.
• the refrigeration oil 6 sucked up to the oil supply hole 42 by the centrifugal pump 45 is supplied to the sliding parts of the compression mechanism 20. Specifically, a portion of the refrigeration oil 6 sucked up to the oil supply hole 42 is supplied to the sliding parts between the upper bearing 24A of the compression mechanism 20 and the rotating shaft 40 through the first oil supply port 43.
• the refrigeration oil 6 for example, mineral oil-based, alkylbenzene-based, polyalkylene glycol-based, polyvinyl ether-based, and polyol ester-based lubricating oils are used.
• a current is supplied from a power source (not shown) to the windings provided on the laminated core of the stator 32, forming a rotating magnetic field in the stator 32. This causes the rotating magnetic field of the stator 32 to act on the permanent magnets provided in the rotor 31, causing the rotor 31 to rotate.
• the rotation of the rotor 31 is transmitted to the first piston 22A and the second piston 22B via the rotating shaft 40, causing the first piston 22A and the second piston 22B to perform eccentric rotational motion.
• 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.
• 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.
• 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. 24 is a side view of the supercharging mechanisms T1 and T2 of the rotary compressor 1 according to the first embodiment.
• FIG. 25 is a view of the impeller of the rotary compressor 1 according to the first embodiment.
• FIG. 26 is a view of the turbine of the rotary compressor 1 according to the first embodiment.
• FIG. 27 is a view of the connecting shaft of the rotary compressor 1 according to the first embodiment.
• FIG. 24(a) shows a side view of the supercharging mechanism T1
• FIG. 24(b) shows a side view of the supercharging mechanism T2.
• FIG. 25 and FIG. 26(a) shows a top view
• FIG. 25(b) shows a side view
• FIG. 25(c) shows a bottom view
• FIG. 26(d) shows a perspective view.
• FIG. 25 and FIG. 26(a) shows a top view
• FIG. 25(b) shows a side view
• FIG. 25(c) shows a bottom view
• 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.
• first turbine blade group 28Aa and the second turbine blade group 28Ba it is possible to arrange the first discharge valve 26A and the second discharge valve 26B radially outside the first turbine 28A and the second turbine 28B.
• first impeller blade group 29Aa and the second impeller blade group 29Ba it is possible to arrange the first suction chamber 57A and the second suction chamber 57B radially outside the first impeller 29A and the second impeller 29B.
• Figure 28 is an arrow view of the A-A cross section of Figure 18.
• Figure 29 is an arrow view of the B-B cross section of Figure 22. Note that Figure 28 is shown upside down.
• the first impeller vane group 29Aa has a first impeller vane base end group 29Aaa which is the base end side in the axial direction, and a first impeller vane tip end group 29Aab which is the tip end side in the axial direction.
• the first impeller vane base end group 29Aaa is configured so that the diameter of the first impeller vane base end group 29Aaa is larger than the diameter of the first impeller vane tip end group 29Aab.
• the first cylinder 21A is formed with a first step portion 21Aa which opens to a surface on one side in the height direction of the first cylinder 21A and communicates with the first intake passage 52A (first communication chamber 21Ab) and accommodates the outer periphery of the first impeller vane base end group 29Aaa.
• the second impeller blade group 29Ba includes a second impeller blade base end group 29Baa, which is the base end side in the axial direction, and a second impeller blade tip end group 29Bab, which is the tip end side in the axial direction.
• the diameter of the second impeller blade base end group 29Baa is configured to be larger than the diameter of the second impeller blade tip end group 29Bab.
• the first step 21Aa formed in the first cylinder 21A and the second step 21Ba formed in the second cylinder 21B are configured to accommodate the outer periphery of the first impeller blade base end group 29Aaa and the outer periphery of the second impeller blade base end group 29Baa, respectively. Therefore, the first impeller blade tip group 29Aab and the first impeller blade base end group 29Aaa can be arranged to be aligned with the inner surface of the first step 21Aa that communicates with the first intake passage 52A of the first cylinder 21A. As a result, it is possible to efficiently flow the refrigerant into the first impeller blade group 29Aa and efficiently flow the refrigerant out of the first impeller blade group 29Aa.
• the second impeller blade tip group 29Bab and the second impeller blade base group 29Baa can be arranged to be aligned with the inner surface of the second step 21Ba that communicates with the second intake passage 52B of the second cylinder 21B.
• the refrigerant can be efficiently introduced into the second impeller blade group 29Ba and efficiently circulated out of the second impeller blade group 29Ba.
• first and second stages 21Aa and 21Ba formed in the first and second cylinders 21A and 21B are configured to accommodate the outer periphery of the first and second impeller blade base end groups 29Aaa and 29Baa, respectively, so that the refrigerant can efficiently flow into the first and second impeller blade groups 29Aa and 29Ba, and can efficiently flow out of the first and second impeller blade groups 29Aa and 29Ba.
• 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 and 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, vanes that separate the cylinder chamber, which is formed by the inner circumference of the cylinder and the outer circumference of the piston, into an intake chamber and a compression chamber, and a height of the cylinder.
• the turbocharging mechanism T1 and T2 are provided with a bearing fixed to one side in the height direction to close one side of the cylinder chamber and to form a discharge flow path that discharges the compressed refrigerant out of the compression chamber, a blocking member fixed to the other side in the height direction of the cylinder 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 mechanism T1 and T2 are provided with a connecting shaft rotatably supported by the bearing, 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 rotated with the rotation of the turbine to promote the flow of the refrigerant flowing through the suction flow path.

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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 JP JP2025570366A patent/JPWO2025154119A1/ja active Pending
  • 2024-01-15 WO PCT/JP2024/000741 patent/WO2025154119A1/ja active Pending

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