WO2017090089A1 - Compresseur rotatif et dispositif de pompe à chaleur équipé de celui-ci - Google Patents

Compresseur rotatif et dispositif de pompe à chaleur équipé de celui-ci Download PDF

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Publication number
WO2017090089A1
WO2017090089A1 PCT/JP2015/082939 JP2015082939W WO2017090089A1 WO 2017090089 A1 WO2017090089 A1 WO 2017090089A1 JP 2015082939 W JP2015082939 W JP 2015082939W WO 2017090089 A1 WO2017090089 A1 WO 2017090089A1
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WIPO (PCT)
Prior art keywords
vane
rotary compressor
compression
permanent magnet
force
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Application number
PCT/JP2015/082939
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English (en)
Japanese (ja)
Inventor
哲英 横山
将吾 諸江
久範 鳥居
高橋　真一
幹一朗 杉浦
聡経 新井
Original Assignee
三菱電機株式会社
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2015/082939 priority Critical patent/WO2017090089A1/fr
Priority to JP2016544890A priority patent/JP6289646B2/ja
Publication of WO2017090089A1 publication Critical patent/WO2017090089A1/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

Definitions

  • the present invention relates to a rotary compressor whose capacity can be changed by switching the operation mode of a plurality of cylinders, and a heat pump device equipped with this rotary compressor.
  • the strengthening of energy-saving regulations for air-conditioning equipment is being promoted.
  • the latest new standard is characterized by evaluating the energy-saving performance under operating conditions closer to the actual load than the conventional standard.
  • the energy saving performance display in Japan used to be the efficiency evaluation display with the average cooling / heating COP under the rated conditions, but since 2011 the APF (Annual Energy Consumption Efficiency) calculated from the cooling / heating 4 conditions COP with intermediate conditions added since 2011 ) Changed to display.
  • APF Automatic Energy Consumption Efficiency
  • the low load condition is a condition in which the temperature difference between the outside air temperature and the room temperature is small and the amount of heat necessary to keep the room temperature constant is small.
  • the difference between the high pressure (Pd) and the low pressure (Ps) of the vapor compressor refrigeration cycle is small, and the amount of heat required in the steady state is small (for example, 25% or less of the rated capacity).
  • the capacity required for steady operation is about 10% to 50% of the rated condition, and the time for operation from low load conditions to intermediate conditions is longer than the time for rated operation. For this reason, in order to substantially evaluate the energy saving performance throughout the year, it has become a new issue to improve COP for low load conditions that were not subject to evaluation in the conventional standards.
  • Patent Document 1 discloses a configuration in which, in a two-cylinder rotary compressor, one refrigerant compression unit is in an uncompressed state at a low load to reduce the refrigerant circulation flow rate by half.
  • the compressor efficiency can be improved.
  • a part of the high-pressure gas compressed in the cylinder chamber that always performs a compression action is introduced into one of the blades (synonymous with vane) and the rear end (rear surface) of the blade (synonymous with vane).
  • the back surface portion means the entire back surface side excluding the tip side, the side surface, and the top and bottom surfaces of the vane.
  • the rear end portion indicates the position of the rearmost end of the back surface portion. If the back part is a parallel plane, it is synonymous with the rear end part, but if it has irregularities or curved shapes, it is a different position.
  • Embodiment 1 of Patent Document 2 includes a cylinder, a rotary piston housed in the cylinder so as to be eccentrically rotatable, and a vane housed in a vane groove provided in the cylinder so as to be reciprocally movable.
  • a magnet is provided in the vane groove and in the vane, and means for disposing the magnet in the vane groove and the magnet of the vane so as to repel each other is disclosed.
  • a magnet is disposed in the vicinity of the vane in contact with the rotating piston, and means for contacting the vane with the rotating piston by the magnetic force generated between the magnet and the rotating piston is disclosed. Has been.
  • the present invention has been made to solve such a problem.
  • the operation mode is appropriately switched without causing a reduction in reliability and efficiency by stably operating the vane without a compression spring even at a low load.
  • An object of the present invention is to obtain a highly efficient rotary compressor and a heat pump device equipped with the rotary compressor.
  • the rotary compressor according to the present invention includes two compression units, an electric motor, and a drive shaft that connects the two compression units and the electric motor, and each of the compression units compresses the sucked refrigerant.
  • a ring-shaped piston that rotates, and is inserted into the vane groove so as to be able to reciprocate back and forth in a direction toward the center of the cylinder chamber and in a direction away from the cylinder chamber.
  • a rotary compressor comprising: the cylinder chamber divided into a low pressure and a high pressure in a state in which the pressure chamber is in contact; and a vane having a back surface portion accommodated in the vane back chamber.
  • the portion has a first permanent magnet disposed behind the back surface portion of the vane, and acts forward with respect to the vane due to a difference in pressure acting on the tip portion and the back surface portion of the vane.
  • the rotary compressor according to the present invention it is possible to appropriately switch the operation mode without causing a reduction in reliability and efficiency by stably operating the vane without a compression spring even at a low load, A highly efficient rotary compressor and a heat pump device equipped with the compressor can be obtained.
  • FIG. 1 is a schematic cross-sectional view (cross section AA in FIG. 1) showing a compression operation state of the second compression section 20 according to Embodiment 1 of the present invention (the second piston 23 is at the bottom dead center position of a shaft rotation angle of 180 degrees). It is.
  • FIG. 1 is a schematic cross-sectional view (cross section AA in FIG. 1) showing a compression operation state of the second compression section 20 according to Embodiment 1 of the present invention (the second piston 23 is at the top dead center position at an axial rotation angle of 0 degrees).
  • FIG. 3 is a schematic cross-sectional view (cross section AA in FIG.
  • FIG. 1 It is a longitudinal cross-sectional view which shows the state (bottom dead center position of 180 degrees of shaft rotation angles) of the 2nd vane 24 when the 2nd compression part 20 which concerns on Embodiment 1 of this invention is a compression driving
  • FIG. 1 is a schematic longitudinal sectional view showing the structure of a rotary compressor 1 according to Embodiment 1 of the present invention.
  • 2 is a schematic cross-sectional view showing the compression operation state (the second piston 23 is at the bottom dead center position of the shaft rotation angle 180 degrees) of the second compression unit 20 according to Embodiment 1 of the present invention (A in FIG. 1).
  • 3 is a schematic cross-sectional view showing the compression operation state of the second compression unit 20 according to Embodiment 1 of the present invention (the second piston 23 is at the top dead center position at an axial rotation angle of 0 degrees) (A in FIG. 1). -A cross section).
  • FIG. 1 is a schematic longitudinal sectional view showing the structure of a rotary compressor 1 according to Embodiment 1 of the present invention.
  • 2 is a schematic cross-sectional view showing the compression operation state (the second piston 23 is at the bottom dead center position of the shaft rotation angle 180 degrees) of the second compression unit 20 according to Embodi
  • FIG. 4 is a schematic cross-sectional view (cross section AA in FIG. 1) showing the non-compression operation state (the second piston 23 is in the suction fixing position) of the second compression unit 20 according to Embodiment 1 of the present invention.
  • FIG. 5 is a longitudinal sectional view showing the state of the second vane 24 when the second compression unit 20 according to the first embodiment of the present invention is in the compression operation state (top dead center position at an axial rotation angle of 0 degrees).
  • FIG. 6 is a longitudinal sectional view showing the state of the second vane 24 (the switching position between the second force and the third force) when the second compression unit 20 according to Embodiment 1 of the present invention is in the compression operation state.
  • FIG. 5 is a longitudinal sectional view showing the state of the second vane 24 when the second compression unit 20 according to the first embodiment of the present invention is in the compression operation state (top dead center position at an axial rotation angle of 0 degrees).
  • FIG. 6 is a longitudinal sectional view showing the state of the second vane
  • FIG. 7 is a longitudinal sectional view showing the state of the second vane 24 (the bottom dead center position of the shaft rotation angle of 180 degrees) when the second compression unit 20 according to Embodiment 1 of the present invention is in the compression operation state.
  • FIG. 8 shows the magnetic force (first force) acting on the second vane 24 with respect to the distance (back gap) between the flat portion 33b of the yoke 33 and the back surface portion 24c of the second vane 24 according to Embodiment 1 of the present invention. 2 force) and a relationship with a magnetic force (a third force) attracted forward.
  • FIG. 9 is a diagram showing a basic configuration of heat pump apparatus 200 according to Embodiment 1 of the present invention. Note that the trapezoidal broken line shown in FIGS. 2 to 4 indicates the mounting position of the second yoke 43.
  • the rotary compressor 1 is used as one of main components of a heat pump device 200 (see FIG. 9) such as an air conditioner or a water heater, for example, and compresses a gas refrigerant into a high temperature and high pressure state.
  • a heat pump device 200 see FIG. 9
  • the refrigerant is circulated in the vapor compression refrigeration cycle.
  • the rotary compressor 1 includes a compression mechanism 99 including a first compression unit 10 and a second compression unit 20 in the internal space 7 of the hermetic shell 3.
  • the second compression unit 20 is driven by the electric motor 8 via the drive shaft 5.
  • the sealed shell 3 is, for example, a cylindrical sealed container with its upper end and lower end closed.
  • a lubricating oil reservoir 3 a that stores lubricating oil that lubricates the compression mechanism 99.
  • a compressor discharge pipe 2 led to an external refrigerant circuit is provided at the upper part of the hermetic shell 3.
  • the electric motor 8 has, for example, a variable rotation frequency by inverter control or the like, and includes a rotor 8a and a stator 8b.
  • the stator 8b is formed in a substantially cylindrical shape, and the outer peripheral portion is fixed to the sealed shell 3 by shrink fitting or the like.
  • a coil that is supplied with electric power from an external power source is wound around the stator 8b.
  • the rotor 8a has a substantially cylindrical shape, and is disposed on the inner peripheral portion of the stator 8b with a predetermined distance from the inner peripheral surface of the stator 8b.
  • the drive shaft 5 is fixed to the rotor 8a, and the electric motor 8 and the compression mechanism 99 are connected via the drive shaft 5. That is, as the electric motor 8 rotates, the rotational power is transmitted to the compression mechanism 99 via the drive shaft 5.
  • the drive shaft 5 is formed between a long shaft portion 5a constituting the upper portion of the drive shaft 5, a short shaft portion 5b constituting the lower portion of the drive shaft, and the long shaft portion 5a and the short shaft portion 5b.
  • the eccentric pin shaft portions 5c and 5d and the intermediate shaft portion 5e are configured.
  • the eccentric pin shaft portion 5c has a cylindrical shape whose central axis is eccentric by a predetermined distance from the rotation center axes of the long shaft portion 5a and the short shaft portion 5b. Arranged in the cylinder chamber 12.
  • the eccentric pin shaft portion 5d has a cylindrical shape whose central axis is eccentric by a predetermined distance from the rotation center axes of the long shaft portion 5a and the short shaft portion 5b, and a second cylinder of the second compression portion 20 described later. It is arranged in the chamber 22.
  • the eccentric pin shaft portion 5c and the eccentric pin shaft portion 5d are provided with a phase difference of 180 degrees.
  • the eccentric pin shaft portion 5c and the eccentric pin shaft portion 5d are connected by an intermediate shaft portion 5e.
  • the intermediate shaft portion 5e is disposed in a through hole of the intermediate partition plate 4 described later.
  • the long shaft portion 5 a is rotatably supported by the bearing portion 60 a of the first support member 60
  • the short shaft portion 5 b is freely rotatable by the bearing portion 70 a of the second support member 70. It is supported. That is, when the drive shaft 5 rotates, the eccentric pin shaft portions 5c and 5d are configured to eccentrically rotate in the first cylinder chamber 12 and the second cylinder chamber 22.
  • the 1st compression part 10 and the 2nd compression part 20 are constituted by the 1st cylinder 11 and the 2nd cylinder 21, the 1st piston 13 and the 2nd piston 23, the 1st vane 14, the 2nd vane 24, etc., respectively.
  • the Each of the first cylinder 11 and the second cylinder 21 is a flat plate in which a substantially cylindrical through hole that is substantially concentric with the drive shaft 5 (more specifically, the long shaft portion 5a and the short shaft portion 5b) is vertically formed. It is a member.
  • One end of the through hole of the first cylinder 11 is closed by the flange portion 60 b of the first support member 60, and the other end is closed by the intermediate partition plate 4 to form the first cylinder chamber 12.
  • the through hole of the second cylinder 21 is closed at one end by the flange portion 70 b of the second support member 70 and closed at the other end by the intermediate partition plate 4 to form the second cylinder chamber 22. ing.
  • first piston 13 and a second piston 23 are provided, respectively.
  • the first piston 13 and the second piston 23 are each formed in a ring shape, and are slidably provided on the eccentric pin shaft portions 5 c and 5 d of the drive shaft 5.
  • one end of each of the first cylinder 11 and the second cylinder 21 communicates with the first cylinder chamber 12 and the second cylinder chamber 22, respectively, and extends in the radial direction of the first cylinder chamber 12 and the second cylinder chamber 22. Extending first vane grooves 19 and second vane grooves 29 are formed.
  • the first vane groove 19 and the second vane groove 29 are respectively formed from the front and the first cylinder chamber 12 and the second cylinder chamber 22 in the direction toward the center of the first cylinder chamber 12 and the second cylinder chamber 22.
  • the 1st vane 14 and the 2nd vane 24 are provided so that reciprocation is possible to the back which is the direction which goes away.
  • the tip portions 14a and 24a of the first vane 14 and the second vane 24 come into contact with the outer peripheral portions of the first piston 13 and the second piston 23, respectively, so that the first cylinder chamber 12 and the second cylinder chamber 22 are sucked respectively. It is divided into a chamber and a compression chamber.
  • the first cylinder 11 and the second cylinder 21 are respectively connected to the rear end portions of the first vane groove 19 and the second vane groove 29, that is, the rear end portions of the first vane 14 and the second vane 24.
  • a first vane back chamber 15 and a second vane back chamber 25 for accommodating 14b and 24b are formed.
  • the first vane back chamber 15 and the second vane back chamber 25 are provided so as to penetrate the first cylinder 11 and the second cylinder 21 in the vertical direction.
  • the first vane back chamber 15 and the second vane back chamber 25 are partially opened in the internal space 7 of the hermetic shell 3, and the lubricant stored in the lubricant storage section 3 a is used as the first vane back chamber 15.
  • FIG. 1 The lubricating oil that has flowed into the first vane back chamber 15 and the second vane back chamber 25 flows between the first vane groove 19 and the second vane groove 29 and the side surfaces of the first vane 14 and the second vane 24, To reduce the sliding resistance between.
  • the rotary compressor 1 according to the first embodiment is configured such that the refrigerant compressed by the compression mechanism 99 is discharged into the internal space 7 of the sealed shell 3. For this reason, the first vane back chamber 15 and the second vane back chamber 25 have the same high-pressure atmosphere as the internal space 7 of the sealed shell 3.
  • the first cylinder 11 and the second cylinder 21 are connected to a suction muffler 6 for allowing a gas refrigerant to flow into the first cylinder chamber 12 and the second cylinder chamber 22, respectively.
  • the suction muffler 6 includes a container 6b, an inflow pipe 6a, and outflow pipes 6c and 6d.
  • the container 6b stores the low-pressure refrigerant that has flowed out of the evaporator constituting the refrigeration cycle.
  • the inflow pipe 6a guides the low-pressure refrigerant from the evaporator to the container 6b, and the outflow pipes 6c and 6d respectively pass the gas refrigerant out of the refrigerant stored in the container 6b via the cylinder suction channels 17 and 27. It plays a role of leading to the first cylinder chamber 12 and the second cylinder chamber 22.
  • first cylinder chamber 12 and the second cylinder chamber 22 are formed with discharge ports 18 and 28 for discharging a gas refrigerant compressed inside.
  • the discharge ports 18 and 28 communicate with through holes formed in the flange portions 60 b and 70 b of the first support member 60 and the second support member 70, and the first cylinder chamber 12 and the second cylinder holes are formed in the through holes.
  • On-off valves 18a and 28a are provided that open when the inside of the cylinder chamber 22 becomes a predetermined pressure or higher.
  • discharge mufflers 63 and 73 are attached to the first support member 60 and the second support member 70 so as to cover the through holes.
  • the basic compression mechanism configuration of the first compression unit 10 and the second compression unit 20 is the same, but the second compression unit 20 is different in that a switching mechanism 31 is installed.
  • the rotary compressor 1 according to Embodiment 1 includes the switching mechanism 31 in the second compression unit 20, thereby performing a parallel operation mode in which the first compression unit 10 and the second compression unit 20 are simultaneously compressed.
  • the first compression unit 10 performs a compression operation and the second compression unit 20 is configured to be switchable to a single operation mode in which a non-compression operation is performed.
  • FIG. 1 shows a longitudinal sectional view in the parallel operation mode, that is, when the first compression unit 10 and the second compression unit 20 are in the compression operation state.
  • 2 and 3 show the state of the second vane 24 in the parallel operation mode in which the second compression unit 20 is in the compression operation state.
  • the bottom dead center position and the shaft rotation angle 0 are respectively set to the shaft rotation angle 180 degrees.
  • 2 is a schematic cross-sectional view (cross section AA in FIG. 1) showing the top dead center position.
  • FIG. 4 shows the state of the second vane 24 when the second compression unit 20 is in the non-compression operation state.
  • the switching mechanism 31 is disposed in a storage chamber 37 of the second cylinder 21 provided behind the second vane back chamber 25.
  • the permanent magnet 32 is arrange
  • the yoke 33 is made of a concave magnetic material, and is composed of a flat portion 33b that is a bottom portion of the concave shape and both arm portions 33a that stand upright and project forward.
  • the permanent magnet 32 corresponds to the first permanent magnet of the present invention.
  • a rectangular parallelepiped permanent magnet 32 is attached to the back surface (rear surface) of the flat portion 33 b of the yoke 33. Further, when the second cylinder 21 is in a normal compression operation, the second vane 24 is at the top dead center position of the second piston 23 (the position of the second piston 23 in FIG. 3 and the shaft rotation angle of the second piston 23 is 0 degrees).
  • the yoke 33 is disposed so that the rear end portion 24b approaches the vicinity of the front-end side inner corners of the concave arm portions 33a of the yoke 33.
  • the permanent magnet 32 and the yoke 33 are covered with a holder 36 made of a nonmagnetic material, and the permanent magnet 32 and the yoke 33 are fixed.
  • the back side of the permanent magnet 32 is surrounded by the outer edge of the second cylinder 21 that is a magnetic material. If a gap is generated between the permanent magnet 32 and the outer edge of the second cylinder 21, a shim 38 of a magnetic material is inserted into the gap for adjustment.
  • the first vane 14 and the second vane 24 are subjected to suction pressure Ps (pressure of the low-pressure refrigerant sucked into the first cylinder chamber 12 and the second cylinder chamber 22) on the front end portions 14a, 24a side, and the rear end portions
  • suction pressure Ps pressure of the low-pressure refrigerant sucked into the first cylinder chamber 12 and the second cylinder chamber 22
  • the discharge pressure Pd acts on the back surface portions 14c and 24c including 14b and 24b.
  • the back surface portion refers to the entire back surface side excluding the tip side, the side surface side, and the top and bottom surface sides of the vane.
  • the rear end portion indicates the position of the rearmost end of the back surface portion. If the back part is a parallel plane, it is synonymous with the rear end part, but if it has irregularities or curved shapes, it is a different position.
  • both the first vane 14 and the second vane 24 have the first vane 14 and the second vane 24 according to the pressure difference (Pd ⁇ Ps) acting on the front end portions 14a and 24a and the back surface portions 14c and 24c.
  • a pressing force Fp that presses the vane 24 toward the first piston 13 and the second piston 23 acts.
  • a compression spring 40 is attached to the rear of the first vane back chamber 15, and the pressing force of the compression spring 40 acts on the first vane 14 in addition to the pressing force of the differential pressure.
  • the differential pressure (Pd ⁇ Ps) is small at the time of startup, the first vane 14 comes into contact with the first piston 13 by the pressing force of the compression spring 40 to perform the compression operation.
  • the attractive magnetic force Fm when the second piston 23 is performing the compression operation and the shaft rotation angle of the second piston 23 is 0 degree is defined as a first attractive magnetic force Fm1.
  • the relationship of pressing force Fpmax> first attractive magnetic force Fm1 is established.
  • the second vane 24 moves from the top dead center position (FIG. 3, the shaft rotation angle of the second piston 23 to 0 degrees) to the bottom dead center position (FIG. 2, the shaft rotation angle of the second piston 23 is 180 degrees). While reciprocating while contacting the peripheral surface of the piston 23, the compression operation state is maintained.
  • the attractive magnetic force Fm acting on the second vane 24 is such that the back surface portion 24c of the second vane 24 is applied to the front end portions of both arm portions 33a of the yoke 33 when the axial rotation angle of the second piston 23 is around 0 degrees. Since it is closest (shortest distance), it becomes the maximum.
  • the switching mechanism 31 around the permanent magnet 32, the yoke 33, and the second vane back chamber 25 is designed so that the attractive magnetic force Fm at this time becomes the first attractive magnetic force Fm1.
  • the attractive magnetic force Fm becomes smaller as the distance between the rear end portion 24b of the second vane 24 (here, synonymous with the back surface portion 24c) and the flat portion 33b of the yoke 33 (back surface gap) becomes smaller. Increases rapidly. That is, the rate of change of the attractive magnetic force Fm with respect to the moving distance of the second vane 24 (gradient of the attractive magnetic force Fm) increases rapidly.
  • the rear end portion 24 b of the second vane 24 is seated on the flat portion 33 b of the yoke 33 and is fixed to the attracting position by the magnetism of the permanent magnet 32. At this time, the distance between the flat portion 33b of the yoke 33 and the rear end portion 24b of the second vane 24 is the shortest.
  • the second attractive magnetic force Fm2 that works when the tip 24a of the second vane 24 is separated (while the magnet is being attracted) is such that the side surface of the second vane 24 has the concave shape of the yoke 33. Since the movement is almost parallel along the inner walls of both arms 33a, the rate of change of the attractive magnetic force Fm with respect to the moving distance of the second vane 24 (gradient of the attractive magnetic force Fm) is a substantially constant value in this section. This is characterized in that there is a section where the gradient of the attractive magnetic force Fm is very small (a constant attractive magnetic force section).
  • FIG. 5 is longitudinal sectional views showing the state of the second vane 24 when the second compression unit 20 is in the compression operation state. The switching position between the second force and the third force, and the bottom dead center position of the shaft rotation angle of 180 degrees are shown.
  • the second compression unit 20 according to the first embodiment has a lower dead center position where the second vane 24 moves most forward (center side of the second cylinder chamber 22) than the back surface portion 24c of the second vane 24.
  • a second yoke 43 is provided at the front position.
  • the second yoke 43 is provided at a position (height) different from the second cylinder chamber 22 below the second cylinder 21, that is, in the axial direction of the drive shaft 5.
  • the second yoke 43 is provided at a position (height) different from that of the second cylinder 21 in the axial direction of the drive shaft 5.
  • the second yoke 43 is attached to the nonmagnetic holder 36 with a bolt 44 made of a magnetic material.
  • the second yoke 43 includes a tip end portion 43 a that faces the lower surface portion of the second vane 24.
  • the position of the back surface portion 24 c of the second vane 24 is closer to the both arm portions 33 a of the yoke 33 than the bolt 44 at the top dead center position of the shaft rotation angle of 0 degree. Therefore, the magnetic flux flows from the permanent magnet 32 through the yoke 33 toward the back surface portion 24c of the second vane 24, passes through the second cylinder 21, and returns to the permanent magnet 32 (second force). .
  • a cylindrical metal material (magnetic material) having a high magnetic permeability is press-fitted into the back surface portion 24c of the second vane 24, and this functions as a vane suction point 41 to concentrate the magnetic flux. That is, a third force, which will be described later, acts on the vane suction portion 41 in a concentrated manner.
  • the portion of the second vane 24 other than the vane suction point can be formed of a material having a lower magnetic permeability than the vane suction point 41.
  • portions other than the vane suction portion of the second vane 24 are formed of a nonmagnetic material.
  • the second vane 24 reciprocates between a top dead center position with an axis rotation angle of 0 degrees and a bottom dead center position with an axis rotation angle of 180 degrees.
  • the side surface portion of the second vane 24 slides with the wall surface of the second vane groove 29, the upper surface portion of the second vane 24 slides with the lower surface portion of the intermediate partition plate 4, and the lower surface portion of the second vane 24.
  • the shaft rotation angle of 180 degrees where the second vane 24 is moving most forward it is outside (rearward) from the second vane groove 29, the intermediate partition plate 4 and the flange portion 70b.
  • the vane suction point 41 is arranged at a position where That is, the vane suction portion 41 is disposed at a position where it does not slide with the surrounding members.
  • the lateral position of the distal end portion 43a of the second yoke 43 is set at the same position as the vane suction point 41 at the bottom dead center position of the shaft rotation angle of 180 degrees in FIGS. It arrange
  • the distance from the back surface portion 24c of the second vane 24 to the bolt 44, and the distance from the back surface portion 24c of the second vane 24 to both arms 33a of the yoke 33. Is almost equivalent.
  • the magnetic flux is divided into a magnetic flux from the permanent magnet 32 through the yoke 33 toward the back surface portion 24 c of the second vane 24 and a magnetic flux from the permanent magnet 32 toward the bolt 44.
  • the shape of the tip 43a of the second yoke 43 is a wedge shape so that the magnetic flux passing through the bolt 44 passes through the second yoke 43 and again approaches the second vane 24.
  • the position of the back surface portion 24 c of the second vane 24 is farther from both the arm portions 33 a of the yoke 33 than the bolts 44 at the bottom dead center position of the shaft rotation angle of 180 degrees.
  • the tip end portion 43a of the second yoke 43 approaches the vane suction point 41, the magnetic flux passing through the bolts 44 easily flows, and a magnetic force (third force) that attracts the second vane 24 forward is generated.
  • FIG. 8 shows the magnetic force (first force) acting on the second vane 24 with respect to the distance (back gap) between the flat portion 33b of the yoke 33 and the back surface portion 24c of the second vane 24 according to Embodiment 1 of the present invention. 2 force) and a relationship with a magnetic force (a third force) attracted forward.
  • a strong attractive magnetic force about 7 N
  • the backward attractive magnetic force (second force) and the forward attractive magnetic force (third force) are both weakened.
  • a forward attractive magnetic force (about 3N) is generated by the third force.
  • the second vane 24 when the second compression unit 20 performs the compression operation under the low load condition, the second vane 24 has the bottom dead center position moved most forward. Then, a third force for sucking the second vane 24 forward acts. Therefore, in the rotary compressor 1 according to the first embodiment, when the second compression unit 20 performs the compression operation under the low load condition, the second vane 24 is separated from the second piston 23 at the bottom dead center position. This can be prevented, and the reliability and efficiency of the rotary compressor 1 can be prevented from decreasing.
  • FIG. 9 is a diagram showing a basic configuration of heat pump apparatus 200 according to Embodiment 1 of the present invention.
  • the heat pump device 200 has the same rotary compressor 1 as shown in FIG. 1, a four-way valve 201, an indoor heat exchanger 202, a decompression mechanism 203, and an outdoor heat exchanger 204, which are connected by a refrigerant circuit pipe 207. Constitutes a vapor compression refrigeration cycle.
  • the heat pump apparatus 200 for air conditioners is demonstrated as an example of the heat pump apparatus 200.
  • FIG. 1 The heat pump device 200 has the same rotary compressor 1 as shown in FIG. 1, a four-way valve 201, an indoor heat exchanger 202, a decompression mechanism 203, and an outdoor heat exchanger 204, which are connected by a refrigerant circuit pipe 207. Constitutes a vapor compression refrigeration cycle.
  • the heat pump apparatus 200 for air conditioners is demonstrated as an example of the heat pump apparatus 200.
  • the indoor unit B is provided with an indoor heat exchanger 202
  • the outdoor unit A is provided with a rotary compressor 1, a four-way valve 201, a pressure reducing mechanism 203, and an outdoor heat exchanger 204.
  • the heat pump device 200 can be switched between a heating operation and a cooling operation by a four-way valve 201.
  • the four-way valve 201 is connected to the heating operation path 201a indicated by the solid line in FIG.
  • the refrigerant gas compressed into the high temperature and high pressure state by the rotary compressor 1 flows into the indoor heat exchanger 202, and the indoor heat exchanger 202 operates as a heat radiation side heat exchanger (condenser).
  • the four-way valve 201 When performing the cooling operation, the four-way valve 201 is connected to the cooling operation path 201b indicated by a dotted line. Thereby, the suction side of the rotary compressor 1 is connected to the indoor heat exchanger 202, and the indoor heat exchanger 202 operates as a heat absorption side heat exchanger (evaporator).
  • the rotary compressor 1 includes the electric motor 8 and the two compression units (the first compression unit 10 and the second compression unit 20), and the single operation mode in which one compression unit is in a non-compression operation state.
  • the normal parallel operation mode in which both compression units are in the compression operation state is passively switched depending on the operation condition of the rotary compressor 1. Specifically, as described above, immediately after the operation of the rotary compressor 1 is started, or when the rotary compressor 1 has a low load (the temperature difference between the room and the outside is small), the differential pressure between the suction pressure and the discharge pressure is increased. In the small state, the operation is performed in the single operation mode. Alternatively, when the discharge pressure rises to the rated load and the differential pressure from the suction pressure increases after a while after startup, the pressing force Fp (first force) acting on the second vane 24 increases, and the parallel operation mode Switch to
  • the indoor unit B includes a temperature sensor 171 that detects the indoor temperature, and a temperature sensor 172 at the outlet of the indoor airflow that passes through the indoor heat exchanger 202.
  • the signals detected by the temperature sensors 171 and 172 are input to the heat pump capacity control device 160 described later.
  • the sensor used for control of the heat pump apparatus 200 is not limited to what was shown in FIG. 9,
  • coolant side of the indoor side heat exchanger 202 and the outdoor side heat exchanger 204, A temperature sensor and a pressure sensor provided on the suction side and the discharge side of the rotary compressor 1 can be appropriately employed as necessary.
  • the outdoor unit A has an inverter drive control device 150 that supplies power for driving the electric motor 8 of the rotary compressor 1 by a power source from the AC power source 140, and a detection that determines the operation mode based on the inverter waveform acquired from the device.
  • a determination unit 145 and a heat pump capacity control device 160 are provided.
  • the inverter drive control device 150, the detection determination unit 145, and the heat pump capacity control device 160 incorporate a circuit such as a storage unit that stores programs for performing various controls and a CPU that performs calculations.
  • the rotational frequency of the electric motor 8 rapidly increases (overshoot).
  • the temperature sensor 172 detects the operation mode.
  • the operating frequency of the electric motor 8 is determined again so that the obtained temperature approaches the target room temperature, and the inverter drive control device 150 is controlled so that the electric motor 8 operates at the determined operating frequency.
  • the temperature detected by the temperature sensor 172 is adjusted so that the fluctuation range of the target room temperature (dry bulb) falls within an allowable range (about ⁇ 1 ° C.).
  • the rotary compressor 1 includes the switching mechanism 31 in the second compression unit 20 so that the first compression unit 10 and the second compression unit 20 are simultaneously compressed.
  • the parallel operation mode to be performed and the single operation mode in which the first compression unit 10 performs the compression operation and the second compression unit 20 performs the non-compression operation can be performed.
  • the second vane 24 is separated from the second piston 23 at the bottom dead center position when the second compression unit 20 performs the compression operation under the low load condition. This can be prevented, and the reliability and efficiency of the rotary compressor 1 can be prevented from decreasing.
  • the rotary compressor 1 according to the first embodiment can stably operate even when the load is low, with the operation control in which the operation range of the plurality of cylinder chambers is switched and the capacity range is expanded when the load is low. Therefore, it is possible to realize an increase in efficiency and reliability of the rotary compressor 1. And also in the heat pump apparatus 200 provided with such a rotary compressor 1, efficiency improvement and improvement in reliability can be realized.
  • the rotary compressor 1 according to the first embodiment has a concave type that holds the second vane 24 in the second compression unit 20 when the second vane 24 is separated from the second piston 23.
  • a yoke 33 having a shape is provided. For this reason, the rotary compressor 1 according to the first embodiment can also keep the position of the second vane 24 stable when the second vane 24 is separated from the outer peripheral wall of the second piston 23.
  • a rotary compressor of a hermetic type high-pressure shell type (in which the first compression unit 10, the second compression unit 20, and the electric motor 8 are arranged in a hermetic shell having the same discharge pressure) is used.
  • the heat pump device has been described, the same configuration can be adopted in other shell types.
  • a semi-enclosed shell type, an intermediate pressure shell type, and a low pressure shell type the same effect is obtained in the case of a type in which a vane is pressed against a piston by a differential pressure to perform a compression operation. Can do.
  • FIG. The rotary compressor 1 according to the second embodiment is the same as the basic configuration and basic operation of the rotary compressor 1, the compression mechanism 99, and the second compression unit 20 according to the first embodiment.
  • the compression mechanism 99 according to No. 1 there is a difference in the configuration and operation of the attractive magnetic force generation unit forward of the second vane 24. Therefore, in this Embodiment 2, only a different part from the rotary compressor 1 which concerns on Embodiment 1 is demonstrated.
  • the same functions and configurations as those of the first embodiment are described using the same reference numerals.
  • FIG. 10 is a longitudinal cross-sectional view showing the state of the second vane 24 when the second compression unit 20 according to Embodiment 2 of the present invention is in the compression operation state (top dead center position of the shaft rotation angle 0 degree).
  • FIG. 11 is a cross-sectional view showing the state of the second vane 24 when the second compression unit 20 according to the second embodiment of the present invention is in the compression operation state (top dead center position of the shaft rotation angle 0 degree).
  • FIG. 12 is a longitudinal sectional view showing the state of the second vane 24 when the second compression unit 20 according to Embodiment 2 of the present invention is in the compression operation state (switching position between the second force and the third force).
  • FIG. 13 is a cross-sectional view showing the state of the second vane 24 when the second compression unit 20 according to the second embodiment of the present invention is in the compression operation state (switching position between the second force and the third force).
  • FIG. 14 is a vertical cross-sectional view showing the state of the second vane 24 when the second compression unit 20 according to Embodiment 2 of the present invention is in the compression operation state (bottom dead center position of the shaft rotation angle of 180 degrees).
  • FIG. 15 is a cross-sectional view showing the state of the second vane 24 when the second compression unit 20 according to Embodiment 2 of the present invention is in the compression operation state (bottom dead center position of the shaft rotation angle 180 degrees).
  • the trapezoidal broken line shown in FIGS. 11, 13, and 15 indicates the mounting position of the second yoke 43.
  • the second vane 24 has a concave notch 45 (non-suction portion) formed on the bottom surface.
  • a cylindrical metal material (magnetic material) having a high magnetic permeability which is the vane attracting portion 41, is provided at the back surface portion 24 c of the second vane 24, more specifically at the rear end portion of the notch portion 45. This position is a position where the vane suction point 41 and the surrounding members do not slide.
  • the position of the back surface portion 24 c of the second vane 24 is closer to the both arm portions 33 a of the yoke 33 than the bolts 44 at the top dead center position of the shaft rotation angle of 0 degree. Therefore, the magnetic flux flows from the permanent magnet 32 through the yoke 33 toward the back surface portion 24c of the second vane 24, passes through the second cylinder 21, and returns to the permanent magnet 32 (second force). .
  • the magnetic flux is divided into a magnetic flux directed from the permanent magnet 32 through the yoke 33 toward the vane back surface portion 24 c and a magnetic flux directed toward the bolt 44.
  • the magnetic flux passing through the bolt 44 tries to approach the second vane 24 again through the second yoke 43, but cannot exert a large attractive magnetic force because of the notch 45 in the bottom surface of the second vane 24.
  • the position of the back surface portion 24 c of the second vane 24 is farther from both the arm portions 33 a of the yoke 33 than the bolts 44 at the bottom dead center position of the shaft rotation angle of 180 degrees.
  • the tip 43a of the second yoke 43 approaches the vane suction point 41 instead of the notch 45, so that the magnetic flux passing through the bolts 44 flows easily, and the magnetic force (first force) attracts the second vane 24 forward. 3 forces) are generated.
  • the switching mechanism 31 is provided in the second compression unit 20 as in the first embodiment.
  • a parallel operation mode in which the compression unit 20 is simultaneously compressed and a single operation mode in which the first compression unit 10 performs a compression operation and the second compression unit 20 performs a non-compression operation can be performed.
  • the second vane 24 is located at the bottom dead center position. It can prevent separating from the 2nd piston 23, and can prevent that the reliability and efficiency of the rotary compressor 1 fall.
  • the operation control in which the operation range of the plurality of cylinder chambers is expanded by changing the operation mode at the time of low load is also achieved at the time of low load. Stable operation is possible. Therefore, it is possible to realize an increase in efficiency and reliability of the rotary compressor 1. And also in the heat pump apparatus 200 provided with such a rotary compressor 1, efficiency improvement and improvement in reliability can be realized.
  • Embodiment 3 FIG.
  • the rotary compressor 1 according to the third embodiment is the same as the basic configuration and basic operation of the rotary compressor 1, the compression mechanism 99, and the second compression unit 20 according to the first embodiment.
  • the compression mechanism 99 according to No. 1 there is a difference in the configuration and operation of the attractive magnetic force generation unit forward of the second vane 24. Therefore, in this Embodiment 3, only a different part from the rotary compressor 1 which concerns on Embodiment 1 is demonstrated.
  • the same functions and configurations as those in the first embodiment are described using the same reference numerals.
  • FIG. 16 is a schematic longitudinal sectional view showing the structure of the rotary compressor 1 according to Embodiment 3 of the present invention.
  • FIG. 17 is a longitudinal cross-sectional view showing the state of the second vane 24 when the second compression unit 20 according to Embodiment 3 of the present invention is in the compression operation state (top dead center position at an axial rotation angle of 0 degrees).
  • FIG. 18 is a cross-sectional view showing the state of the second vane 24 when the second compression unit 20 according to the third embodiment of the present invention is in the compression operation state (top dead center position at an axial rotation angle of 0 degrees).
  • FIG. 17 is a longitudinal cross-sectional view showing the state of the second vane 24 when the second compression unit 20 according to Embodiment 3 of the present invention is in the compression operation state (top dead center position at an axial rotation angle of 0 degrees).
  • FIG. 18 is a cross-sectional view showing the state of the second vane 24 when the second compression unit 20 according to the third embodiment of the present invention is in
  • FIG. 19 is a longitudinal sectional view showing a state of the second vane 24 (a switching position between the second force and the third force) when the second compression unit 20 according to Embodiment 3 of the present invention is in the compression operation state.
  • FIG. 20 is a cross-sectional view illustrating the state of the second vane 24 (the switching position between the second force and the third force) when the second compression unit 20 according to Embodiment 3 of the present invention is in the compression operation state.
  • FIG. 21 is a longitudinal sectional view showing the state of the second vane 24 when the second compression unit 20 according to the third embodiment of the present invention is in the compression operation state (bottom dead center position of the shaft rotation angle of 180 degrees).
  • FIG. 22 is a cross-sectional view showing the state of the second vane 24 (the bottom dead center position of the shaft rotation angle 180 degrees) when the second compression unit 20 according to Embodiment 3 of the present invention is in the compression operation state.
  • a vane suction point 41 of a metal material (magnetic material) having a high magnetic permeability is provided on the back surface portion 24 c of the second vane 24.
  • the second vane 24 includes a protruding vane suction portion 41 a that protrudes downward from the bottom surface of the second vane 24.
  • the protruding vane suction portion 41a is a vane suction portion where a third force acts as will be described later.
  • the projecting vane suction portion 41a is located at a position different from the second cylinder chamber 22 in the axial direction of the drive shaft 5 (more specifically, on the flange portion 70b side of the second support member 70 relative to the second cylinder chamber 22, It is arranged at a position on the outside of the flange portion 70b) at the dead center position.
  • the protruding vane suction portion 41 a is arranged at a position different from the second cylinder 21 in the axial direction of the drive shaft 5.
  • the said position of the protruding vane suction location 41a is a position where the protruding vane suction location 41a and a surrounding member do not slide.
  • the rotary compressor 1 is provided with a second permanent magnet 42 that generates a third force with respect to the second vane 24, in addition to the permanent magnet 32.
  • the second permanent magnet 42 is provided at a position facing the vane suction point 41 at the bottom dead center position of the shaft rotation angle of 180 degrees where the second vane 24 is moving most forward. That is, the second permanent magnet 42 is disposed at a position that is more forward than the back surface portion 24c of the second vane 24 at the bottom dead center position where the second vane 24 moves most forward. Further, the second permanent magnet 42 is disposed at a position (height) different from the second cylinder chamber 22 in the axial direction of the drive shaft 5, more specifically, on the flange portion 70 b side of the second support member 70.
  • the second permanent magnet 42 is arranged at a position (height) different from the second cylinder 21 in the axial direction of the drive shaft 5. Furthermore, in the third embodiment, the second permanent magnet 42 is disposed outside the flange portion 70b. In the third embodiment, the second permanent magnet 42 generates a magnetic field in a direction repelling the permanent magnet 32.
  • Such a second permanent magnet 42 is fixed to the flange portion 70 b of the second support member 70.
  • the second permanent magnet 42 is covered with a second holder 46 made of a nonmagnetic material in order to allow the magnetic flux to pass through the second vane 24 in a concentrated manner. For this reason, the second permanent magnet 42 is fixed to the flange portion 70 b of the second support member 70 via the second holder 46.
  • the position of the second permanent magnet 42 excluding the rear surface portion (location facing the protruding vane suction location 41a), the top surface portion, and the bottom surface portion. Is covered with the second yoke 43 (magnetic material).
  • the distance between the back surface portion 24c of the second vane 24 and both arm portions 33a of the yoke 33 is equal to the protruding vane suction of the second vane 24 at the top dead center position.
  • the distance is smaller than the distance between the portion 41a and the second permanent magnet 42 (the second yoke 43 when the second yoke 43 is provided). For this reason, the magnetic flux flows from the permanent magnet 32 through the yoke 33 toward the back surface portion 24 c of the vane, passes through the second cylinder 21, and returns to the permanent magnet 32. That is, a second force that sucks the second vane 24 backward acts on the second vane 24.
  • the distance between the portion 41a and the second permanent magnet 42 (the second yoke 43 when the second yoke 43 is provided) is substantially the same. For this reason, the magnetic flux flows from the permanent magnet 32 through the yoke 33 toward the back surface portion 24c of the vane, passes through the second cylinder 21, and returns to the permanent magnet 32 (second force).
  • the position of the back surface portion 24 c of the second vane 24 is moved away from both arm portions 33 a of the yoke 33 at the bottom dead center position of the shaft rotation angle of 180 degrees.
  • the protruding vane attracting portion 41a of the second vane 24 approaches the second permanent magnet 42 (the second yoke 43 when the second yoke 43 is provided). Therefore, a magnetic flux (third force) attracts the second vane 24 forward by generating a magnetic flux from the second permanent magnet 42 through the second yoke 43 toward the projecting vane suction portion 41a of the second vane 24. ) Occurs.
  • the second compression unit 20 since the second compression unit 20 includes the switching mechanism 31 as in the first embodiment, the first compression unit 10 and the second compression unit 10 are provided. A parallel operation mode in which the compression unit 20 is simultaneously compressed and a single operation mode in which the first compression unit 10 performs a compression operation and the second compression unit 20 performs a non-compression operation can be performed.
  • the second vane 24 when the second compressor 20 performs the compression operation under a low load condition, the second vane 24 is located at the bottom dead center position. It can prevent separating from the 2nd piston 23, and can prevent that the reliability and efficiency of the rotary compressor 1 fall.
  • the operation control in which the operation range of the plurality of cylinder chambers is expanded by changing the operation mode at the time of low load is also achieved at the time of low load. Stable operation is possible. Therefore, it is possible to realize an increase in efficiency and reliability of the rotary compressor 1. And also in the heat pump apparatus 200 provided with such a rotary compressor 1, efficiency improvement and improvement in reliability can be realized.

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

Abstract

L'invention concerne un compresseur rotatif (1) comprenant une première unité de compression (10) et une deuxième unité de compression (20), qui est pourvu, au niveau de la deuxième unité de compression (20), d'un mécanisme de commutation (31) pour commuter entre un état de fonctionnement de compression dans lequel une deuxième ailette (24) bute contre une surface périphérique extérieure d'un deuxième piston (23), et un état de fonctionnement sans compression dans lequel la deuxième ailette (24), ayant été écartée de la surface périphérique extérieure du deuxième piston (23), est attirée et fixée par un aimant permanent (32). La deuxième unité de compression (20) du compresseur rotatif (1) comprend en outre un deuxième étrier (43) qui est disposé plus en avant qu'une section de surface arrière (24c) de la deuxième ailette (24) de telle sorte qu'une troisième force aspirant la deuxième ailette (24) vers l'avant agisse au niveau d'une position de point mort bas dans laquelle la deuxième ailette (24) est déplacée le plus loin en avant.
PCT/JP2015/082939 2015-11-24 2015-11-24 Compresseur rotatif et dispositif de pompe à chaleur équipé de celui-ci WO2017090089A1 (fr)

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PCT/JP2015/082939 WO2017090089A1 (fr) 2015-11-24 2015-11-24 Compresseur rotatif et dispositif de pompe à chaleur équipé de celui-ci
JP2016544890A JP6289646B2 (ja) 2015-11-24 2015-11-24 ロータリ式圧縮機、及びこれを搭載したヒートポンプ装置

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PCT/JP2015/082939 WO2017090089A1 (fr) 2015-11-24 2015-11-24 Compresseur rotatif et dispositif de pompe à chaleur équipé de celui-ci

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS56163693U (fr) * 1980-05-07 1981-12-04
WO2015163257A1 (fr) * 2014-04-25 2015-10-29 三菱電機株式会社 Compresseur rotatif et dispositif de pompe à chaleur muni de celui-ci

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS56163693U (fr) * 1980-05-07 1981-12-04
WO2015163257A1 (fr) * 2014-04-25 2015-10-29 三菱電機株式会社 Compresseur rotatif et dispositif de pompe à chaleur muni de celui-ci

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