WO2014155802A1 - Compresseur rotatif multicylindre et dispositif à cycle de réfrigération - Google Patents

Compresseur rotatif multicylindre et dispositif à cycle de réfrigération Download PDF

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Publication number
WO2014155802A1
WO2014155802A1 PCT/JP2013/079429 JP2013079429W WO2014155802A1 WO 2014155802 A1 WO2014155802 A1 WO 2014155802A1 JP 2013079429 W JP2013079429 W JP 2013079429W WO 2014155802 A1 WO2014155802 A1 WO 2014155802A1
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WIPO (PCT)
Prior art keywords
blade
cylinder
chamber
roller
back chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2013/079429
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English (en)
Japanese (ja)
Inventor
平野　浩二
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Japan Corp
Original Assignee
Toshiba Carrier Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Toshiba Carrier Corp filed Critical Toshiba Carrier Corp
Priority to CN201380071563.3A priority Critical patent/CN105008721B/zh
Publication of WO2014155802A1 publication Critical patent/WO2014155802A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F04C18/3562—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • F04C28/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • 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
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type

Definitions

  • Embodiments of the present invention relate to a multi-cylinder rotary compressor and a refrigeration cycle apparatus including the multi-cylinder rotary compressor and constituting a refrigeration cycle.
  • a multi-cylinder rotary compressor having a plurality of cylinder chambers as a compression mechanism is frequently used.
  • a blade that contacts a roller in the cylinder chamber and divides the cylinder chamber into a suction chamber and a compression chamber, and a position where the blade does not contact the roller And a permanent magnet to be fixed to.
  • the blade is pressed against the roller by a high operating pressure supplied to the rear end side.
  • a low operating pressure is supplied to the rear end of the blade.
  • the pressure acting on the rear end of the blade becomes low, there is no pressure difference between the front end side and the rear end side of the blade, so there is no pressing force to press the blade against the roller, and the blade is fixed by the magnetic force of the permanent magnet. The By fixing the position of the blade, the blade does not contact the roller, so that the compression action of the cylinder is stopped.
  • a multi-cylinder rotary compressor of one embodiment includes a first cylinder, a second cylinder, a first roller, a second roller, a first blade, a second blade, and a blade back chamber. And an operating pressure supply unit, a permanent magnet, and a check valve mechanism.
  • the first cylinder includes a first cylinder chamber.
  • the second cylinder includes a second cylinder chamber.
  • the first roller rotates eccentrically in the first cylinder chamber.
  • the second roller rotates eccentrically in the second cylinder chamber.
  • the first blade is in contact with the first roller to partition the first cylinder chamber.
  • the second blade is in contact with the second roller to partition the second cylinder chamber and is made of a magnetic material.
  • the blade back chamber is provided on the rear end side of the second blade.
  • the operating pressure supply unit selectively supplies an operating pressure for moving the second blade toward the second roller in the blade back chamber.
  • the fixed component is disposed in a direction perpendicular to the moving direction of the second blade in the blade back chamber.
  • the permanent magnet is provided on the fixed component and fixes the second blade at a position where it does not contact the second roller.
  • the check valve mechanism is provided in the fixed component and discharges the pressure in the blade back chamber.
  • FIG. 1 is a schematic view showing an air conditioner according to the first embodiment.
  • FIG. 2 is an exploded perspective view showing a part of the compression mechanism of the air conditioner.
  • FIG. 3 is an enlarged cross-sectional view of a range F3 in FIG.
  • FIG. 4 is a plan view showing a second cylinder of the compression mechanism section.
  • FIG. 5 is a cross-sectional view showing the vicinity of the check valve mechanism of the air conditioner according to the second embodiment, similar to FIG.
  • FIG. 1 is a schematic diagram illustrating an air conditioner R that is an example of a refrigeration cycle apparatus according to the first embodiment.
  • the air conditioner R includes a multi-cylinder rotary compressor M, a refrigerant pipe P, a four-way switching valve 50, an outdoor heat exchanger 51, an expansion device 52, an indoor heat exchanger 53, The accumulator 32 is provided.
  • the multi-cylinder rotary compressor M is shown in a longitudinal sectional view.
  • the multi-cylinder rotary compressor M includes a sealed case 1, a compression mechanism unit 3, an electric motor unit 4 that is an example of a drive unit, and a rotary shaft 5.
  • the compression mechanism part 3 is provided in the lower part in the sealed case 1.
  • the electric motor unit 4 is provided in the upper part in the sealed case 1.
  • the rotating shaft 5 is connected to the electric motor unit 4 and the compression mechanism unit 3, and transmits the power generated by the electric motor unit 4 to the compression mechanism unit 3.
  • the compression mechanism section 3 includes a first cylinder 6a, a second cylinder 6b, a main bearing 7a, a sub bearing 7b, and an intermediate partition plate 2.
  • the first cylinder 6a is disposed on the upper side, and the second cylinder 6b is disposed below the first cylinder 6a.
  • a main bearing 7a is attached and fixed to the upper end surface of the first cylinder 6a.
  • a secondary bearing 7b is attached and fixed to the lower end surface of the second cylinder 6b.
  • An intermediate partition plate 2 is interposed between the first cylinder 6a and the second cylinder 6b.
  • the rotary shaft 5 passes through the first and second cylinders 6a and 6b.
  • the rotating shaft 5 includes a first eccentric part 5a and a second eccentric part 5b.
  • the first eccentric part 5a and the second eccentric part 5b are cylindrical with a circular plane having the same diameter, and are arranged with a phase difference of approximately 180 °.
  • the first eccentric portion 5a is accommodated in the first cylinder chamber 61 in the first cylinder 6a.
  • the second eccentric part 5b is accommodated in the second cylinder chamber 62 of the second cylinder 6b.
  • the 1st roller 9a is fitted by the surrounding surface of the 1st eccentric part 5a.
  • the 2nd roller 9b is fitted by the surrounding surface of the 2nd eccentric part 5b.
  • the first cylinder chamber 61 of the first cylinder 6a is formed by closing the internal space of the first cylinder 6a by the main bearing 7a and the intermediate partition plate 2.
  • the second cylinder chamber 62 of the second cylinder 6b is formed by closing the internal space of the second cylinder 6b by the intermediate partition plate 2 and the auxiliary bearing 7b.
  • the first and second cylinder chambers 61 and 62 are formed to have the same diameter and height. Part of the peripheral walls of the first and second rollers 9a and 9b can be moved eccentrically while making line contact with part of the inner surfaces of the first and second cylinder chambers 61 and 62 via the lubricating oil film.
  • the first and second rollers 9a and 9b are accommodated in the first and second cylinder chambers 61 and 62, respectively. The first and second rollers 9a and 9b rotate as the rotating shaft 5 rotates.
  • the discharge muffler 8a that is doubled is attached to the main bearing 7a.
  • the discharge muffler 8a covers a discharge valve mechanism provided in the main bearing 7a. Both the discharge mufflers 8a are provided with discharge holes.
  • a single discharge muffler 8b is attached to the auxiliary bearing 7b.
  • the discharge muffler 8b covers a discharge valve mechanism provided in the sub bearing 7b.
  • the discharge muffler 8b is not provided with a discharge hole.
  • the discharge valve mechanism of the main bearing 7a is opposed to the first cylinder chamber 61 and is opened when the inside of the first cylinder chamber 61 rises to a predetermined pressure due to the compression action in the first cylinder chamber 61.
  • the compressed gas in the first cylinder chamber 61 is discharged into the discharge muffler 8a.
  • the discharge valve mechanism of the sub-bearing 7b faces the second cylinder chamber 62 and opens when the pressure in the second cylinder chamber 62 rises to a predetermined pressure due to the compression action in the second cylinder chamber 62.
  • the compressed gas in the second cylinder chamber 62 is discharged into the discharge muffler 8b.
  • a discharge gas guide path is provided across the auxiliary bearing 7b, the second cylinder 6b, the intermediate partition plate 2, the first cylinder 6a, and the main bearing 7a.
  • the discharge gas guide path guides the high-pressure gas discharged from the second cylinder chamber 62 through the discharge valve mechanism into the discharge muffler 8b into the double discharge muffler 8a disposed in the upper part.
  • An oil reservoir 14 for collecting lubricating oil is formed at the inner bottom of the sealed case 1. Substantially the entire compression mechanism 3 is immersed in the lubricating oil in the oil reservoir 14. An oil supply passage for supplying lubricating oil in the oil reservoir 14 is provided across the lower end surface of the rotating shaft 5 and each sliding portion of the compression mechanism unit 3.
  • FIG. 2 is an exploded perspective view showing a part of the compression mechanism section 3.
  • FIG. 2 schematically shows a main part of the compression mechanism unit 3.
  • a first blade groove 10 a communicating with the first cylinder chamber 61 and a first blade back chamber 11 a are formed in the first cylinder 6 a.
  • the first blade back chamber 11a is disposed on the opposite side of the first cylinder chamber 61 across the first blade groove 10a, and communicates with the first blade groove 10a.
  • a first blade 12a is movably accommodated in the first blade groove 10a.
  • the tip end portion of the first blade 12 a can protrude and retract into the first cylinder chamber 61.
  • the rear end portion of the first blade 12a can protrude and retract into the first blade back chamber 11a.
  • the second cylinder 6b is formed with a second blade groove 10b communicating with the second cylinder chamber 62 and a second blade back chamber 11b.
  • the second blade back chamber 11b communicates with the second blade groove 10b.
  • One end opening of the second blade back chamber 11 b is closed by the intermediate partition plate 2.
  • the other end opening of the second blade back chamber 11 b is closed by a closing member 18.
  • the second blade back chamber 11b communicates with the inside of the sealed case 1 through a check valve mechanism 70 described later.
  • the second blade groove 10b accommodates the second blade 12b in a movable manner.
  • the tip of the second blade 12 b can protrude and retract into the second cylinder chamber 62.
  • the second blade back chamber 11b is located on the rear end side of the second blade 12b.
  • the rear end portion of the second blade 12b can protrude and retract into the second blade back chamber 11b.
  • the second blade 12b is made of a magnetic material.
  • the tip portions of the first and second blades 12a and 12b are formed in a substantially arc shape in plan view. These leading end portions protrude into the opposing first and second cylinder chambers 61 and 62, and the first and second rollers 9a are disposed on the outer peripheral walls of the opposing first and second rollers 9a and 9b. , 9b regardless of the rotation angle.
  • the first cylinder 6 a is provided with a lateral hole 63 that communicates the first blade back chamber 11 a with the outside of the first cylinder chamber 61.
  • the spring member 13 is accommodated in the horizontal hole 63.
  • the spring member 13 is interposed between the end surface of the rear end portion of the first blade 12a and the inner peripheral wall of the sealed case 1, and applies an elastic force toward the first roller 9a to the first blade 12a.
  • the tip of the second blade 12 b receives the pressure of the second cylinder chamber 62.
  • the rear end portion of the second blade 12b receives the pressure of the second blade back chamber 11b.
  • the back pressure toward the second roller 9b is applied or not applied to the second blade 12b due to the pressure difference between the pressure applied to the front end portion and the rear end portion.
  • a check valve mechanism 70 is provided in the intermediate partition plate 2 as a fixed component located in a direction perpendicular to the moving direction of the second blade 12b of the second blade back chamber 11b.
  • FIG. 3 is an enlarged cross-sectional view of a range F3 in FIG.
  • FIG. 3 shows an enlarged view of the vicinity of the second blade back chamber 11b of the second cylinder 6b.
  • the check valve mechanism 70 includes a discharge path 71, a valve body 72, and a valve retaining ring 73.
  • the check valve mechanism 70 constitutes a so-called free valve.
  • the discharge path 71 is provided at a position opposite to the second blade back chamber 11 b in the intermediate partition plate 2 in the axial direction of the rotating shaft 5, and extends in the axial direction of the rotating shaft 5 to penetrate the intermediate partition plate 2. is doing.
  • the axial direction of the rotating shaft 5 is a direction perpendicular to the moving direction of the second blade 12b.
  • the other end of the discharge path 71 opens between the intermediate partition plate 2 and the first cylinder 6a. For this reason, the discharge path 71 communicates with the second blade back chamber 11 b and the inside of the sealed case 1.
  • the range F ⁇ b> 31 shows a state where the discharge path 71 is cut in a direction perpendicular to the direction in which the discharge path 71 extends.
  • the discharge path 71 has a circular cross-sectional shape as an example.
  • the valve body 72 is accommodated in the discharge path 71.
  • the valve body 72 is movable in the discharge path 71 between a position where the second blade back chamber 11b is closed and a position where the second blade back chamber 11b is opened.
  • the valve body 72 and the surrounding structure will be specifically described.
  • a permanent magnet 74 is disposed at a connection portion between the discharge path 71 and the second blade back chamber 11 b.
  • the permanent magnet 74 has a cylindrical shape having a through hole 75 at the center. For this reason, even if the permanent magnet 74 is fixed to the discharge path 71, the discharge path 71 is not blocked by the permanent magnet 74 by the through hole 75 of the permanent magnet 74.
  • the valve body 72 includes a main body portion 76 and a plurality of extending portions 77.
  • the main body 76 has a plate shape with a circular planar shape having a size for closing the through hole 75 of the permanent magnet 74.
  • a range F31 is a state in which the main body 76 is on the permanent magnet 74 and the through hole 75 is closed.
  • the extending portion 77 extends outward from the main body portion 76.
  • a plurality of extending portions 77 are provided at equal angles with respect to the center of the main body portion 76. In the present embodiment, as an example, four extending portions 77 are provided.
  • the extending portion 77 is formed so that a gap with the inner surface of the discharge path 71 is extremely small. As a result, the main body 76 is maintained in a position overlapping the through hole 75 in the direction in which the discharge path 71 extends.
  • a gap is formed in the circumferential direction. For this reason, when the valve body 72 moves away from the permanent magnet 74 while maintaining the above-described posture, the through hole 75 communicates with the discharge path 71 through the gap between the extending portions 77. In addition, a gap is provided between the extending portion 77 and the inner surface of the discharge path 71 so that the valve body 72 can move in the discharge path 71 while maintaining the above-described posture.
  • the position where the second blade back chamber 11 b is closed in the valve body 72 is a position where the valve body 72 is fixed to the permanent magnet 74. By being fixed, the main body 76 closes the through hole 75 of the permanent magnet 74.
  • the position where the second blade back chamber 11 b is opened is a position where the valve body 72 is separated from the permanent magnet 74.
  • the extension portions 77 communicate with the through hole 75.
  • the valve retaining ring 73 is provided on the opposite side of the permanent magnet 74 with the valve body 72 interposed therebetween.
  • the valve retaining ring 73 is provided along the inner surface of the discharge path 71 and protrudes toward the inside of the discharge path 71.
  • valve body 72 Since the inside of the valve retaining ring 73 penetrates, the discharge path 71 is not blocked by the valve retaining ring 73.
  • the valve body 72 does not move beyond the valve retaining ring 73 by being caught by the valve retaining ring 73.
  • the valve body 72 is movable between the permanent magnet 74 and the valve retaining ring 73.
  • the valve body 72 is made of a magnetic material. For this reason, the valve body 72 is fixed to the permanent magnet 74 so as to close the through hole 75.
  • the magnetic force of the permanent magnet 74 will be specifically described later.
  • the second blade 12b is formed of a magnetic material as described above. For this reason, the movement of the second blade 12 b is fixed by the magnetic force of the permanent magnet 74. More specifically, when the second blade 12b moves to a position facing the permanent magnet 74 in the axial direction of the rotary shaft 5, in a state where a low-pressure back pressure is acting on the second blade 12b, The second blade 12 b is fixed at a position facing the permanent magnet 74 by the magnetic force of the permanent magnet 74.
  • a discharge refrigerant pipe P is connected to the upper end portion of the sealed case 1 constituting the multi-cylinder rotary compressor M.
  • the refrigerant pipe P is sequentially communicated with devices constituting the heat pump refrigeration cycle, and is connected to an upper end portion of an accumulator 32 that is attached and fixed to the sealed case 1 via a fixture 31.
  • the lower end of the accumulator 32 and the sealed case 1 are connected via a refrigerant pipe P2 for suction.
  • the refrigerant pipe P2 passes through the sealed case 1 and is connected to the peripheral end surface of the intermediate partition plate 2.
  • the intermediate partition plate 2 is provided with a branch guide path 80 that branches into a bifurcated shape from the peripheral surface portion to which the refrigerant pipe P2 is connected in the axial direction.
  • FIG. 4 is a plan view showing the second cylinder 6b. As shown by a one-dot chain line in FIG. 4, one branch guide path 80 communicates with the first cylinder chamber 61. The other branch guide path communicates with the second cylinder chamber 62 as in FIG. The accumulator 32 and the first and second cylinder chambers 61 and 62 of the multi-cylinder rotary compressor M are always in communication.
  • the pressure control pipe P ⁇ b> 1 is provided so as to extend to an upper position than the upper ends of the sealed case 1 and the accumulator 32.
  • a pressure switching valve 33 which will be described later, is provided at the end of the pressure control pipe P1.
  • the pressure switching valve 33 uses a four-way switching valve used in an air conditioner including a heat pump refrigeration cycle capable of switching between cooling and heating operations.
  • the other end of the pressure control pipe P1 communicates with the second blade back chamber 11b.
  • the other end of the pressure control pipe P ⁇ b> 1 enters the sealed case 1 through the sealed case 1, and is connected to the closing member 18.
  • a back pressure introduction passage H communicating with the second blade back chamber 11b is formed.
  • the other end of the pressure control pipe P1 communicates with the back pressure introduction passage H.
  • the first branch pipe (high pressure pipe) 35 is branched from the refrigerant pipe P connected to the upper end of the sealed case 1.
  • the first branch pipe 35 is connected to the first port Pa of the pressure switching valve 33.
  • a pressure control pipe P ⁇ b> 1 is connected to the second port Pb of the pressure switching valve 33.
  • a second branch pipe 36 branched from the refrigerant pipe P on the refrigerant introduction side of the accumulator 32 is connected to the third port Pc of the pressure switching valve 33.
  • the fourth port Pd of the pressure switching valve 33 is always closed by the plug 37.
  • the inverted U-shaped valve 38 accommodated in the pressure switching valve 33 has a position where the third port Pc and the fourth port Pd communicate with each other and a two-dot chain line.
  • the second port Pb and the third port Pc are electromagnetically switched to a position where they communicate with each other.
  • the first port Pa is always open, and the fourth port Pd is always closed.
  • the first port Pa and the second port Pb are in direct communication, and the third port Pc and the fourth port Pd are in communication via the inverted U-shaped valve 38. ing. However, since the fourth port Pd is closed by the plug 37, the first port Pa and the second port Pb are in communication.
  • the pressure switching valve 33 is a four-way switching valve that is a standard product used in a refrigeration cycle constituting a normal heat pump type air conditioner. Instead of this four-way switching valve, Even if a three-way valve is used, or a combination of a plurality of on-off valves, the same effect can be obtained.
  • the blade back pressure control mechanism K is constituted by the pressure switching valve 33, the pressure control pipe P1, the first and second branch pipes 35 and 36, and the back pressure introduction passage H provided in the closing member 18. Is configured.
  • the blade back pressure control mechanism K can guide the second blade back chamber 11b by switching between high pressure and low pressure, and can apply the back pressure to the second blade 12b.
  • the multi-cylinder rotary compressor M is connected to a four-way switching valve 50 through a refrigerant pipe P.
  • the four-way switching valve 50 is connected to the outdoor heat exchanger 51 through the refrigerant pipe P.
  • the expansion device 52 is connected to the indoor heat exchanger 53 via the refrigerant pipe P.
  • the indoor heat exchanger 53 is connected to the accumulator 32 via the refrigerant pipe P and the four-way switching valve 50.
  • the accumulator 32 is connected to the multi-cylinder rotary compressor M via the refrigerant pipe P2.
  • the liquid refrigerant led out from the outdoor heat exchanger 51 is led to the expansion device 52 and adiabatically expands. Then, the refrigerant is guided to the indoor heat exchanger 53 to evaporate by exchanging heat with the indoor air, and takes away the latent heat of evaporation from the indoor air to perform an indoor cooling action. That is, the indoor heat exchanger 53 functions as an evaporator.
  • the evaporative refrigerant led out from the indoor heat exchanger 53 is sucked into the multi-cylinder rotary compressor M through the four-way switching valve 50, is compressed as described above, and circulates in the refrigeration cycle.
  • the four-way switching valve 50 When the heating operation is selected, the four-way switching valve 50 is switched, and the gas refrigerant discharged from the multi-cylinder rotary compressor M to the refrigerant pipe P passes through the four-way switching valve 50 to the indoor heat exchanger 53 as indicated by a broken line arrow. Guided and condensed by exchanging heat with room air. The indoor air absorbs the heat of condensation of the indoor heat exchanger 53 serving as a condenser, so that the temperature rises and an indoor heating action is obtained.
  • the liquid refrigerant led out from the indoor heat exchanger 53 is led to the expansion device 52, adiabatically expands and led to the outdoor heat exchanger 51 to evaporate.
  • the evaporative refrigerant derived from the outdoor heat exchanger 51 which is an evaporator, is sucked into the multi-cylinder rotary compressor M from the four-way switching valve 50, compressed as described above, and circulates in the refrigeration cycle.
  • switching between full capacity operation (first operation) and half capacity operation (second operation) can be selected in each of the above-described cooling operation and heating operation.
  • first operation full capacity operation
  • second operation half capacity operation
  • the above-described refrigeration cycle during the cooling operation is configured, and the inverted U-shaped valve 38 housed in the pressure switching valve 33 of the blade back pressure control mechanism K is switched.
  • the pressure switching valve 33 is controlled so that the second port Pb and the third port Pc communicate with each other as indicated by a two-dot chain line in FIG.
  • a refrigerant pipe P communicating from the indoor heat exchanger 53 to the accumulator 32, a second branch pipe 36, a pressure switching valve 33, a pressure control pipe P1, a back pressure introduction passage H, and a second blade back chamber 11b are provided. It becomes a communication state.
  • an operation signal is sent to the motor unit 4 and the rotary shaft 5 is driven to rotate.
  • the first and second rollers 9 a and 9 b move eccentrically in the first and second cylinder chambers 61 and 62.
  • the first blade 12a is pressed and urged against the spring member 13, and the tip end part slidably contacts the peripheral wall of the first roller 9a to bisect the inside of the first cylinder chamber 61.
  • the low-pressure refrigerant gas evaporated in the indoor heat exchanger 53 is guided from the accumulator 32 to the refrigerant pipe P2 on the suction side, and is guided to the two branch guide paths 80 provided in the intermediate partition plate 2 of the multi-cylinder rotary compressor M. The Then, the air is sucked into the first cylinder chamber 61 and the second cylinder chamber 62 from the respective branch guide paths 80.
  • the low-pressure gas refrigerant filling the second blade back chamber 11b applies a low-pressure back pressure to the rear end portion of the second blade 12b. Since the tip of the second blade 12b facing the second cylinder chamber 62 is in a low pressure atmosphere, the rear end of the second blade 12b facing the second blade back chamber 11b is also in a low pressure atmosphere. No differential pressure is generated between the front end portion and the rear end portion of the second blade 12b. In other words, there is no pressure in the second blade back chamber 11b to urge the second blade 12b toward the second roller 9b.
  • the tip of the second blade 12b is kicked by the second roller 9b and moves backward as shown in FIG. Then, the rear end portion of the second blade 12b contacts or approaches the permanent magnet 74 disposed on the second blade back chamber 11b, and the second blade 12b is magnetically attracted to the permanent magnet 74.
  • the range F4 is shown enlarged.
  • a range F4 shows the vicinity of the permanent magnet 74 in an enlarged manner.
  • the second blade 12b Since there is no pressure in the second blade back chamber 11b for urging the second blade 12b toward the second roller 9b, the second blade 12b is, as shown in FIG. The tip of 12b is fixed at a position where it does not protrude into the second cylinder chamber 62. For this reason, since the second cylinder chamber 62 is not divided into the suction chamber and the compression chamber, the second roller 9b fitted to the second eccentric portion 5b of the rotating shaft 5 runs idle. As a result, no compression action is performed in the second cylinder chamber 62. In other words, the second cylinder chamber 62 is in a cylinder-free operation state.
  • the first blade 12 a receives the elastic force of the spring member 13.
  • the tip of the first blade 12a abuts on the peripheral wall of the first roller 9a, and divides the first cylinder chamber 61 into two chambers, a compression chamber and a suction chamber.
  • the first roller 9a moves eccentrically, the volume on the compression chamber side decreases, and the sucked gas is gradually compressed to increase the pressure.
  • the discharge valve mechanism When the pressure in the first cylinder chamber 61 rises to a predetermined value, in other words, when the pressure in the first cylinder chamber 61 is increased, the discharge valve mechanism is opened and the increased pressure is discharged to the discharge mufflers 8a and 8b. The Further, it is guided into the sealed case 1 to fill the sealed case 1.
  • the high-pressure gas refrigerant filled in the sealed case 1 is discharged to the refrigerant pipe P, constitutes a refrigeration cycle as described above, and performs an indoor cooling action.
  • the compression operation is not performed in the second cylinder chamber 62, and the compression operation is performed only in the first cylinder chamber 61.
  • the inside of the sealed case 1 is filled with the high-pressure gas compressed in the first cylinder chamber 61 and is in a high-pressure atmosphere.
  • the lubricating oil in the oil reservoir 14 formed at the inner bottom of the sealed case 1 is also in a high pressure state.
  • the lubricating oil in the oil reservoir 14 enters the discharge path 71 from the opening of the discharge path 71.
  • the valve body 72 closes the through hole 75 by the magnetic force of the permanent magnet 74, the weight of the valve body 72, and the pressure of the lubricating oil. In other words, the valve body 72 closes the discharge path 71.
  • a low-pressure gas refrigerant is guided to the back pressure introduction passage H.
  • a low-pressure gas refrigerant is guided to the pressure control pipe P1 and the back pressure introduction passage H, fills the second blade back chamber 11b, and applies a low pressure back pressure to the second blade 12b.
  • the sealed case 1 is filled with compressed high pressure gas and is in a high pressure state, and the lubricating oil collected in the oil reservoir 14 is also affected by the high pressure.
  • the low-pressure gas refrigerant evaporated in the indoor heat exchanger 53 is guided from the accumulator 32 to the refrigerant pipe P2 on the suction side, and is sucked into the first and second cylinder chambers 61 and 62 through the branch guide path 80. Since the compression action is performed in the first cylinder chamber 61, the gas refrigerant whose pressure has been increased fills the sealed case 1.
  • the high-pressure gas refrigerant is guided from the sealed case 1 to the refrigerant pipe P on the discharge side and circulates in the above-described refrigeration cycle.
  • a part of the high-pressure gas refrigerant is diverted from the refrigerant pipe P to the first branch pipe 35, passes through the pressure switching valve 33, the pressure control pipe P 1, and the back pressure introduction passage H of the closing member 18, so that the second blade back. It is introduced into the chamber 11b.
  • the rear end portion of the second blade 12b receives a high back pressure.
  • the tip of the second blade 12b faces the second cylinder chamber 62 in a low pressure atmosphere.
  • the second blade 12b is pushed into the second cylinder chamber 62 against the magnetic attraction by the permanent magnet 74 due to the differential pressure between the pressure acting on the front end and the pressure acting on the rear end.
  • the magnetic force of the permanent magnet 74 will be specifically described.
  • the magnetic force of the permanent magnet 74 is such a magnetic force that the second blade 12 b is pushed out into the second cylinder chamber 62 by the differential pressure generated as described above when full capacity operation is selected.
  • the second blade groove 10b reciprocates while the tip of the second blade 12b is in contact with the peripheral surface of the second roller 9b. Since the second blade 12 b bisects the second cylinder chamber 62 into a compression chamber and a suction chamber, a compression action is performed in the second cylinder chamber 62.
  • the first cylinder chamber 61 and the second cylinder chamber 62 are simultaneously compressed to perform full capacity operation.
  • the pressure in the second blade back chamber 11b and the pressure of the lubricating oil in the oil reservoir 14 are the same.
  • the valve body 72 is urged to close the through hole 75 by its own weight and the magnetic force of the permanent magnet 74.
  • Lubricating oil in the oil reservoir 14 enters the second blade back chamber 11b through the clearance, and further is guided to the back pressure introduction passage H over time, and rises in the pressure control pipe P1. If the half capacity operation is continued for a long time, the back pressure introduction passage H is likely to be filled with lubricating oil. Then, there is a case where the full-capacity operation is switched as it is.
  • full capacity operation may be started under conditions where the outside air is cold.
  • the high-pressure gas refrigerant is led from the pressure switching valve 33 to the second blade back chamber 11b through the pressure control pipe P1 and the back pressure introduction passage H, and the gas refrigerant condenses as the time elapses. It turns into a refrigerant. That is, there is a possibility that the lubricating oil and liquid refrigerant, which are incompressible fluids, fill the second blade back chamber 11b, the back pressure introduction passage H, and the pressure control pipe P1.
  • the gas component evaporates from the incompressible fluid due to the heat generated by the operation of the compression mechanism unit 3, and only a pure liquid remains.
  • the reciprocating motion of the second blade 12b is directly received by the incompressible fluid that is completely liquid in the second blade back chamber 11b, and there is almost no buffering effect. If the high rotation operation is performed as it is, the flow of the incompressible fluid cannot follow the reciprocating operation of the second blade 12b.
  • valve body 72 opens quickly with respect to the pressure increase in the second blade back chamber 11b, so that the incompressible fluid in the back pressure introduction passage H and the pressure control pipe P1 is The oil is quickly discharged to the oil reservoir 14 in the sealed case 1. For this reason, problems such as the pressure pulsation as described above can be avoided, and the oil level of the oil reservoir 14 can be prevented from being lowered.
  • the check valve mechanism 70 and the permanent magnet 74 are provided on the intermediate partition plate 2, the check valve mechanism 70 and the permanent magnet 74 can be simultaneously assembled by assembling the intermediate partition plate 2. it can. For this reason, the efficiency of the assembly work of the compression mechanism part 3 can be improved. In other words, the efficiency of the assembly work of the multi-cylinder rotary compressor M can be improved.
  • the permanent magnet 74 is arranged in a direction perpendicular to the moving direction of the second blade 12b. For this reason, even if the second blade 12b reciprocates in the second blade groove 10b during full capacity operation, the second blade 12b does not contact the permanent magnet 74 at that time. For this reason, the permanent magnet 74 is not damaged due to the contact.
  • the intermediate partition plate 2 is an example of a fixed component that is disposed in a direction perpendicular to the moving direction of the second blade 12b of the second blade back chamber 11b.
  • the permanent magnet 74 can fix the valve body 72 at a position where the through hole 75 is closed even during full capacity operation.
  • the opening direction of the through-hole 75 is not limited.
  • the axial direction of the rotary shaft 5 is a direction in which gravity acts
  • the valve body 72 is positioned above the second blade back chamber 11b. That is, the valve body 72 moves between a position where the second blade back chamber 11b is opened and a position where the second blade back chamber 11b is opened by moving up and down in the direction in which gravity acts.
  • the valve body 72 can use its own weight in order to close the through hole 75. Since the multi-cylinder rotary compressor M includes the permanent magnet 74, for example, even if the through hole 75 is provided at the lower end of the second blade back chamber 11b, the valve body 72 may block the through hole 75. it can.
  • the permanent magnet 74 has a function of fixing the second blade 12b to a position where it does not come into contact with the second roller 9b when the second cylinder 6b is stopped, and fixing the valve body 72 to a closed position during full capacity operation. Have. That is, the number of parts can be reduced by using the permanent magnet 74 as the check valve mechanism 70.
  • FIG. 5 is a cross-sectional view showing the vicinity of the check valve mechanism 70 of the present embodiment in the same manner as FIG. As shown in FIG. 5, in this embodiment, the check valve mechanism 70 includes an urging mechanism 79 that urges the valve body 72 to a position where the through hole 75 is closed.
  • the shape of the discharge path 71 is different from that of the first embodiment.
  • a narrow portion 78 is formed between the permanent magnet 74 and the valve retaining ring 73 in the discharge path 71.
  • the flow path width in the discharge path 71 is narrowed.
  • the channel shape in the narrow portion 78 is the same as that of the through hole 75.
  • the narrow portion 78 is formed continuously with respect to the permanent magnet 74.
  • the valve body 72 is accommodated between the narrow portion 78 and the valve retaining ring 73. As described above, the flow path shape in the narrow portion 78 is the same shape as the through hole 75. For this reason, the valve body 72 can open and close the flow path in the narrow portion 78.
  • the urging mechanism 79 is formed between the valve body 72 and the valve retaining ring 73.
  • the biasing mechanism 79 includes a spring member 81 that is an example of a biasing member and a spring seat 82.
  • the spring member 81 is a coil spring as an example.
  • the spring receiving seat 82 is engaged with the valve retaining ring 73 and supports one end of the spring member 81. The other end of the spring member 81 urges the valve body 72 toward the narrow portion 78.
  • the valve element 72 closes the flow path in the narrow portion 78 by being biased by the spring member 81.
  • the valve body 72 moves against the urging force of the spring member 81 and opens the flow path in the narrow portion 78.
  • the flow path in the narrow portion 78 and the through hole 75 of the permanent magnet 74 communicate with each other. For this reason, the valve body 72 opens the through hole 75 by moving against the urging force of the spring member 81.
  • valve body 72 is positioned at the closed position by the urging force of the spring member 81, and therefore may not be formed of a magnetic material. In the present embodiment, the same effect as in the first embodiment can be obtained.
  • the second blade 12 b is formed of a magnetic material that can be fixed to the permanent magnet 74 as an example.
  • the 2nd blade 12b should just be provided with the part formed with the magnetic material in the part. And if the part formed with this magnetic body material is fixed to the permanent magnet 74, if the 2nd braid
  • valve body 72 is entirely formed of a magnetic material as an example, but as another example, a part thereof may be formed of a magnetic material.
  • the blade back pressure control mechanism K is an example of an operating pressure supply unit.
  • the intermediate partition plate 2 is used as an example of a fixed component.
  • a permanent magnet 74 and a check valve mechanism 70 may be provided on a component fixed to the lower end of the second cylinder chamber 6b.
  • the closing member 18 may be used. As described above, by providing the permanent magnet 74 and the check valve mechanism 70 in one fixed component, the efficiency of the assembly work can be improved.

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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 porte sur un compresseur rotatif multicylindre, qui comprend : des premier et second cylindres; des premier et second rouleaux qui tournent excentriquement dans les chambres des premier et second cylindres; une première pale servant à diviser l'intérieur de la chambre du premier cylindre; une seconde pale servant à diviser l'intérieur de la chambre du second cylindre, la seconde pale étant formée d'un matériau magnétique; une chambre d'extrados de pale destinée à recevoir la partie d'extrémité de la seconde pale; une partie de fourniture de pression de travail servant à fournir sélectivement une pression de travail à l'intérieur de la chambre d'extrados de pale; un élément de fixation disposé dans une direction perpendiculaire à la direction de mouvement de la seconde pale dans la chambre d'extrados de pale; un aimant permanent fourni à l'élément de fixation, l'aimant permanent fixant la seconde pale dans une position qui n'est pas en contact avec le second rouleau; et un mécanisme de clapet de non-retour fourni à l'élément de fixation.
PCT/JP2013/079429 2013-03-27 2013-10-30 Compresseur rotatif multicylindre et dispositif à cycle de réfrigération Ceased WO2014155802A1 (fr)

Priority Applications (1)

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CN201380071563.3A CN105008721B (zh) 2013-03-27 2013-10-30 多气缸旋转压缩机和制冷循环装置

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JP2013-065922 2013-03-27
JP2013065922A JP2016106194A (ja) 2013-03-27 2013-03-27 多気筒回転圧縮機と冷凍サイクル装置

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011030809A1 (fr) * 2009-09-11 2011-03-17 東芝キヤリア株式会社 Compresseur rotatif à multiples cylindres et dispositif de cycle de réfrigération
JP2011127475A (ja) * 2009-12-16 2011-06-30 Toshiba Carrier Corp 多気筒ロータリ式圧縮機と冷凍サイクル装置
JP4856091B2 (ja) * 2005-02-23 2012-01-18 エルジー エレクトロニクス インコーポレイティド 容量可変型ロータリ圧縮機及びこれを備える冷却システム

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Publication number Priority date Publication date Assignee Title
JPS58104387A (ja) * 1981-12-17 1983-06-21 Hitachi Ltd ロ−タリ式圧縮機
JP3762043B2 (ja) * 1997-01-17 2006-03-29 東芝キヤリア株式会社 ロータリ式密閉形圧縮機および冷凍サイクル装置
CN102132046B (zh) * 2008-08-29 2014-08-06 东芝开利株式会社 密闭型压缩机、双汽缸旋转式压缩机和制冷循环装置
KR20120015843A (ko) * 2010-08-13 2012-02-22 삼성전자주식회사 용량가변 회전압축기 및 이를 포함하는 공조시스템

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4856091B2 (ja) * 2005-02-23 2012-01-18 エルジー エレクトロニクス インコーポレイティド 容量可変型ロータリ圧縮機及びこれを備える冷却システム
WO2011030809A1 (fr) * 2009-09-11 2011-03-17 東芝キヤリア株式会社 Compresseur rotatif à multiples cylindres et dispositif de cycle de réfrigération
JP2011127475A (ja) * 2009-12-16 2011-06-30 Toshiba Carrier Corp 多気筒ロータリ式圧縮機と冷凍サイクル装置

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