WO2017031669A1 - 旋转式压缩机和具有其的冷冻循环装置 - Google Patents

旋转式压缩机和具有其的冷冻循环装置 Download PDF

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Publication number
WO2017031669A1
WO2017031669A1 PCT/CN2015/087931 CN2015087931W WO2017031669A1 WO 2017031669 A1 WO2017031669 A1 WO 2017031669A1 CN 2015087931 W CN2015087931 W CN 2015087931W WO 2017031669 A1 WO2017031669 A1 WO 2017031669A1
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Prior art keywords
port
rotary compressor
cylinder
valve port
piston
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PCT/CN2015/087931
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English (en)
French (fr)
Inventor
杨国用
向卫民
伏拥军
Original Assignee
广东美芝制冷设备有限公司
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Application filed by 广东美芝制冷设备有限公司 filed Critical 广东美芝制冷设备有限公司
Priority to US15/503,494 priority Critical patent/US10465682B2/en
Priority to ES15901940T priority patent/ES2911212T3/es
Priority to PCT/CN2015/087931 priority patent/WO2017031669A1/zh
Priority to EP15901940.5A priority patent/EP3343040B1/en
Priority to JP2017515828A priority patent/JP6408698B2/ja
Publication of WO2017031669A1 publication Critical patent/WO2017031669A1/zh

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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
    • 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
    • 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
    • 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
    • F04C23/008—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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • 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
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
    • 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
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings

Definitions

  • the present invention relates to the field of compressor equipment, and in particular to a rotary compressor and a refrigeration cycle apparatus therewith.
  • the evaporation temperature is lowered, the capacity of the refrigeration cycle system is lowered, and the performance of the ordinary single-stage rotary compressor is deteriorated.
  • the capacity jet boosting scheme can effectively improve the capacity of the refrigeration cycle system, but the ordinary high-capacity two-cylinder jet booster compressor still performs the twin-cylinder operation when the compression load is small, which makes the operation efficiency worse.
  • the present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides a rotary compressor having the advantages of simple and reasonable structure, high operation efficiency, wide application range, and excellent low-temperature heating effect.
  • the present invention also proposes a refrigeration cycle apparatus having the above rotary compressor.
  • a rotary compressor includes: a reservoir; a housing provided outside the reservoir, a discharge port formed on the housing; a compression mechanism, the compression The mechanism is disposed in the housing, the compression mechanism includes a main bearing, a cylinder assembly, a sub-bearing, two pistons and two sliding plates, and the main bearing and the sub-bearing are respectively disposed in an axial direction of the cylinder assembly
  • the cylinder assembly includes two cylinders having a compression chamber and a partition disposed between the two cylinders, each of which is formed with a vane groove, an intake port, and an exhaust port, each of which
  • the pistons are disposed in the corresponding compression chambers and are rollable along an inner wall of the compression chamber, and each of the sliding sheets is movably disposed in a corresponding one of the sliding grooves, in the two cylinders
  • the head of the slider on one of the cylinders abuts against the corresponding peripheral wall of the piston, the slider on the other of the two two cylinders
  • the rotary compressor according to the present invention has the advantages of high operation efficiency, wide application range, and excellent low-temperature heating effect.
  • rotary compressor apparatus may further have the following additional technical features:
  • the first air outlet and the second air outlet are formed on the partition.
  • the first air outlet and the second air outlet are formed on the main bearing and the sub-bearing, respectively.
  • the second air vent is located in a rolling direction of the first air vent along the piston Adjacent to the side of the exhaust port.
  • the rotary compressor further includes: a one-way valve provided at the second air injection port to unidirectionally pass into the compression cavity of the other cylinder Into the refrigerant.
  • a tail portion of the slider on the other cylinder is provided with a slider braking device, when a difference between a pressure of a tail portion of the slider and a pressure of a head portion of the slider is greater than
  • the sliding piece is separated from the sliding piece braking device by the sliding brake device when the braking force is applied to the sliding piece, and the head of the sliding piece and the corresponding outer peripheral wall of the piston are stopped.
  • the braking force is 2N to 10N.
  • the third valve port is directly connected to the discharge port or the interior of the housing.
  • the first reversing assembly is a three-way valve.
  • a refrigeration cycle apparatus comprising the rotary compressor according to the first aspect of the present invention; the second reversing assembly, the second reversing assembly including the first to fourth interfaces, the first The interface is connected to the discharge port of the rotary compressor, the fourth interface is connected to the accumulator; the outdoor heat exchanger, the first end of the outdoor heat exchanger is connected to the second interface; a first end of the indoor heat exchanger is connected to a third interface, a second end of the indoor heat exchanger is connected to a second end of the outdoor heat exchanger; and a flasher, the flashing Connected between the second end of the indoor heat exchanger and the second end of the outdoor heat exchanger, wherein the flasher and the first air vent of the rotary compressor and the The second jet is connected.
  • the overall performance of the refrigeration cycle apparatus is improved.
  • FIG. 1 is a cross-sectional view of an angle of a rotary compressor in accordance with an embodiment of the present invention
  • Figure 2 is a cross-sectional view of another angle of the rotary compressor shown in Figure 1, in which the first valve port of the first reversing assembly is in communication with the second valve port;
  • Figure 3 is a cross-sectional view of another angle of the rotary compressor shown in Figure 1, in which the first valve port of the first reversing assembly is in communication with the third valve port;
  • Figure 4 is a cross-sectional view taken along line D-D of Figure 2;
  • Figure 5 is a cross-sectional view of a rotary compressor in accordance with another embodiment of the present invention.
  • Figure 6 is a cross-sectional view of a rotary compressor in accordance with still another embodiment of the present invention.
  • Fig. 7 is a schematic view showing the system configuration of a refrigeration cycle apparatus according to an embodiment of the present invention.
  • 100 a second reversing component; 101: a first interface; 102: a second interface;
  • 500 a first throttle component
  • 600 a second throttle component
  • 421 main bearing
  • 4211 first exhaust valve
  • 431 a first muffler
  • 432 a second muffler
  • 44 a jet pipe; 441: a first air outlet; 442: a second air outlet; 443: a one-way valve;
  • 452 a second cylinder; 4521: a second compression chamber; 4522: a second sliding vane;
  • 461 a first piston
  • 462 a second piston
  • 471 a first sliding piece
  • 472 a second sliding piece
  • first reversing assembly 491: first valve port; 492: second valve port; 493: third valve port.
  • a rotary compressor 700 according to an embodiment of the first aspect of the present invention will now be described with reference to Figs.
  • a rotary compressor 700 includes: a reservoir 1, a housing 2, a compression mechanism, and a first reversing assembly 49.
  • the casing 2 is provided outside the accumulator 1, and the casing 2 is formed with a discharge port 21.
  • the rotary compressor 700 may be a vertical compressor.
  • the housing 2 may be formed into a generally hollow cylindrical shape that is hollow and sealed, and the central axis of the housing 2 may extend in a vertical direction.
  • the outlet 21 can penetrate the top wall of the casing 2 in the up and down direction and is discharged
  • a vertically extending exhaust pipe 22 may be inserted at the port 21 for discharging the gaseous refrigerant (or the mixed portion of the liquid refrigerant and the lubricating oil) inside the casing 2, and the accumulator 1 is disposed outside the casing 2.
  • the present invention is not limited thereto, and the rotary compressor 700 according to the present invention may also be a horizontal compressor, in which case the central axis of the casing 2 may extend in the horizontal direction.
  • the rotary compressor 700 will be described as a vertical compressor.
  • the compression mechanism is disposed in the housing 2, and the compression mechanism includes a main bearing 421, a cylinder assembly, and a sub-bearing 422.
  • the main bearing 421 and the sub-bearing 422 are respectively disposed at axial ends of the cylinder assembly, for example, in the example of FIG.
  • the main bearing 421 may be provided at the top of the cylinder assembly and the sub-bearing 422 may be provided at the bottom of the cylinder assembly.
  • the cylinder assembly includes two cylinders having a compression chamber and a partition 453 disposed between the two cylinders, that is, the cylinder assembly includes two cylinders, and the partition 453 is disposed between the two cylinders, each The cylinders each have a compression chamber.
  • the cylinder assembly includes a first cylinder 451 disposed above the partition 453 and a second cylinder 452 disposed below the partition 453, a main bearing 421, a first cylinder 451, and a partition 453 A first compression chamber 4511 is defined therebetween, and a second compression chamber 4521 is defined between the partition 453, the second cylinder 452, and the sub-bearing 422.
  • the compression mechanism further includes two pistons and two sliding plates, each of which is formed with a sliding groove, an air inlet and an exhaust port, and each piston is disposed in the corresponding compression chamber and along the inner wall of the compression chamber Rollable, each slider is movably disposed in a corresponding slider slot.
  • Each of the exhaust ports directly or indirectly communicates with the inside of the casing 2, and is in communication with the discharge port 21.
  • the two sliding sheets are a first sliding piece 471 and a second sliding piece 472, respectively, and the two pistons are a first piston 461 and a second piston 462, respectively, formed on the first cylinder 451.
  • the first piston 461 is disposed in the first compression chamber 4511 and is slidable along an inner wall of the first compression chamber 4511.
  • the groove 4512 is extendable in the radial direction of the first cylinder 451.
  • the first sliding piece 471 is movably disposed in the first sliding plate groove 4512 along the longitudinal direction of the first sliding plate groove 4512, and the second sliding plate 452 is formed in the second sliding plate 4512. a sliding slot 4522, a second suction opening 4523 and a second exhaust opening 4524.
  • the second piston 462 is disposed in the second compression chamber 4521. and is rotatable along an inner wall of the second compression chamber 4521.
  • the second sliding slot 4522 can be Extending along the radial direction of the second cylinder 452, the second slider 472 is movably disposed in the second slider groove 4522 along the length direction of the second slider groove 4522.
  • the head of the vane on one of the two cylinders abuts against the outer peripheral wall of the corresponding piston, and the vane on the other of the two cylinders is selectively contacted or disengaged from the corresponding piston. That is to say, the following two possibilities are included.
  • the first possibility is that when the head of the first sliding piece 471 on the first cylinder 451 is stopped against the outer peripheral wall of the first piston 461, the second cylinder 452 is The second sliding piece 472 is selectively in contact with or separated from the second piston 462; the second possibility is: when the head of the second sliding piece 472 on the second cylinder 452 is stopped against the outer peripheral wall of the second piston 462,
  • the first slider 471 on a cylinder 451 is selectively contacted or separated from the first piston 461.
  • the head of the sliding piece can be understood as the end of the sliding piece adjacent to the central axis of the corresponding compression cavity, and the opposite end is the tail end of the sliding piece, that is, the end of the sliding piece away from the central axis of the corresponding compression cavity. .
  • a spring 481 may be disposed between the tail of the first sliding piece 471 and the inner side wall of the housing 2, and the spring 481 always pushes the head of the first sliding piece 471 and the outer peripheral wall of the first piston 461.
  • a sliding piece braking device 482 can be disposed, and the sliding piece braking device 482 can be controlled under certain working conditions.
  • the head of the second slider 472 is abutted against the outer peripheral wall of the second piston 462, and the head of the second slider 472 is controlled to be separated from the outer peripheral wall of the second piston 462 under other operating conditions.
  • the means for controlling the first slider 471 and the second slider 472 are not limited to the spring 481 and the slider brake device 482.
  • the slider brake device 482 will be described in detail below and will not be described herein.
  • a first air injection port 441 for introducing a refrigerant into the compression chamber of the one of the cylinders is formed on the compression mechanism and is used for the single
  • a second air injection port 442 of refrigerant is introduced into the compression chamber of the other cylinder (i.e., the cylinder in which the slider is selectively contacted or separated from the corresponding piston).
  • the compression mechanism is formed with a first air injection port 441 for introducing refrigerant into the first compression chamber 4511 of the first cylinder 451, and the compression mechanism is further formed with a unidirectional direction to the second cylinder.
  • the second air injection port 442 of the refrigerant is introduced into the second compression chamber 4521 of the 452.
  • the one-way access is understood to mean that the refrigerant in the second compression chamber 4521. does not flow back to the second air injection port 442.
  • the specific configuration positions of the first air outlet 441 and the second air outlet 442 will be described in detail below, and are not described herein.
  • the backstop function can be implemented by providing the one-way valve 443. That is, the rotary compressor 700 may further include a one-way valve 443 provided at the second air injection port 442 to unidirectionally move toward the other cylinder (ie, a sliding piece and a corresponding piston are provided therein) A refrigerant is introduced into the compression chamber of the selectively contactable or disengageable cylinder.
  • the one-way valve 443 is provided at the second gas injection port 442 to unidirectionally move to the second compression chamber of the second cylinder 452.
  • the refrigerant is introduced into the 4521 to prevent the refrigerant in the second compression chamber 4521 from flowing back to the second gas injection port 442.
  • the present invention is not limited thereto, and the backstop function can also be realized by setting other devices.
  • the first reversing assembly 49 includes a first valve port 491, a second valve port 492, and a third valve port 493, the first valve port 491 and the other cylinder (ie, therein)
  • the slide valve is connected to the suction port of the cylinder which is selectively contacted or separated by the corresponding piston, the second valve port 492 is connected to the accumulator 1, and the third valve port 493 and the exhaust port (the first exhaust port)
  • the 4514 and the second exhaust port 4524 can both be in communication, and one of the second valve port 492 and the third valve port 493 can selectively communicate with the first valve port 491, that is, under certain operating conditions,
  • the second valve port 492 is in communication with the first valve port 491 (as shown in FIG.
  • the third valve port 493 is in communication with the first valve port 491 (as shown in FIG. 3).
  • the first reversing assembly 49 is a three-way valve.
  • the present invention is not limited thereto, and the first reversing component 49 can also be configured as other structural forms that can realize the three-way switching effect.
  • the third valve port 493 is in communication with the exhaust port, and since the exhaust port communicates with the inside of the casing 2 and the discharge port 21, the third valve port 493 can communicate with the inside of the casing 2 and the discharge port 21 That is, the third valve port 493 can draw the exhaust pressure from the exhaust pipe 22 or the hermetic casing 2. As shown in Figures 1-3, the third valve port 493 is connected to the discharge port 21 to achieve communication with the exhaust port. Alternatively, as shown in Fig. 6, the third valve port 493 is directly connected to the inside of the casing 2 to achieve communication with the exhaust port. This facilitates processing and implementation.
  • the first suction port 4513 on the first cylinder 451 is connected and in communication with the accumulator 1, and the second suction port 4523 on the second cylinder 452 is coupled to the first reversing assembly.
  • the first valve port 491 of 49 is connected and communicated, and the first exhaust port 4514 on the first cylinder 451 is in direct communication with the inside of the casing 2 or indirectly communicated through the first muffler 431 described below, on the second cylinder 452
  • the second exhaust port 4524 is in direct communication with the interior of the housing 2 or indirectly via a second muffler 432 as described below such that the first exhaust port 4514 and the second exhaust port 4524 can pass through the interior of the housing 2 Connected to the discharge port 21.
  • the second valve port 492 of the first reversing assembly 49 is connected and in communication with the accumulator 1, and when the second valve port 492 is in communication with the first valve port 491, the accumulator 1 can pass the second inhalation.
  • the port 4523 conveys the refrigerant to the second compression chamber 4521.
  • the third valve port 493 of the first reversing assembly 49 is in communication with the first exhaust port 4514 or the second exhaust port 4524, in other words, the third valve port 493 of the first reversing assembly 49 and the housing 2
  • the inside and the discharge port 21 are in communication such that when the third valve port 493 is in communication with the first valve port 491, the second suction port 4523 communicates with the inside of the casing 2 and the discharge port 21.
  • two modes of operation can be realized by switching the two commutation modes by the first reversing unit 49, namely, a full load operation mode and a partial load operation mode.
  • the first reversing assembly 49 is disposed such that the first valve port 491 communicates with the second valve port 492 such that the second cylinder
  • the second suction port 4523 of the 452 is in communication with the accumulator 1.
  • the low-pressure refrigerant from the refrigeration cycle apparatus 1000 (which will be described later in detail) having the evaporation side pressure of Ps passes through the accumulator 1, passes through the first suction port 4513, enters the first cylinder 451, and passes through the first reversing assembly. 49.
  • the second air inlet 4523 enters the second cylinder 452.
  • the first cylinder 451 and the second cylinder 452 all work normally, and the low pressure refrigerant is compressed by the first cylinder 451 and the second cylinder 452, respectively, and the pressure is increased to Pd.
  • the first exhaust port 4514 and the second exhaust port 4524 enter the sealed casing 2 and are discharged from the exhaust pipe 22 at the discharge port 21, and the rotary compressor 700 is operated in a double cylinder.
  • the rotary compressor 700 operates in a full load mode of operation.
  • the refrigerant of the circulation device 1000 having a pressure of Pm can be made to flow through the first air injection port 441 to the first compression chamber 4511, and the refrigerant can be unidirectionally ejected to the second compression chamber 4521 through the second air outlet 442, thereby realizing The twin-cylinder jet operation of the rotary compressor 700.
  • the first reversing assembly 49 is disposed such that the first valve port 491 communicates with the third valve port 493 such that the second cylinder
  • the second intake port 4523 of the 452 communicates with the inside of the casing 2 and the discharge port 21.
  • the low-pressure refrigerant from the refrigerating cycle device 1000 having the evaporation side pressure Ps passes through the accumulator 1 and enters the first cylinder 451 through only the first intake port 4513, the first cylinder 451 operates normally; and at the same time, the second suction port 4523 communicates with the inside of the casing 2 and the discharge port 21, the pressure in the second compression chamber 4521 is high pressure refrigerant, and the pressure of the second suction port 4523 is high pressure Pd, and the back pressure of the second sliding piece 472 is the inside of the sealed casing 2
  • the high pressure Pd, the second sliding piece 472 is stopped by the sliding brake device 482 to stop in the second sliding plate groove 4522 due to insufficient pressure difference (as shown in FIG. 3), and the second sliding piece 472
  • the head is disengaged from the outer peripheral wall of the second piston 462, so that the second cylinder 452 is stopped, and at this time, the rotary compressor 700 operates in the partial load operation mode.
  • the increased refrigerant from the refrigeration cycle apparatus 1000 having a pressure of Pm may be blown to the first compression chamber 4511 through the first gas injection port 441, and the high pressure refrigerant having a pressure of Pd in the second compression chamber will be It is stopped by the check valve 443 and cannot flow to the second air injection port 442, thereby achieving single cylinder air injection operation of the rotary compressor 700.
  • the rotary compressor 700 is a variable capacity jet booster compressor, and the rotary compressor 700 can be made full by providing a first reversing assembly 49 that can be switched between two communication modes. Load working mode and Partial load mode of operation is conveniently switched between the two modes of operation. Specifically, the rotary compressor 700 can be operated in a partial load mode when the system load is small, so that the system operates efficiently, when the rotary compressor 700 When operating in the full load mode of operation, the gas transmission capacity of the rotary compressor 700 can be increased, thereby greatly improving the heating effect in the low temperature heating application, thereby making the structure of the rotary compressor 700 more reasonable and more efficient. High, wide application range, and better low temperature heating effect.
  • the rotary compressor 700 may include a housing 2 and a motor 3 and a compression mechanism provided in the housing 2, the motor 3 being coupled to a compression mechanism, and the compression mechanism may include a first cylinder 451 and a second cylinder 452 and the partition 453, the partition 453 may include a first partition 4531 and a second partition 4532.
  • the top of the first cylinder 451 is provided with a main bearing 421, and the bottom of the second cylinder 452 is provided with a sub-bearing 422.
  • a first compression chamber 4511 is formed in the first cylinder 451.
  • a first piston 461 (rolling piston) and a first sliding piece 471 are disposed in the first cylinder 451, and the first piston 461 is in the first cylinder.
  • the first compression chamber 4511 of the 451 is eccentrically rotated, the first sliding piece 471 is received in the first sliding piece groove 4512, and the head (front end) of the first sliding piece 471 is in contact with the outer peripheral wall of the first piston 461, first A tail portion (rear end) of the slider 471 is provided with a spring 481.
  • a second compression chamber 4521 is formed in the second cylinder 452.
  • the second cylinder 452 is provided with an eccentrically placed second piston 462 (rolling piston) and a second sliding piece 472.
  • the second piston 462 is The second compression chamber 4521 of the second cylinder 452 is eccentrically rotated, the second sliding piece 472 is received in the second sliding piece groove 4522, and the head of the second sliding piece 472 and the outer peripheral wall of the second piston 462 are selectively Contact or disengage, the tail of the second slider 472 is provided with a slider brake device 482.
  • the compression mechanism further includes a crankshaft 41, and the first piston 461 and the second piston 462 are sleeved on the crankshaft 41 to simultaneously drive the first piston 461 and the second piston 462 through the crankshaft 41 in corresponding compression. Rolling in the cavity.
  • a first air inlet 4513 and a first air outlet 4514 are formed on the first cylinder 451.
  • the first air cylinder 451 is further provided with a first air suction pipe 11 for the first air suction pipe 11. One end is connected to the first air inlet 4513 and the other end is connected to the accumulator 1.
  • the first exhaust port 4514 passes through the first exhaust valve 4211 on the main bearing 421, the first muffler 431 and the inside of the sealed casing 2. Connected.
  • a second air inlet 4523 and a second air outlet 4524 are formed on the second cylinder 452.
  • the second air cylinder 452 is further provided with a second air suction pipe 12, and the second air suction pipe 12 is provided.
  • One end is connected to the second suction port 4523, and the other end is connected to the accumulator 1 and the discharge port 21 (or the inside of the casing 2) through the first reversing component 49 (for example, a three-way valve), and the second exhaust port 4524
  • the second exhaust valve 4221 and the second muffler 432 on the sub-bearing 422 communicate with the inside of the sealed casing 2.
  • the partition 453 may be formed with a first air outlet 441 communicating with the first compression chamber 4511 and a second air outlet 442 communicating with the second compression chamber 4521, that is, the first air outlet 441 and the first Two air outlets 442 may be formed on the partition 453.
  • the rotary compressor 700 may further include a gas injection pipe 44, and the first air injection port 441 and the second air injection port 442 are respectively connected to the air injection pipe 44, wherein the second air injection port 442 and the air injection pipe 44 are provided.
  • a check valve 443 is disposed between the gas, and the gas can flow unidirectionally from the gas pipe 44 through the check valve 443 to the second gas injection port 442.
  • the first gas injection port 441 and the second gas injection port 442 can respectively follow the first Rolling of one piston 461 and second piston 462 It is periodically turned on and off. Thereby, the processing is facilitated, and the opening and closing control of the first air outlet 441 and the second air outlet 442 is facilitated.
  • the first cylinder 451 needs to operate when the load is small, when the load of the rotary compressor 700 is small, the time of the end of the jet is higher.
  • the first air outlet 441 should be closed earlier, and when the second cylinder 452 is operating at a higher load, the second air outlet 442 can be closed later to increase the amount of air.
  • the second gas injection port 442 should be located adjacent to the corresponding exhaust port of the first air injection port 441 in the rolling direction of the piston (since the first exhaust port 4514 and the second exhaust port 4524 are below
  • the projection on the reference plane is largely coincident, so that the exhaust port here is understood to be one side of the first exhaust port 4514 and the second exhaust port 4524, in other words, the second air outlet 442 is opposite to the first
  • the air outlet 441 is closer to the exhaust port in the direction of rotation of the compressor. Therefore, the rotary compressor 700 can switch between the two modes of operation, the full load operation mode and the partial load operation mode, so that the operation efficiency is higher, the application range is wider, and the low temperature heating effect is better. .
  • the first exhaust port 4514 coincides with the projection of the second exhaust port 4524, with the intersection of the central axis of the crankshaft 41 and the reference plane as the origin.
  • the angle A defined between the two may represent the angle between the first air outlet 441 relative to the first exhaust port 4514 (or the second exhaust port 4524); the first exhaust port 4514 (or the second row)
  • the port 4524) is an angle B defined between a line connecting the midpoint of the reference plane and the origin, and a line connecting the end point of the second air outlet 442 projected on the reference plane to the origin, and may represent the second
  • the angle between the air outlet 442 and the first exhaust port 4514 (or the second exhaust port 4524) is smaller than the angle A, so that the second air outlet 442 is located at the edge of the first air outlet 441.
  • the rolling direction of the piston is adjacent to one side of the first exhaust port 4514 (or to the second exhaust port 4524).
  • the present invention is not limited thereto, and as shown in FIG. 5, the first air outlet 441 and the second air outlet 442 may be formed on the main bearing 421 and the sub-bearing 422, respectively. That is, the first air injection port 441 is formed on the main bearing 421, and the second air injection port 442 is formed on the sub-bearing 422. At this time, the first air outlet 441 and the second air outlet 442 may be periodically opened and closed as the first piston 461 and the second piston 462 roll, respectively.
  • the second air outlet 442 is located on the side of the first air outlet 441 adjacent to the corresponding exhaust port in the rolling direction of the piston, that is, the second air outlet 442 is opposite to the first air outlet 441. It is closer to the exhaust port in the direction of rotation of the compressor. Thereby, it is convenient to process and realize the opening and closing control of the first air outlet 441 and the second air outlet 442.
  • the tail of the slider on the other cylinder i.e., the cylinder in which the slider is selectively contacted or separated from the corresponding piston
  • a slider brake device 482 when the difference between the pressure of the tail portion of the sliding piece and the pressure of the head of the sliding piece is greater than the braking force of the sliding piece braking device 482 to the sliding piece, the sliding piece is separated from the sliding piece braking device 482 and the head of the sliding piece is The outer peripheral wall of the corresponding piston is stopped.
  • the braking force is 2N to 10N.
  • the slider brake device 482 may be a magnet and is fixed in the second cylinder 452 between the rear end of the second slider 472 and the inner side wall of the housing 2, second Slide 472 through its rear end and front end The pressure difference slides within the second vane slot 4522.
  • the second slider 472 may slide toward the second compression chamber 4521 to be separated from the slider brake device 482, and The front end of the second sliding piece 472 is abutted against the outer peripheral wall of the second piston 462 (as shown in FIG.
  • a refrigeration cycle apparatus 1000 includes: a rotary compressor 700 according to the first aspect of the present invention, a second reversing assembly 100 (for example, a four-way reversing valve), and an outdoor heat exchange The device 200, the indoor heat exchanger 300, and the flasher 400.
  • the flasher 400 may have a gas-liquid separation function and should be well known to those skilled in the art and will not be described in detail herein.
  • the second reversing assembly 100 includes a first interface 101, a second interface 102, a third interface 103, and a fourth interface 104, and the first interface 101 and the discharge port 21 of the rotary compressor 700 Connected, the fourth interface 104 is connected to the accumulator 1, the first end of the outdoor heat exchanger 200 is connected to the second interface 102, the first end of the indoor heat exchanger 300 is connected to the third interface 103, and the indoor heat exchanger 300 The second end is connected to the second end of the outdoor heat exchanger 200, and the flasher 400 is connected between the second end of the indoor heat exchanger 300 and the second end of the outdoor heat exchanger 200, and the flasher 400 and The first air outlet 441 of the rotary compressor 700 is connected to the second air outlet 442.
  • the first throttle unit 500 can be connected in series between the outdoor heat exchanger 200 and the flasher 400, and the flasher 400 is exchanged indoors.
  • the second throttle member 600 may be connected in series between the heaters 300. Thereby, the circulation of the refrigerant can be realized, so that the refrigeration cycle apparatus 1000 can be cooled and heated.
  • the working principle of the refrigeration cycle device 1000 should be well known to those skilled in the art and will not be described in detail herein.
  • the arrow pointing in Fig. 7 shows the direction of refrigerant flow in the refrigeration cycle apparatus 1000 in one mode of operation.
  • the operation efficiency is higher and the application range is wider.
  • first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated.
  • features defining “first” and “second” may include one or more of the features either explicitly or implicitly.
  • the meaning of "a plurality” is two or more unless specifically and specifically defined otherwise.
  • the terms “installation”, “connected”, “connected”, “fixed” and the like shall be understood broadly, and may be either a fixed connection or a detachable connection, unless explicitly stated and defined otherwise. Or integrated; can be directly connected, or indirectly connected through an intermediate medium, which can be the internal communication of two elements or the interaction of two elements.
  • an intermediate medium which can be the internal communication of two elements or the interaction of two elements.
  • the first feature "on” or “under” the second feature may be a direct contact of the first and second features, or the first and second features may be indirectly through an intermediate medium, unless otherwise explicitly stated and defined. contact.
  • the first feature "above”, “above” and “above” the second feature may be that the first feature is directly above or above the second feature, or merely that the first feature level is higher than the second feature.
  • the first feature “below”, “below” and “below” the second feature may be that the first feature is directly below or obliquely below the second feature, or merely that the first feature level is less than the second feature.

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Abstract

一种旋转式压缩机（700）和具有其的冷冻循环装置（1000），包括储液器（1）、第一换向组件（49）以及压缩机构。压缩机构包括两个气缸（451，452）和两个喷气口（441，442）。一个气缸（451）上的滑片（471）与该气缸（451）内活塞（461）的外周壁止抵，一个喷气口（441）用于向该气缸（451）通入冷媒。另一个气缸（452）上的滑片（472）与该气缸（452）内的活塞（462）可选择地接触或分离，另一个喷气口（442）用于单向地向该气缸（452）通入冷媒。第一换向组件（49）的第一阀口（491）与另一个气缸（452）的吸气口（4523）相连，第二阀口（492）与储液器（1）相连，第三阀口（493）与排气口连通，第二阀口（492）和第三阀口（493）可选择地与第一阀口（491）连通。

Description

旋转式压缩机和具有其的冷冻循环装置 技术领域
本发明涉及压缩机设备领域，具体而言，特别涉及一种旋转式压缩机和具有其的冷冻循环装置。
背景技术
相关技术中指出，在一些应用场合，例如低温度环境时的热泵应用，由于蒸发温度的降低，将导致冷冻循环系统的能力降低、普通单级旋转式压缩机的性能变差无法使用，采用大容量喷气增焓的方案，可以有效地提升冷冻循环系统的能力，但是普通的大容量双缸喷气增焓式压缩机在压缩负荷较小的时候仍然进行双缸运行，使得运转效率变差。
发明内容
本发明旨在至少解决现有技术中存在的技术问题之一。为此，本发明在于提出一种旋转式压缩机，所述旋转式压缩机具有结构简单合理、运转效率高、适用范围广、低温制热效果优等优点。
本发明还提出一种具有上述旋转式压缩机的冷冻循环装置。
根据本发明第一方面的旋转式压缩机，包括：储液器；壳体，所述壳体设在所述储液器外，所述壳体上形成有排出口；压缩机构，所述压缩机构设在所述壳体内，所述压缩机构包括主轴承、气缸组件、副轴承、两个活塞和两个滑片，所述主轴承和所述副轴承分别设在所述气缸组件的轴向两端，所述气缸组件包括具有压缩腔的两个气缸和设在所述两个气缸之间的隔板，每个所述气缸上形成有滑片槽、吸气口和排气口，每个所述活塞设在对应的所述压缩腔内且沿所述压缩腔的内壁可滚动，每个所述滑片可移动地设在对应的所述滑片槽内，所述两个气缸中的其中一个气缸上的所述滑片的头部与对应的所述活塞的外周壁止抵，所述两个气缸中的另一个气缸上的所述滑片与对应的所述活塞可选择地接触或分离，其中，所述压缩机构上形成有用于向所述其中一个气缸的所述压缩腔内通入冷媒的第一喷气口和用于单向地向所述另一个气缸的所述压缩腔内通入所述冷媒的第二喷气口；以及第一换向组件，所述第一换向组件包括第一阀口至第三阀口，所述第一阀口与所述另一个气缸的所述吸气口相连，第二阀口与所述储液器相连，所述第三阀口与所述排气口连通，所述第二阀口和所述第三阀口中的其中一个与所述第一阀口连通。
根据本发明的旋转式压缩机，具有运转效率高、适用范围广、低温制热效果优等优点。
另外，根据本发明上述实施例的旋转式压缩机具还可以具有如下附加的技术特征：
根据本发明的一个示例，所述第一喷气口和所述第二喷气口形成在所述隔板上。
根据本发明的一个示例，所述第一喷气口和所述第二喷气口分别形成在所述主轴承和所述副轴承上。
根据本发明的一个示例，所述第二喷气口位于所述第一喷气口的沿所述活塞的滚动方向 的邻近所述排气口的一侧。
根据本发明的一个示例，所述旋转式压缩机进一步包括：单向阀，所述单向阀设在所述第二喷气口处以单向地向所述另一个气缸的所述压缩腔内通入所述冷媒。
根据本发明的一个示例，所述另一个气缸上的所述滑片的尾部设有滑片制动装置，当所述滑片的尾部的压力与所述滑片的头部的压力之差大于所述滑片制动装置对所述滑片的制动力时所述滑片与所述滑片制动装置分离且所述滑片的头部与对应的所述活塞的外周壁止抵。
根据本发明的一个示例，所述制动力为2N～10N。
根据本发明的一个示例，所述第三阀口与所述排出口或所述壳体内部直接相连。
根据本发明的一个示例，所述第一换向组件为三通阀。
根据本发明第二方面的冷冻循环装置，包括根据本发明第一方面的旋转式压缩机；第二换向组件，所述第二换向组件包括第一接口至第四接口，所述第一接口与所述旋转式压缩机的排出口相连，所述第四接口与所述储液器相连；室外换热器，所述室外换热器的第一端与第二接口相连；室内换热器，所述室内换热器的第一端与第三接口相连，所述室内换热器的第二端与所述室外换热器的第二端相连；以及闪发器，所述闪发器连接在所述室内换热器的第二端与所述室外换热器的第二端之间，其中所述闪发器与所述旋转式压缩机的所述第一喷气口和所述第二喷气口相连。
根据本发明的冷冻循环装置，通过设置上述第一方面的旋转式压缩机，从而提高了冷冻循环装置的整体性能。
本发明的附加方面和优点将在下面的描述中部分给出，部分将从下面的描述中变得明显，或通过本发明的实践了解到。
附图说明
图1是根据本发明实施例的旋转式压缩机的一个角度的剖面图；
图2是图1中所示的旋转式压缩机的另一个角度的剖面图，图中，第一换向组件的第一阀口与第二阀口连通；
图3是图1中所示的旋转式压缩机的另一个角度的剖面图，图中，第一换向组件的第一阀口与第三阀口连通；
图4是沿图2中D-D线的剖面图；
图5是根据本发明另一个实施例的旋转式压缩机的剖面图；
图6是根据本发明再一个实施例的旋转式压缩机的剖面图；
图7是根据本发明实施例的冷冻循环装置的系统结构示意图。
附图标记：
1000：冷冻循环装置
100：第二换向组件；101：第一接口；102：第二接口；
                   103：第三接口；104：第四接口；
200：室外换热器；300：室内换热器；400：闪发器；
500：第一节流部件；600：第二节流部件；
700：旋转式压缩机；
 1：储液器；11：第一吸气管；12：第二吸气管；
 2：壳体；21：排出口；22：排气管；3：电机；
   41：曲轴；
   421：主轴承；4211：第一排气阀；
   422：副轴承；4221：第二排气阀；
   431：第一消音器；432：第二消音器；
   44：喷气管；441：第一喷气口；442：第二喷气口；443：单向阀；
       451：第一气缸；4511：第一压缩腔；4512：第一滑片槽；
                      4513：第一吸气口；4514：第一排气口；
       452：第二气缸；4521：第二压缩腔；4522：第二滑片槽；
                      4523：第二吸气口；4524：第二排气口；
       453：隔板；4531：第一隔板；4532：第二隔板；
    461：第一活塞；462：第二活塞；
    471：第一滑片；472：第二滑片；
    481：弹簧；482：滑片制动装置；
    49：第一换向组件；491：第一阀口；492：第二阀口；493：第三阀口。
具体实施方式
下面详细描述本发明的实施例，所述实施例的示例在附图中示出，其中自始至终相同或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附图描述的实施例是示例性的，旨在用于解释本发明，而不能理解为对本发明的限制。
下文的公开提供了许多不同的实施例或例子用来实现本发明的不同结构。为了简化本发明的公开，下文中对特定例子的部件和设置进行描述。当然，它们仅仅为示例，并且目的不在于限制本发明。此外，本发明可以在不同例子中重复参考数字和/或字母。这种重复是为了简化和清楚的目的，其本身不指示所讨论各种实施例和/或设置之间的关系。此外，本发明提供了的各种特定的工艺和材料的例子，但是本领域普通技术人员可以意识到其他工艺的可应用于性和/或其他材料的使用。
下面参考图1-图6描述根据本发明第一方面实施例的旋转式压缩机700。
如图1所示，根据本发明第一方面实施例的旋转式压缩机700，包括：储液器1、壳体2、压缩机构以及第一换向组件49。
具体地，壳体2设在储液器1外，壳体2上形成有排出口21。参照图1，旋转式压缩机700可以为立式压缩机，此时，壳体2可以大体形成为中空且密闭的大体圆柱筒形，且壳体2的中心轴线可以沿竖直方向延伸，排出口21可以沿上下方向贯穿壳体2的顶壁，且排出 口21处可以插设竖直延伸的排气管22，以用于将壳体2内部的气态冷媒(或混合部分液态冷媒及润滑油)排出，储液器1设在壳体2的外部。当然，本发明不限于此，根据本发明的旋转式压缩机700还可以是卧式压缩机，此时，壳体2的中心轴线可以沿水平方向延伸。下面仅以旋转式压缩机700为立式压缩机为例进行说明。
具体地，压缩机构设在壳体2内，压缩机构包括主轴承421、气缸组件、副轴承422，主轴承421和副轴承422分别设在气缸组件的轴向两端，例如在图1的示例中，主轴承421可以设在气缸组件的顶部，副轴承422可以设在气缸组件的底部。
进一步地，气缸组件包括具有压缩腔的两个气缸和设在两个气缸之间的隔板453，也就是说，气缸组件包括两个气缸，隔板453设在两个气缸之间，每个气缸均具有压缩腔。例如在图1和图2的示例中，气缸组件包括设在隔板453上方的第一气缸451和设在隔板453下方的第二气缸452，主轴承421、第一气缸451以及隔板453之间限定出第一压缩腔4511，隔板453、第二气缸452以及副轴承422之间限定出第二压缩腔4521。
进一步地，压缩机构还包括两个活塞和两个滑片，每个气缸上形成有滑片槽、吸气口和排气口，每个活塞设在对应的压缩腔内且沿压缩腔的内壁可滚动，每个滑片可移动地设在对应的滑片槽内。其中，每个排气口均直接或间接与壳体2内部连通，进而与排出口21连通。
例如在图1和图2的示例中，两个滑片分别为第一滑片471和第二滑片472，两个活塞分别为第一活塞461和第二活塞462，第一气缸451上形成有第一滑片槽4512、第一吸气口4513和第一排气口4514，第一活塞461设在第一压缩腔4511内且沿第一压缩腔4511的内壁可滚动，第一滑片槽4512可以沿第一气缸451的径向延伸，第一滑片471沿第一滑片槽4512的长度方向可移动地设在第一滑片槽4512内，第二气缸452上形成有第二滑片槽4522、第二吸气口4523和第二排气口4524，第二活塞462设在第二压缩腔4521内且沿第二压缩腔4521的内壁可滚动，第二滑片槽4522可以沿第二气缸452的径向延伸，第二滑片472沿第二滑片槽4522的长度方向可移动地设在第二滑片槽4522内。
两个气缸中的其中一个气缸上的滑片的头部与对应的活塞的外周壁止抵，两个气缸中的另一个气缸上的滑片与对应的活塞可选择地接触或分离。也就是说，包括以下两种可能，第一种可能为：当第一气缸451上的第一滑片471的头部与第一活塞461的外周壁止抵时，第二气缸452上的第二滑片472与第二活塞462可选择地接触或分离；第二种可能为：当第二气缸452上的第二滑片472的头部与第二活塞462的外周壁止抵时，第一气缸451上的第一滑片471与第一活塞461可选择地接触或分离。下面仅以第一种可能为例进行说明，当然，本领域技术人员在阅读了下面的技术方案后，显然可以理解第二种可能的技术方案。这里，需要说明的是，滑片的头部可以理解为，滑片的邻近相应压缩腔中心轴线的一端，其相反的一端为滑片的尾部，即滑片的远离相应压缩腔中心轴线的一端。
可选地，参照图2，第一滑片471的尾部与壳体2的内侧壁之间可以设有弹簧481，弹簧481始终推动第一滑片471的头部与第一活塞461的外周壁止抵，第二滑片472的尾部与壳体2的内侧壁之间可以设有滑片制动装置482，滑片制动装置482可以在某些工况下控 制第二滑片472的头部与第二活塞462的外周壁止抵，在另外一些工况下控制第二滑片472的头部与第二活塞462的外周壁分离。这里，需要说明的是，控制第一滑片471和第二滑片472的装置不限于弹簧481和滑片制动装置482。另外，需要说明的是，滑片制动装置482将在下文中详述，这里不作赘述。
压缩机构上形成有用于向所述其中一个气缸(即其内设有滑片的头部与活塞的外周壁止抵的气缸)的压缩腔内通入冷媒的第一喷气口441和用于单向地向所述另一个气缸(即其内设有滑片与对应的活塞可选择地接触或分离的气缸)的压缩腔内通入冷媒的第二喷气口442。例如在图2的示例中，压缩机构上形成有用于向第一气缸451的第一压缩腔4511内通入冷媒的第一喷气口441，压缩机构上进一步形成有用于单向地向第二气缸452的第二压缩腔4521内通入冷媒的第二喷气口442，这里，单向通入可以理解为，第二压缩腔4521内的冷媒不会向第二喷气口442回流。另外，需要说明的是，第一喷气口441和第二喷气口442的具体构造位置将在下文中详述，这里不作赘述。
可选地，可以通过设置单向阀443实现逆止功能。也就是说，旋转式压缩机700进一步可以包括单向阀443，单向阀443设在第二喷气口442处以单向地向所述另一个气缸(即其内设有滑片与对应的活塞可选择地接触或分离的气缸)的压缩腔内通入冷媒，例如在图2的示例中，单向阀443设在第二喷气口442处以单向地向第二气缸452的第二压缩腔4521内通入冷媒，以防至第二压缩腔4521内的冷媒向第二喷气口442回流。当然，本发明不限于此，还可以通过设置其他装置实现逆止功能。
进一步地，参照图2和图3，第一换向组件49包括第一阀口491、第二阀口492和第三阀口493，第一阀口491与所述另一个气缸(即其内设有滑片与对应的活塞可选择地接触或分离的气缸)的吸气口相连，第二阀口492与储液器1相连，第三阀口493与排气口(第一排气口4514和第二排气口4524均可)连通，第二阀口492和第三阀口493中的其中一个与第一阀口491可选择地连通，也就是说，某些工况下，第二阀口492与第一阀口491连通(如图2所示)，另外一些工况下，第三阀口493与第一阀口491连通(如图3所示)。可选地，第一换向组件49为三通阀。当然，本发明不限于此，第一换向组件49还可以构造为可实现三通切换效果的其他结构形式。
这里，需要说明的是，第三阀口493与排气口连通，由于排气口与壳体2内部以及排出口21连通，从而第三阀口493可以与壳体2内部以及排出口21连通，也就是说，第三阀口493可以将排气压力从排气管22或密闭壳体2引出。如图1-图3所示，第三阀口493与排出口21相连，从而实现与排气口的连通。或者可选地，如图6所示，第三阀口493与壳体2内部直接相连，从而实现与排气口的连通。由此，方便加工和实现。
例如在图1-图3的示例中，第一气缸451上的第一吸气口4513与储液器1相连且连通，第二气缸452上的第二吸气口4523与第一换向组件49的第一阀口491相连且连通，第一气缸451上的第一排气口4514与壳体2内部直接连通或者通过下文所述的第一消音器431间接连通，第二气缸452上的第二排气口4524与壳体2内部直接连通或者通过下文所述的第二消音器432间接连通，从而第一排气口4514和第二排气口4524可以通过壳体2内部 连通至排出口21。
参照图2，第一换向组件49的第二阀口492与储液器1相连且连通，当第二阀口492与第一阀口491连通时，储液器1可以通过第二吸气口4523向第二压缩腔4521输送冷媒。参照图3，第一换向组件49的第三阀口493与第一排气口4514或第二排气口4524连通，换言之，第一换向组件49的第三阀口493与壳体2内部以及排出口21连通，从而当第三阀口493与第一阀口491联通时，第二吸气口4523与壳体2内部以及排出口21连通。
这样，旋转式压缩机700工作的过程中，通过第一换向组件49在两种连通模式间的切换可实现两种工作模式，即：全负荷工作模式和部分负荷工作模式。
具体地，如图1和图2所示，当旋转式压缩机700采用全负荷工作模式时，第一换向组件49设置为第一阀口491与第二阀口492连通，使得第二气缸452的第二吸气口4523与储液器1连通。此时，来自冷冻循环装置1000(将在下文中详述)蒸发侧压力为Ps的低压冷媒经过储液器1后，通过第一吸气口4513进入第一气缸451，同时通过第一换向组件49、第二吸气口4523进入第二气缸452，此时第一气缸451、第二气缸452均正常工作，低压冷媒分别被第一气缸451、第二气缸452压缩并提高压力至Pd后，分别经过第一排气口4514、第二排气口4524进入密闭的壳体2内部并从排出口21处的排气管22排出，此时旋转式压缩机700为双缸运转，此时，旋转式压缩机700在全负荷工作模式下工作。
在全负荷工作模式下，因为第二吸气口4523的压力为低压力Ps，第二滑片472的尾部背压为密闭壳体2内部的高压力Pd，第二滑片472在压差作用下脱离滑片制动装置482(如图2所示)，且第二滑片472的头部与第二活塞462的外周壁相接触运行，第二气缸452可正常工作运行，此时来自冷冻循环装置1000的压力为Pm的增焓冷媒可通过第一喷气口441向第一压缩腔4511喷气，同时增焓冷媒可通过第二喷气口442单向地向第二压缩腔4521喷气，从而实现旋转式压缩机700的双缸喷气运行。
具体地，如图1和图3所示，当旋转式压缩机700采用部分负荷工作模式时，第一换向组件49设置为第一阀口491与第三阀口493连通，使得第二气缸452的第二吸气口4523与壳体2内部以及排出口21连通。此时，来自冷冻循环装置1000蒸发侧压力为Ps的低压冷媒经过储液器1后仅通过第一吸气口4513进入第一气缸451，第一气缸451正常工作；同时由于第二吸气口4523与壳体2内部以及排出口21连通，第二压缩腔4521内为高压冷媒、第二吸气口4523的压力为高压力Pd，同时第二滑片472尾部背压为密闭壳体2内部的高压力Pd，第二滑片472因没有足够的压差作用被滑片制动装置482作用停止在第二滑片槽4522内静止(如图3所示)，且第二滑片472的头部与第二活塞462的外周壁脱离，从而第二气缸452停止工作，此时，旋转式压缩机700在部分负荷工作模式下工作。
在部分负荷工作模式下，此时来自冷冻循环装置1000的压力为Pm的增焓冷媒可通过第一喷气口441向第一压缩腔4511喷气，同时第二压缩室内的压力为Pd的高压冷媒将被单向阀443逆止而不能流向第二喷气口442，从而实现旋转式压缩机700的单缸喷气运行。
根据本发明实施例的旋转式压缩机700，为可变容量喷气增焓式压缩机，通过设置可在两种连通模式间切换的第一换向组件49，可以使得旋转式压缩机700在全负荷工作模式和 部分负荷工作模式这两种工作模式间方便地切换，具体而言，旋转式压缩机700在系统负荷较小时，可以采用部分负荷工作模式运行，从而使得系统运转效率高，当旋转式压缩机700在全负荷工作模式运行时，旋转式压缩机700的输气能力可以提高，从而极大地提升了低温制热应用时的制热效果，从而使得旋转式压缩机700的结构更加合理、运转效率更高、适用范围更广、低温制热效果更优。
下面，参照图1-图6简要描述根据本发明一些具体实施例的旋转式压缩机700。
参照图1和图2，旋转式压缩机700可以包括壳体2以及设在壳体2内的电机3和压缩机构，电机3与压缩机构相连，压缩机构可以包括第一气缸451、第二气缸452以及隔板453，隔板453可以包括第一隔板4531和第二隔板4532，第一气缸451的顶部设有主轴承421、第二气缸452的底部设置有副轴承422。
参照图1和图2，第一气缸451内形成有第一压缩腔4511，第一气缸451内设置有第一活塞461(滚动活塞)及第一滑片471，第一活塞461在第一气缸451的第一压缩腔4511内做偏心转动，第一滑片471收纳在第一滑片槽4512内，第一滑片471的头部(前端)与第一活塞461的外周壁接触，第一滑片471的尾部(后端)设置有弹簧481。
参照图1和图2，第二气缸452内形成有第二压缩腔4521，第二气缸452内设置有偏心放置的第二活塞462(滚动活塞)及第二滑片472，第二活塞462在第二气缸452的第二压缩腔4521内做偏心转动，第二滑片472收纳在第二滑片槽4522内，第二滑片472的头部与第二活塞462的外周壁可选择性的接触或分离，第二滑片472的尾部设置滑片制动装置482。
参照图1和图2，压缩机构还包括曲轴41，第一活塞461和第二活塞462均套设在曲轴41上，以通过曲轴41同时驱动第一活塞461及第二活塞462在对应的压缩腔内滚动。
参照图1和图2，第一气缸451上形成有第一吸气口4513和第一排气口4514，第一气缸451上还设置有第一吸气管11，第一吸气管11的一端连接第一吸气口4513上、另一端连接至储液器1，第一排气口4514通过主轴承421上的第一排气阀4211、第一消音器431与密闭的壳体2内部连通。
参照图1和图2，第二气缸452上形成有第二吸气口4523和第二排气口4524，第二气缸452上还设置有第二吸气管12，第二吸气管12的一端连接第二吸气口4523上、另一端通过第一换向组件49(例如三通阀)分别与储液器1及排出口21(或壳体2内部)连通，第二排气口4524通过副轴承422上的第二排气阀4221、第二消音器432腔与密闭的壳体2内部连通。
进一步地，隔板453上可以形成有与第一压缩腔4511连通的第一喷气口441、以及与第二压缩腔4521连通的第二喷气口442，也就是说，第一喷气口441和第二喷气口442可以形成在隔板453上。此时，如图2所示，旋转式压缩机700还可以包括喷气管44，第一喷气口441、第二喷气口442分别与喷气管44连接，其中，第二喷气口442与喷气管44之间设置有单向阀443，气体可单向地从喷气管44经过单向阀443向第二喷气口442流动，此时，第一喷气口441和第二喷气口442可以分别随着第一活塞461和第二活塞462的滚 动而被周期性地打开及关闭。由此，方便加工，且方便第一喷气口441和第二喷气口442的开闭控制。
由于旋转式压缩机700在两种工作模式下、第一气缸451一直处于工作状态，即第一气缸451需要在负荷较小时工作，当旋转式压缩机700的负荷较小时，喷气结束的时间较早，第一喷气口441应当较早关闭，而当第二气缸452在负荷较高时工作，第二喷气口442可以关闭较晚，以提高喷气量。由此，如图4所示，第二喷气口442应当位于第一喷气口441的沿活塞的滚动方向的邻近相应排气口(由于第一排气口4514与第二排气口4524在下文所述的基准平面上的投影大体重合，从而这里的排气口理解为第一排气口4514和第二排气口4524均可)的一侧，换言之，第二喷气口442相对于第一喷气口441沿压缩机旋转方向更靠近即排气口。由此，旋转式压缩机700在全负荷工作模式和部分负荷工作模式这两种工作模式间可以更好、更有效地切换，使得运转效率更高、适用范围更广、低温制热效果更优。
例如在图4的示例中，在垂直于曲轴41中心轴线的基准平面上，第一排气口4514与与第二排气口4524的投影重合，以曲轴41中心轴线与基准平面的交点为原点，第一排气口4514(或与第二排气口4524)投影在基准平面上的中点与原点的连线、和第一喷气口441投影在基准平面上的端点与原点的连线之间所限定出的夹角A，可以表示第一喷气口441相对于第一排气口4514(或与第二排气口4524)的夹角；第一排气口4514(或与第二排气口4524)投影在基准平面上的中点与原点的连线、和第二喷气口442投影在基准平面上的端点与原点的连线之间所限定出的夹角B，可以表示第二喷气口442相对于第一排气口4514(或与第二排气口4524)的夹角，夹角B小于夹角A，从而可以理解为第二喷气口442位于第一喷气口441的沿活塞的滚动方向的邻近第一排气口4514(或与第二排气口4524)的一侧。
当然，本发明不限于此，如图5所示，第一喷气口441和第二喷气口442还可以分别形成在主轴承421和副轴承422上。也就是说，第一喷气口441形成在主轴承421上，第二喷气口442形成在副轴承422上。此时，第一喷气口441和第二喷气口442同样可以分别随着第一活塞461和第二活塞462的滚动而被周期性地打开及关闭。同样，如图4所示，第二喷气口442位于第一喷气口441的沿活塞的滚动方向的邻近相应排气口的一侧，也就是说，第二喷气口442相对第一喷气口441沿压缩机旋转方向更靠近排气口。由此，方便加工和实现第一喷气口441和第二喷气口442的开闭控制。
在本发明的一个可选实施例中，所述另一个气缸(即其内设有滑片与对应的活塞可选择地接触或分离的气缸)上的滑片的尾部设有滑片制动装置482，当滑片的尾部的压力与滑片的头部的压力之差大于滑片制动装置482对滑片的制动力时滑片与滑片制动装置482分离且滑片的头部与对应的活塞的外周壁止抵。可选地，制动力为2N～10N。由此，可以确保旋转式压缩机700在全负荷工作模式和部分负荷工作模式这两种工作模式间可靠地切换。
例如在图2和图3的示例中，滑片制动装置482可以为磁铁，且固定在第二气缸452内位于第二滑片472的后端与壳体2的内侧壁之间，第二滑片472通过其后端与前端之间 的压力差在第二滑片槽4522内滑动。当第二滑片472后端的压力与第二滑片472前端的压力之差大于制动力时，第二滑片472可以朝向第二压缩腔4521内滑动以与滑片制动装置482分离，并且第二滑片472的前端与第二活塞462的外周壁止抵(如图2所示)，当第二滑片472后端的压力与第二滑片472前端的压力之差小于等于制动力时，第二滑片472贴紧滑片制动装置482以与滑片制动装置482相对静止，从而与第二活塞462的外周壁分离(如图3所示)。
根据本发明第二方面实施例的冷冻循环装置1000，包括：根据本发明上述第一方面实施例的旋转式压缩机700、第二换向组件100(例如四通换向阀)、室外换热器200、室内换热器300以及闪发器400。这里，需要说明的是，闪发器400可以具有气液分离功能、应为本领域技术人员所熟知，这里不再详述。
具体地，如图7所示，第二换向组件100包括第一接口101、第二接口102、第三接口103和第四接口104，第一接口101与旋转式压缩机700的排出口21相连，第四接口104与储液器1相连，室外换热器200的第一端与第二接口102相连，室内换热器300的第一端与第三接口103相连，室内换热器300的第二端与室外换热器200的第二端相连，闪发器400连接在室内换热器300的第二端与室外换热器200的第二端之间，且闪发器400与旋转式压缩机700的第一喷气口441和第二喷气口442相连，另外，室外换热器200与闪发器400之间可以串接第一节流部件500，闪发器400与室内换热器300之间可以串接第二节流部件600。由此，可以实现冷媒的循环流通，使得冷冻循环装置1000可以制冷、制热工作。其中，冷冻循环装置1000的工作原理应为本领域技术人员所熟知，这里不再详述。另外，图7中的箭头指向展示了冷冻循环装置1000在一种工作模式下的冷媒流动方向。
根据本发明实施例的冷冻循环装置1000，通过设置上述第一方面实施例的旋转式压缩机700，运转效率更高、适用范围更广。
在本发明的描述中，需要理解的是，术语“中心”、“上”、“下”、“前”、“后”、“竖直”、“水平”、“顶”、“底”、“内”、“外”、“轴向”、“径向”、“周向”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括一个或者更多个该特征。在本发明的描述中，“多个”的含义是两个或两个以上，除非另有明确具体的限定。
在本发明中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固定”等术语应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本发明中的具体含义。
在本发明中，除非另有明确的规定和限定，第一特征在第二特征“上”或“下”可以是第一和第二特征直接接触，或第一和第二特征通过中间媒介间接接触。而且，第一特征在第二特征“之上”、“上方”和“上面”可是第一特征在第二特征正上方或斜上方，或仅仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”可以是第一特征在第二特征正下方或斜下方，或仅仅表示第一特征水平高度小于第二特征。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本发明的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不必须针对的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任一个或多个实施例或示例中以合适的方式结合。此外，在不相互矛盾的情况下，本领域的技术人员可以将本说明书中描述的不同实施例或示例以及不同实施例或示例的特征进行结合和组合。
尽管已经示出和描述了本发明的实施例，本领域的普通技术人员可以理解：在不脱离本发明的原理和宗旨的情况下可以对这些实施例进行多种变化、修改、替换和变型，本发明的范围由权利要求及其等同物限定。

Claims (10)

  1. 一种旋转式压缩机，其特征在于，包括：
    储液器；
    壳体，所述壳体设在所述储液器外，所述壳体上形成有排出口；
    压缩机构，所述压缩机构设在所述壳体内，所述压缩机构包括主轴承、气缸组件、副轴承、两个活塞和两个滑片，所述主轴承和所述副轴承分别设在所述气缸组件的轴向两端，所述气缸组件包括具有压缩腔的两个气缸和设在所述两个气缸之间的隔板，每个所述气缸上形成有滑片槽、吸气口和排气口，每个所述活塞设在对应的所述压缩腔内且沿所述压缩腔的内壁可滚动，每个所述滑片可移动地设在对应的所述滑片槽内，所述两个气缸中的其中一个气缸上的所述滑片的头部与对应的所述活塞的外周壁止抵，所述两个气缸中的另一个气缸上的所述滑片与对应的所述活塞可选择地接触或分离，
    其中，所述压缩机构上形成有用于向所述其中一个气缸的所述压缩腔内通入冷媒的第一喷气口和用于单向地向所述另一个气缸的所述压缩腔内通入所述冷媒的第二喷气口；以及
    第一换向组件，所述第一换向组件包括第一阀口至第三阀口，所述第一阀口与所述另一个气缸的所述吸气口相连，第二阀口与所述储液器相连，所述第三阀口与所述排气口连通，所述第二阀口和所述第三阀口中的其中一个与所述第一阀口连通。
  2. 根据权利要求1所述的旋转式压缩机，其特征在于，所述第一喷气口和所述第二喷气口形成在所述隔板上。
  3. 根据权利要求1所述的旋转式压缩机，其特征在于，所述第一喷气口和所述第二喷气口分别形成在所述主轴承和所述副轴承上。
  4. 根据权利要求1-3中任一项所述的旋转式压缩机，其特征在于，所述第二喷气口位于所述第一喷气口的沿所述活塞的滚动方向的邻近所述排气口的一侧。
  5. 根据权利要求1-4中任一项所述的旋转式压缩机，其特征在于，进一步包括：
    单向阀，所述单向阀设在所述第二喷气口处以单向地向所述另一个气缸的所述压缩腔内通入所述冷媒。
  6. 根据权利要求1-5中任一项所述的旋转式压缩机，其特征在于，所述另一个气缸上的所述滑片的尾部设有滑片制动装置，当所述滑片的尾部的压力与所述滑片的头部的压力之差大于所述滑片制动装置对所述滑片的制动力时所述滑片与所述滑片制动装置分离且所述滑片的头部与对应的所述活塞的外周壁止抵。
  7. 根据权利要求6所述的旋转式压缩机，其特征在于，所述制动力为2N～10N。
  8. 根据权利要求1-7中任一项所述的旋转式压缩机，其特征在于，所述第三阀口与所述排出口或所述壳体内部直接相连。
  9. 根据权利要求1-8中任一项所述的旋转式压缩机，其特征在于，所述第一换向组件为三通阀。
  10. 一种冷冻循环装置，其特征在于，包括：
    根据权利要求1-9中任一项所述的旋转式压缩机；
    第二换向组件，所述第二换向组件包括第一接口至第四接口，所述第一接口与所述旋转式压缩机的排出口相连，所述第四接口与所述储液器相连；
    室外换热器，所述室外换热器的第一端与第二接口相连；
    室内换热器，所述室内换热器的第一端与第三接口相连，所述室内换热器的第二端与所述室外换热器的第二端相连；以及
    闪发器，所述闪发器连接在所述室内换热器的第二端与所述室外换热器的第二端之间，其中所述闪发器与所述旋转式压缩机的所述第一喷气口和所述第二喷气口相连。
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