WO2017024865A1 - 压缩机和换热系统 - Google Patents

压缩机和换热系统 Download PDF

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Publication number
WO2017024865A1
WO2017024865A1 PCT/CN2016/084328 CN2016084328W WO2017024865A1 WO 2017024865 A1 WO2017024865 A1 WO 2017024865A1 CN 2016084328 W CN2016084328 W CN 2016084328W WO 2017024865 A1 WO2017024865 A1 WO 2017024865A1
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WIPO (PCT)
Prior art keywords
cylinder
compressor
partition
cavity
exhaust port
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/CN2016/084328
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English (en)
French (fr)
Inventor
胡余生
魏会军
吴健
杨欧翔
陈圣
罗惠芳
廖李平
邹鹏
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.)
Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Original Assignee
Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
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 Gree Green Refrigeration Technology Center Co Ltd of Zhuhai filed Critical Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Priority to EP16834490.1A priority Critical patent/EP3336359B1/en
Priority to KR1020187001399A priority patent/KR101986965B1/ko
Priority to US15/751,631 priority patent/US20180231000A1/en
Priority to JP2018506927A priority patent/JP6595700B2/ja
Publication of WO2017024865A1 publication Critical patent/WO2017024865A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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
    • 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
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0071—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • 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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a

Definitions

  • the invention relates to the field of heat exchange technology, in particular to a compressor and a heat exchange system.
  • electric auxiliary heat is generally used to increase the heat generation of the compressor, or a compressor having a two-stage boosting function is used to solve the problem of poor low-temperature heating capability of the compressor, but there are different degrees of problems.
  • the method of using electric auxiliary heat to increase the heat generation of the compressor has the problem of low energy efficiency
  • the compressor with double-stage boosting function can not adjust the displacement of the compressor, and the adaptability of the compressor to the operating conditions is poor.
  • the heating capacity and energy efficiency of the compressor under low temperature conditions are guaranteed. Under the premise, the compressor will have a problem of reduced energy efficiency when operating under normal working conditions.
  • the main object of the present invention is to provide a compressor and a heat exchange system to solve the problem that the compressor of the prior art has poor heating capacity and low energy efficiency due to inability to change capacity.
  • a compressor including a crankshaft and first, second, and third cylinders sequentially arranged along an axial direction of the crankshaft, the first cylinder being a high pressure cylinder,
  • the second cylinder and the third cylinder are low-pressure cylinders
  • the compressor further includes a variable-capacity switching mechanism, and the variable-capacity switching mechanism controls the third cylinder to be unloaded or loaded.
  • the compressor has a full operation mode and a partial operation mode when the compressor is in full operation. In the mode, the variable capacity switching mechanism loads the third cylinder under the action of the exhaust pressure of the compressor; when the compressor is in the partial operation mode, the variable capacity switching mechanism causes the third cylinder under the action of the intake pressure of the compressor Uninstall.
  • variable capacity switching mechanism includes: a pressure control unit that selectively conducts with an exhaust port of the compressor or an intake port of the compressor; a lock member, the pressure control unit controls the lock member and the third The cooperation relationship of the sliding plates of the cylinder, when the pressure control portion is electrically connected to the intake port of the compressor, the locking member and the sliding plate of the third cylinder are locked to unload the third cylinder, when the pressure control portion and the compressor are arranged When the air port is turned on, the lock member is unlocked with the slider of the third cylinder to load the third cylinder.
  • variable capacity switching mechanism further includes an elastic returning element, the first end of the locking member is unlocked or locked with the sliding piece, and the elastic returning element is disposed on the second end of the locking member opposite to the first end, and the pressure
  • the control unit controls the pressure of the first end of the lock member.
  • variable capacity switching mechanism further includes a voltage stabilizing branch, the first end of the voltage stabilizing branch is in communication with the air inlet of the compressor, and the second end of the voltage stabilizing branch provides pressure to the second end of the locking member.
  • the pressure control portion includes: a first branch, the first end of the first branch is in communication with the intake port of the compressor, and the second end of the first branch controls the pressure of the first end of the lock member;
  • the first on-off valve that controls the opening and closing of the first branch, the first on-off valve is disposed on the first branch;
  • the second branch, the first end of the second branch is connected to the exhaust port of the compressor, and the second branch
  • the second end of the road controls the pressure of the first end of the locking member;
  • the second switching valve for controlling the opening and closing of the second branch, and the second switching valve is disposed on the second branch.
  • the compressor further includes a mixer, the first intake port of the mixer is in communication with the exhaust port of the second cylinder, the mixer exhaust port of the mixer is in communication with the intake port of the first cylinder, and the mixer is The second air inlet is an air inlet.
  • the compressor further includes a first partition disposed between the second cylinder and the third cylinder.
  • the first baffle has a first baffle cavity communicating with the exhaust port of the second cylinder
  • the second cylinder further has an external communication port communicating with the first baffle cavity, the first intake of the mixer The port communicates with the first partition cavity through the external communication port.
  • the third cylinder has a first intermediate flow passage isolated from the compression chamber of the third cylinder
  • the compressor further includes: a second partition disposed between the first partition and the third cylinder,
  • the second baffle further has a second baffle communication hole for communicating the first intermediate flow path of the third cylinder with the first baffle cavity;
  • the first flange, the first flange is disposed away from the second cylinder of the third cylinder
  • the first flange has a first flange cavity, and the first flange cavity is in communication with the exhaust port of the third cylinder and the first intermediate flow passage, when the compressor is in the full operation mode, the second The intake port of the cylinder, the exhaust port of the second cylinder, the first diaphragm cavity, the external communication port of the second cylinder, the mixer, the intake port of the first cylinder, and the exhaust port of the first cylinder are sequentially connected And the air inlet of the third cylinder communicates with the first diaphragm cavity through the exhaust port of the third cylinder, the first
  • the compressor further includes an augmenting member that communicates with the intake port of the first cylinder.
  • the compressor further includes: a first partition, the first partition is disposed between the second cylinder and the first cylinder; and the third partition, the third partition is disposed between the first cylinder and the first partition .
  • the third baffle has a third baffle communication hole
  • the first baffle has a first baffle cavity communicating with the exhaust port of the second cylinder
  • the first baffle cavity is connected through the third baffle
  • the hole is in communication with the intake port of the first cylinder, and when the compressor is in the partial operation mode, the intake port of the second cylinder, the exhaust port of the second cylinder, the first diaphragm cavity, the third diaphragm communication hole, The intake port of the first cylinder and the exhaust port of the first cylinder are sequentially connected.
  • the third cylinder has a first intermediate flow passage isolated from the compression chamber of the third cylinder
  • the second cylinder further has a second intermediate flow passage isolated from the compression chamber of the second cylinder, the second intermediate flow passage and the first
  • the diaphragm cavity is connected
  • the compressor further includes: a second partition, the second partition is disposed between the second cylinder and the third cylinder, and the second partition further has a first intermediate flow passage of the third cylinder a second partition communicating hole communicating with the second intermediate flow passage of the two cylinders;
  • the first flange, the first flange is disposed on a side of the third cylinder away from the second cylinder, and the first flange has a first flange a cavity, the first flange cavity is in communication with the exhaust port of the third cylinder and the first intermediate flow passage, and when the compressor is in the full operation mode, the intake port of the second cylinder, the exhaust port of the second cylinder,
  • a heat exchange system including a compressor, the compressor being a compressor described below.
  • variable capacity switching mechanism in the compressor, at least one cylinder is put into use or unloaded under the action of the variable capacity switching mechanism, so that the compressor has the function of variable capacity switching and can satisfy different functions.
  • the operating requirements of the working conditions can improve the heating capacity of the compressor under different working conditions and effectively improve the overall energy efficiency of the compressor.
  • Figure 1 is a schematic view showing the operation of the heat exchange system of the compressor in the full operation mode of the present invention
  • Figure 2 is a schematic view showing the operation of the heat exchange system of the compressor in the partial operation mode of the present invention
  • FIG. 3 is a schematic view showing the working state of the variable displacement switching mechanism and the third cylinder when the third cylinder is locked in the present invention
  • FIG. 4 is a schematic view showing an operation state of the varactor switching mechanism and the third cylinder in the unlocking process of the present invention
  • Figure 5 is a schematic view showing the appearance of a compressor in a first embodiment of the present invention.
  • Figure 6 is a schematic view showing the internal structure of the compressor of Figure 5;
  • Figure 7 is a schematic view showing the flow of refrigerant in the partial operation mode of the compressor of Figure 6;
  • Figure 8 is a schematic view showing the flow of refrigerant in the full operation mode of the compressor of Figure 6;
  • Figure 9 is a schematic view showing the structure of the first partition of the compressor of Figure 6;
  • Figure 10 is a schematic view showing the structure of the second cylinder of the compressor of Figure 6;
  • Figure 11 is a view showing the structure of the third cylinder of the compressor of Figure 6;
  • Figure 12 is a schematic view showing the structure of the first flange of the compressor of Figure 6;
  • Figure 13 is a view showing the structure of the first flange cover of the compressor of Figure 6;
  • Figure 14 is a schematic view showing the relationship between the first flange, the third cylinder and the first flange cover of the compressor of Figure 6;
  • Figure 15 is a view showing the appearance of a compressor in a second embodiment of the present invention.
  • Figure 16 is a view showing the internal structure of the compressor of Figure 15;
  • Figure 17 is a flow chart showing the flow of refrigerant in the partial operation mode of the compressor of Figure 16;
  • Figure 18 is a flow chart showing the flow of refrigerant in the full operation mode of the compressor of Figure 16;
  • Figure 19 is a view showing the structure of the first cylinder of the compressor of Figure 16;
  • Figure 20 is a view showing the structure of the first partition of the compressor of Figure 16;
  • Fig. 21 is a view showing the structure of the second cylinder of the compressor of Fig. 16.
  • the term “inner or outer” as used herein refers to the inside and outside of the outline of each component, and the above-mentioned orientation words are not intended to limit the present invention.
  • the present invention provides a compressor and a heat exchange system, wherein the heat exchange system includes a compressor
  • the compressor is the compressor described below.
  • the heat exchange system further includes a four-way valve 200, a first heat exchanger 300, a first throttle valve 400, a flasher 500, a second throttle valve 600, and a second heat exchanger 700.
  • the second throttle valve 600 and the second heat exchanger 700 are in communication with the four-way valve 200, and the four-way valve 200 is also in communication with the intake port of the compressor through the liquid separator 800.
  • the flasher 500 is in communication with the cylinder of the compressor via the augmenting component 100 or mixer 60.
  • the compressor includes a crankshaft 10 and a first cylinder 20, a second cylinder 30, and a third cylinder 40 which are sequentially arranged along the axial direction of the crankshaft 10.
  • the first cylinder 20 is a high pressure stage cylinder
  • the second The cylinder 30 and the third cylinder 40 are at a low pressure level a cylinder, characterized in that the compressor further comprises a variable capacity switching mechanism 50, the variable capacity switching mechanism 50 controls the third cylinder 40 to be unloaded or loaded, and the compressor has a full operation mode and a partial operation mode, when the compressor is in the full operation mode,
  • the variable capacity switching mechanism 50 loads the third cylinder 40 under the action of the exhaust pressure of the compressor; when the compressor is in the partial operation mode, the variable capacity switching mechanism 50 causes the third cylinder under the action of the intake pressure of the compressor. 40 uninstall.
  • the above-mentioned high-pressure stage cylinder refers to a cylinder in which the air pressure is higher than that of the low-pressure stage cylinder, that is, the gas supplied from the low-pressure stage cylinder is compressed again in the high-pressure stage cylinder to generate the second time. Compressed gas.
  • a low pressure stage cylinder refers to a cylinder in which the air pressure is lower relative to the high pressure stage cylinder.
  • the high pressure or low pressure here is relatively comparative, regardless of the numerical range of high pressure and low pressure.
  • variable capacity switching mechanism 50 By providing a variable capacity switching mechanism in the compressor, at least one cylinder is put into use or unloaded by the variable capacity switching mechanism 50, so that the compressor has the function of variable capacity switching, and can meet the operation requirements of different working conditions, It can improve the heating capacity of the compressor under different working conditions and effectively improve the overall energy efficiency of the compressor.
  • the compressor By adopting the method of variable capacity switching, the compressor can be operated with different capacity and volume ratio under the conditions of full operation mode and partial operation mode, so that the compressor has strong adaptability to different working conditions and high comprehensive energy efficiency.
  • variable capacity switching mechanism 50 is used to control the loading or unloading of the third cylinder 40.
  • variable capacity switching mechanism 50 can also selectively control the second cylinder 30 (not shown).
  • the variable capacity switching mechanism 50 includes a pressure control portion and a lock member 52, and the pressure control portion is selectively connected to the exhaust port of the compressor or the intake port of the compressor; the pressure control portion Controlling the cooperation relationship between the locking member 52 and the sliding piece 41 of the third cylinder 40, when the pressure control portion is electrically connected to the intake port of the compressor, the locking member 52 and the sliding piece 41 of the third cylinder 40 are locked to make the first The three cylinders 40 are unloaded, and the lock member 52 and the slide 41 of the third cylinder 40 are unlocked to load the third cylinder 40 when the pressure control portion is electrically connected to the exhaust port of the compressor.
  • the exhaust pressure of the compressor Since the exhaust pressure of the compressor is high and the intake pressure of the compressor is low, the exhaust pressure of the compressor causes the lock member 52 and the slider 41 of the third cylinder 40 in the state shown in FIG. Unlocking, so that the third cylinder 40 is loaded, that is, put into use, at this time, the compressor realizes a full-displacement mode with large displacement and small volume ratio and two-stage compression; in the state shown in FIG. 2, the intake pressure of the compressor makes The locking member 52 is locked with the slider 41 of the third cylinder 40, so that the third cylinder 40 is unloaded, that is, it is idling without compression, and the compressor realizes a partial operation mode of small displacement and large volume ratio of two-stage compression.
  • variable capacity switching mechanism 50 further includes an elastic returning member 53.
  • the first end of the locking member 52 is unlocked or locked with the slide 41, and the elastic returning member 53 is disposed at the lock.
  • the second end of the stop 52 opposite the first end, and the pressure control portion controls the pressure of the first end of the lock member 52. Since the elastic returning member 53 is provided, the locking member 52 is provided with a supporting force for the movement of the side of the slider 41 by the elastic returning member 53, when the exhaust pressure of the compressor overcomes the elastic returning member 53.
  • the lock member 52 and the slide 41 are unlocked, thereby bringing the compressor into the full operation mode.
  • the resilient return element 53 is a spring.
  • the locking member 52 in the present invention is a pin having a head, and when the head of the pin is engaged with the slot of the slider 41, both are locked.
  • variable capacity switching mechanism 50 of the present invention further includes a voltage stabilizing branch 54.
  • the first end of the voltage stabilizing branch 54 communicates with the air inlet of the compressor.
  • the second end of the path 54 provides pressure to the second end of the locking member 52 (please refer to Figures 1 and 2). Since the voltage stabilizing branch 54 always supplies the compressor inlet pressure to the second end of the lock member 52, it is ensured that the first end of the lock member 52 is only used with the discharge pressure of the compressor.
  • the unlocking 41 makes the variable capacity switching mechanism 50 have an advantage of being easy to control.
  • the pressure control portion includes a first branch 511, a first switching valve 512 for controlling the opening and closing of the first branch 511, a second branch 513, and for controlling The second branch valve 513 is connected to the second switch valve 514.
  • the first end of the first branch 511 is in communication with the intake port of the compressor, and the second end of the first branch 511 controls the first end of the lock member 52.
  • the first switching valve 512 is disposed on the first branch 511; the first end of the second branch 513 is in communication with the exhaust port of the compressor, and the second end of the second branch 513 controls the locking member 52
  • the pressure at the first end; the second switching valve 514 is disposed on the second branch 513.
  • the first branch 511 is for supplying the exhaust pressure of the compressor to the lock member 52
  • the second branch 513 is for supplying the exhaust pressure of the compressor to the lock member 52 to realize the lock member 52 and the slide member The unlocking or locking of the sheet 41 is switched.
  • the broken line in the figure indicates that the on-off valve corresponding to the branch is in a closed state, and the branch is unreachable.
  • the present invention provides two specific embodiments depending on the gas supply components.
  • the compressor employs a mixer 60.
  • the compressor employs a reinforcing member 100.
  • the compressor further includes a mixer 60, and the first intake port 61 of the mixer 60 communicates with the exhaust port of the second cylinder 30, the mixer 60
  • the mixer exhaust port 62 communicates with the intake port of the first cylinder 20, and the second intake port 63 of the mixer 60 is an air inlet.
  • the flasher 500 is coupled to the second intake port 63 of the mixer 60.
  • the mixer 60 is disposed outside the casing 11 of the compressor. This prevents the mixer 60 from occupying the internal space of the compressor, so that the two are properly laid out.
  • the upper end of the housing 11 is further provided with an upper cover assembly 12 and a lower cover 13.
  • the compressor further includes a stator assembly 14, a rotor assembly 15 disposed within the stator assembly 14, a first roller 21 disposed within the first cylinder 20, a second roller 33 disposed within the second cylinder 30, and a A third roller 43 in the three cylinders 40 and a third separator 16 disposed between the second cylinder 30 and the first cylinder 20 are provided.
  • the compressor further includes a second flange 900 disposed on a side of the first cylinder 20 remote from the second cylinder 30.
  • the compressor further includes a first partition 70, and the first partition 70 is disposed between the second cylinder 30 and the third cylinder 40.
  • the compressor in this embodiment adopts a structure in which the second cylinder 30 is exhausted, the mixer 60 (with medium-pressure refrigerant therein) is externally disposed, and the medium-pressure refrigerant discharged from the low-pressure stage cylinder is taken to the intake passage of the high-pressure stage cylinder. It consists of an external pipe.
  • the first partition plate 70 has a first partition cavity 71 that communicates with the exhaust port of the second cylinder 30, and the second cylinder 30 also has a cavity with the first partition plate.
  • the 71-connected external communication port 31, the first air inlet 61 of the mixer 60 communicates with the first diaphragm cavity 71 through the external communication port 31.
  • the third cylinder 40 has a first intermediate flow passage 42 isolated from the compression chamber of the third cylinder 40, and the compressor further includes a second partition 80 and a first flange 90, the second partition
  • the plate 80 is disposed between the first partition 70 and the third cylinder 40, and the second partition 80 further has a second partition that connects the first intermediate flow passage 42 of the third cylinder 40 with the first diaphragm cavity 71.
  • a first flange 90 is disposed on a side of the third cylinder 40 remote from the second cylinder 30, and the first flange 90 has a first flange cavity 91, a first flange cavity 91 and a third cylinder 40 Both the exhaust port and the first intermediate flow path 42 are in communication.
  • the second partition 80, the first partition 70, and the second cylinder 30 cause the first partition cavity 71 to form a refrigerant containing chamber for accommodating the exhaust of the second cylinder 30.
  • the compressor further includes a first flange cover 92 interposed between the third cylinder 40 and the first flange cover 92 such that the first flange cavity 91 A refrigerant accommodating chamber for accommodating the exhaust gas of the third cylinder 40 is formed.
  • the internal flow path of the refrigerant is disposed on the third cylinder 40, the first flange 90, the second separator 80, the second cylinder 30, and the first separator 70.
  • the variable pressure control passage 44 of the variable displacement switching mechanism 50 of the compressor is disposed on the third cylinder 40, the first flange 90, and the first flange cover 92.
  • the third cylinder 40, the first flange 90 and the first flange cover 92 each have a variable pressure control passage 44 (control of the pressure of the first end and the second end of the lock member 52) .
  • the first switching valve 512 is turned on, the second switching valve 514 is turned off, and the compressor is operated with a small displacement and a large volume ratio than the two-cylinder two-stage mode.
  • the refrigerant gas supplied from the liquid separator 800 is sent into the second cylinder 30, and the refrigerant gas after the first compression is discharged into the first diaphragm cavity 71, and then passes through the external communication port 31 of the second cylinder 30.
  • the supplemental gas supplied from the side of the flasher 500 is introduced into the second intake port 63 of the mixer 60, mixed with the gas in the mixer 60, and sent into the first cylinder 20 together.
  • the second compression is performed, and then discharged to the upper space of the casing 11, and then discharged through the exhaust pipe of the upper cover assembly 12, until the compressor completes the entire compressor process of the refrigerant.
  • the intake port of one cylinder 20 and the exhaust port of the first cylinder 20 are sequentially connected, and the intake port of the third cylinder 40 passes through the exhaust port of the third cylinder 40, the first flange cavity 91, and the first intermediate portion
  • the flow passage 42 and the second diaphragm communication hole communicate with the first diaphragm cavity 71.
  • the second switching valve 514 is turned on, the first switching valve 512 is closed, and the compressor is operated with a large displacement and a small volume ratio three-cylinder two-stage mode.
  • the refrigerant gas supplied from the liquid separator 800 is sent into the second cylinder 30, and the refrigerant gas after the first compression is discharged into the first diaphragm cavity 71; at the same time, the refrigerant supplied from the liquid separator 800 At the same time, it is sent into the third cylinder 40, and the refrigerant gas after the first compression is discharged to the first flange cavity 91, and the refrigerant gas in the first flange cavity 91 passes through the first flange 90, the second The partition 80, the first partition cavity 71, and the external communication port 31 of the second cylinder 30 enter the mixer 60; at the same time, the qi supplied from the side of the flasher 500 is introduced into the second of the mixer 60.
  • the gas port 63 is mixed with the gas in the mixer 60 and sent to the first cylinder 20 for a second compression, and then discharged to the upper space of the casing 11, and then discharged through the exhaust pipe of the upper cover assembly 12, At this point the compressor completes the entire compressor process of the refrigerant.
  • the compressor further includes an augmenting member 100 that communicates with an intake port of the first cylinder 20.
  • the flasher 500 is coupled to the augmentation component 100.
  • the upper end of the housing 11 is further provided with an upper cover assembly 12 and a lower cover 13.
  • the compressor further includes a stator assembly 14, a rotor assembly 15 disposed within the stator assembly 14, a first roller 21 disposed within the first cylinder 20, a second roller 33 disposed within the second cylinder 30, and a The third roller 43 in the three cylinders 40.
  • the compressor further includes a first partition 70 and a third partition 16, the first partition 70 is disposed between the second cylinder 30 and the first cylinder 20, and the third partition 16 is disposed at the first
  • the cylinder 20 is between the first partition plate 70.
  • the compressor in this embodiment adopts a structure of exhausting the second cylinder 30, and the intermediate pressure refrigerant flow passage is disposed inside the casing 11, and is respectively disposed in the third cylinder 40, the first flange 90, and the second partition. 80.
  • the variable pressure control passage 44 of the compressor is disposed on the third cylinder 40, the first flange 90, and the first flange cover 92 (the pressure of the first end and the second end of the lock member 52 is controlled).
  • the compressor further includes a second flange 900 disposed on a side of the first cylinder 20 remote from the second cylinder 30.
  • the third partition plate 16 has a third partition plate communication hole
  • the first partition plate 70 has a first partition plate cavity 71 communicating with the exhaust port of the second cylinder 30,
  • the first diaphragm cavity 71 communicates with the intake port of the first cylinder 20 through the third diaphragm communication hole.
  • the third cylinder 40 has a first intermediate flow passage 42 that is isolated from the compression chamber of the third cylinder 40, and the second cylinder 30 also has a second intermediate portion that is isolated from the compression chamber of the second cylinder 30.
  • the flow passage 32, the second intermediate flow passage 32 communicates with the first partition cavity 71
  • the compressor further includes a second partition 80 and a first flange 90
  • the second partition 80 is disposed at the second cylinder 30 and the third
  • the second partition 80 further has a second partition communicating hole that communicates the first intermediate flow passage 42 of the third cylinder 40 with the second intermediate flow passage 32 of the second cylinder 30;
  • the first flange 90 Disposed on a side of the third cylinder 40 remote from the second cylinder 30, the first flange 90 has a first flange cavity 91, a first flange cavity 91 and an exhaust port of the third cylinder 40 and a first intermediate portion
  • the flow passages 42 are all connected.
  • the first partition plate 70, the third partition plate 16, and the second cylinder 30 form the first partition cavity 71 to form a refrigerant containing chamber for accommodating the exhaust gas of the second cylinder 30.
  • the first flange 90, the third cylinder 40, and the first flange cover 92 form the first flange cavity 91 to form an exhaust refrigerant accommodating chamber for accommodating the third cylinder 40.
  • the intake port of the second cylinder 30, the exhaust port of the second cylinder 30, the first diaphragm cavity 71, the third diaphragm communication hole, and the air inlet of the first cylinder 20 are sequentially connected.
  • the second switching valve 514 is closed, the first switching valve 512 is turned on, and the compressor operates with a small displacement and a large volume ratio than the two-cylinder two-stage mode.
  • the refrigerant gas supplied from the liquid separator 800 is sent into the second cylinder 30, and the refrigerant gas after the first compression is discharged into the first diaphragm cavity 71, and is filled in with the side of the reinforcing member 100.
  • the gas is fed into the first cylinder 20 for secondary compression, and then discharged to the upper space of the casing 11, and then discharged through the exhaust pipe of the upper cover assembly 12, until the compressor completes the entire compressor process of the refrigerant.
  • the intake port of the second cylinder 30, the exhaust port of the second cylinder 30, the first diaphragm cavity 71, the intake port of the first cylinder 20, and the row of the first cylinder 20 The air ports are connected in sequence, and the air inlets of the third cylinder 40 are open
  • the exhaust port of the third cylinder 40, the first flange cavity 91, the first intermediate flow path 42, the second diaphragm communication hole, and the second intermediate flow path 32 communicate with the first diaphragm cavity 71.
  • the second switching valve 514 is turned on, the first switching valve 512 is closed, and the compressor is operated with a large displacement and a small volume ratio three-cylinder two-stage mode.
  • the refrigerant gas supplied from the liquid separator 800 is sent into the second cylinder 30, and the refrigerant gas after the first compression is discharged into the first diaphragm cavity 71; at the same time, the refrigerant supplied from the liquid separator 800 At the same time, it is sent into the third cylinder 40, and the refrigerant gas after the first compression is discharged to the first flange cavity 91, and the refrigerant gas in the first flange cavity 91 passes through the first flange 90, the second The partition 80 is fed into the first partition cavity 71; at this time, the gas in the first partition cavity 71 and the gas supplemented by the side of the reinforcing member 100 are fed into the first cylinder 20 to perform two.
  • the secondary compression is then discharged to the upper space of the casing 11, and then discharged through the exhaust pipe of the upper cover assembly 12, until the compressor completes the entire compressor process of the refrigerant.

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Abstract

一种压缩机，包括曲轴（10）和沿曲轴（10）的轴向依次排列的第一气缸（20）、第二气缸（30）和第三气缸（40），第一气缸（20）是高压级气缸，第二气缸（30）和第三气缸（40）为低压级气缸，还包括变容切换机构（50），其控制第三气缸（40）卸载或加载，压缩机具有全运行模式和部分运行模式，当压缩机处于全运行模式时，变容切换机构（50）在压缩机的排气压力的作用下使第三气缸（40）加载；当压缩机处于部分运行模式时，变容切换机构（50）在压缩机的进气压力的作用下使第三气缸（40）卸载；以及一种包括该压缩机的换热系统。通过在压缩机内设置变容切换机构（50），以使至少一个气缸在变容切换机构（50）的作用下投入使用或卸载，从而使压缩机具有变容切换的功能，能够满足不同工况的运行要求并提高不同工况下的压缩机的制热能力。

Description

压缩机和换热系统 技术领域
本发明涉及换热技术领域，具体而言，涉及一种压缩机和换热系统。
背景技术
现有技术中，通常采用电辅热来提高压缩机的制热量，或者采用具有双级增焓功能的压缩机来解决压缩机存在的低温制热能力差的问题，但存在不同程度的问题。
1.采用电辅热来提高压缩机的制热量的方法，存在能效较低的问题；
2.采用具有双级增焓功能的压缩机，存在压缩机的排量无法调节、压缩机对运行工况的适应能力较差，在保证压缩机在低温工况下的制热能力和能效的前提下，会导致压缩机在普通工况下运行时存在能效降低的问题。
发明内容
本发明的主要目的在于提供一种压缩机和换热系统，以解决现有技术中的压缩机由于无法变容运行而导致压缩机的制热能力差、能效低的问题。
为了实现上述目的，根据本发明的一个方面，提供了一种压缩机，包括曲轴和沿曲轴的轴向依次排列的第一气缸、第二气缸和第三气缸，第一气缸是高压级气缸，第二气缸和第三气缸为低压级气缸，压缩机还包括变容切换机构，变容切换机构控制第三气缸卸载或加载，压缩机具有全运行模式和部分运行模式，当压缩机处于全运行模式时，变容切换机构在压缩机的排气压力的作用下使第三气缸加载；当压缩机处于部分运行模式时，变容切换机构在压缩机的进气压力的作用下使第三气缸卸载。
进一步地，变容切换机构包括：压力控制部，压力控制部选择性地与压缩机的排气口或压缩机的进气口导通；锁止件，压力控制部控制锁止件与第三气缸的滑片的配合关系，当压力控制部与压缩机的进气口导通时锁止件与第三气缸的滑片锁止以使第三气缸卸载，当压力控制部与压缩机的排气口导通时锁止件与第三气缸的滑片解锁以使第三气缸加载。
进一步地，变容切换机构还包括弹性复位元件，锁止件的第一端与滑片解锁或锁止，弹性复位元件设置在锁止件的与第一端相对的第二端上，且压力控制部控制锁止件的第一端的压力。
进一步地，变容切换机构还包括稳压支路，稳压支路的第一端与压缩机的进气口连通，稳压支路的第二端为锁止件的第二端提供压力。
进一步地，压力控制部包括：第一支路，第一支路的第一端与压缩机的进气口连通，第一支路的第二端控制锁止件的第一端的压力；用于控制第一支路通断的第一开关阀，第一开关阀设置在第一支路上；第二支路，第二支路的第一端与压缩机的排气口连通，第二支路的第二端控制锁止件的第一端的压力；用于控制第二支路通断的第二开关阀，第二开关阀设置在第二支路上。
进一步地，压缩机还包括混合器，混合器的第一进气口与第二气缸的排气口连通，混合器的混合器排气口与第一气缸的进气口连通，且混合器的第二进气口为补气口。
进一步地，压缩机还包括第一隔板，第一隔板设置在第二气缸与第三气缸之间。
进一步地，第一隔板具有与第二气缸的排气口连通的第一隔板空腔，第二气缸还具有与第一隔板空腔连通的外部连通口，混合器的第一进气口通过外部连通口与第一隔板空腔连通，当压缩机处于部分运行模式时，第二气缸的进气口、第二气缸的排气口、第一隔板空腔、第二气缸的外部连通口、混合器、第一气缸的进气口、第一气缸的排气口顺次连通。
进一步地，第三气缸具有与第三气缸的压缩腔隔离的第一中间流道，压缩机还包括：第二隔板，第二隔板设置在第一隔板与第三气缸之间，第二隔板还具有使第三气缸的第一中间流道与第一隔板空腔连通的第二隔板连通孔；第一法兰，第一法兰设置在第三气缸的远离第二气缸的一侧，第一法兰具有第一法兰空腔，第一法兰空腔与第三气缸的排气口和第一中间流道均连通，当压缩机处于全运行模式时，第二气缸的进气口、第二气缸的排气口、第一隔板空腔、第二气缸的外部连通口、混合器、第一气缸的进气口、第一气缸的排气口顺次连通，且第三气缸的进气口通过第三气缸的排气口、第一法兰空腔、第一中间流道、第二隔板连通孔与第一隔板空腔连通。
进一步地，压缩机还包括增焓部件，增焓部件与第一气缸的进气口连通。
进一步地，压缩机还包括：第一隔板，第一隔板设置在第二气缸与第一气缸之间；第三隔板，第三隔板设置在第一气缸与第一隔板之间。
进一步地，第三隔板具有第三隔板连通孔，第一隔板具有与第二气缸的排气口连通的第一隔板空腔，且第一隔板空腔通过第三隔板连通孔与第一气缸的进气口连通，当压缩机处于部分运行模式时，第二气缸的进气口、第二气缸的排气口、第一隔板空腔、第三隔板连通孔、第一气缸的进气口、第一气缸的排气口顺次连通。
进一步地，第三气缸具有与第三气缸的压缩腔隔离的第一中间流道，第二气缸还具有与第二气缸的压缩腔隔离的第二中间流道，第二中间流道与第一隔板空腔连通，压缩机还包括：第二隔板，第二隔板设置在第二气缸与第三气缸之间，第二隔板还具有使第三气缸的第一中间流道与第二气缸的第二中间流道连通的第二隔板连通孔；第一法兰，第一法兰设置在第三气缸的远离第二气缸的一侧，第一法兰具有第一法兰空腔，第一法兰空腔与第三气缸的排气口和第一中间流道均连通，当压缩机处于全运行模式时，第二气缸的进气口、第二气缸的排气口、第一隔板空腔、第一气缸的进气口、第一气缸的排气口顺次连通，且第三气缸的进气 口通过第三气缸的排气口、第一法兰空腔、第一中间流道、第二隔板连通孔与第二中间流道与第一隔板空腔连通。
根据本发明的另一方面，提供了一种换热系统，包括压缩机，压缩机是下述的压缩机。
应用本发明的技术方案，通过在压缩机内设置变容切换机构，以使至少一个气缸在变容切换机构的作用下投入使用或卸载，从而使压缩机具有变容切换的功能、能够满足不同工况的运行要求、能够提高不同工况下的压缩机的制热能力、有效提高了压缩机的综合能效。
附图说明
构成本申请的一部分的说明书附图用来提供对本发明的进一步理解，本发明的示意性实施例及其说明用于解释本发明，并不构成对本发明的不当限定。在附图中：
图1示出了本发明中的压缩机处于全运行模式下的换热系统的运行原理图；
图2示出了本发明中的压缩机处于部分运行模式下的换热系统的运行原理图；
图3示出了本发明中的变容切换机构与第三气缸锁止时的工作状态示意图；
图4示出了本发明中的变容切换机构与第三气缸解锁时的工作状态示意图；
图5示出了本发明的第一个实施例中的压缩机的外观结构示意图；
图6示出了图5中的压缩机的内部结构示意图；
图7示出了图6中的压缩机处于部分运行模式下的制冷剂流动示意图；
图8示出了图6中的压缩机处于全运行模式下的制冷剂流动示意图；
图9示出了图6中的压缩机的第一隔板的结构示意图；
图10示出了图6中的压缩机的第二气缸的结构示意图；
图11示出了图6中的压缩机的第三气缸的结构示意图；
图12示出了图6中的压缩机的第一法兰的结构示意图；
图13示出了图6中的压缩机的第一法兰盖板的结构示意图；
图14示出了图6中的压缩机的第一法兰、第三气缸和第一法兰盖板组合后的通道关系示意图；
图15示出了本发明的第二个实施例中的压缩机的外观结构示意图；
图16示出了图15中的压缩机的内部结构示意图；
图17示出了图16中的压缩机处于部分运行模式下的制冷剂流动示意图；
图18示出了图16中的压缩机处于全运行模式下的制冷剂流动示意图；
图19示出了图16中的压缩机的第一气缸的结构示意图；
图20示出了图16中的压缩机的第一隔板的结构示意图；以及
图21示出了图16中的压缩机的第二气缸的结构示意图。
其中，上述附图包括以下附图标记：
10、曲轴；11、壳体；12、上盖组件；13、下盖；14、定子组件；15、转子组件；16、第三隔板；20、第一气缸；21、第一滚子；30、第二气缸；31、外部连通口；32、第二中间流道；33、第二滚子；40、第三气缸；41、滑片；42、第一中间流道；43、第三滚子；44、变容压力控制通道；50、变容切换机构；511、第一支路；512、第一开关阀；513、第二支路；514、第二开关阀；52、锁止件；53、弹性复位元件；54、稳压支路；60、混合器；61、第一进气口；62、混合器排气口；63、第二进气口；70、第一隔板；71、第一隔板空腔；80、第二隔板；90、第一法兰；91、第一法兰空腔；92、第一法兰盖板；100、增焓部件；200、四通阀；300、第一换热器；400、第一节流阀；500、闪蒸器；600、第二节流阀；700、第二换热器；800、分液器；900、第二法兰。
具体实施方式
需要说明的是，在不冲突的情况下，本申请中的实施例及实施例中的特征可以相互组合。下面将参考附图并结合实施例来详细说明本发明。
应该指出，以下详细说明都是例示性的，旨在对本申请提供进一步的说明。除非另有指明，本文使用的所有技术和科学术语具有与本申请所属技术领域的普通技术人员通常理解的相同含义。
在本发明中，在未作相反说明的情况下，使用的方位词如“内、外”是指相对于各部件本身的轮廓的内、外，但上述方位词并不用于限制本发明。
为了解决现有技术中的压缩机由于无法变容运行而导致压缩机的制热能力差、能效低的问题，本发明提供了一种压缩机和换热系统，其中，换热系统包括压缩机，压缩机是下述的压缩机。
如图1和图2所示，换热系统还包括四通阀200、第一换热器300、第一节流阀400、闪蒸器500、第二节流阀600、第二换热器700、分液器800以及下述的增焓部件100或混合器60，其中，压缩机的排气口通过四通阀200、第一换热器300、第一节流阀400、闪蒸器500、第二节流阀600、第二换热器700与四通阀200连通，四通阀200还通过分液器800与压缩机的进气口连通。闪蒸器500通过增焓部件100或混合器60与压缩机的气缸连通。
如图1和图2所示，压缩机包括曲轴10和沿曲轴10的轴向依次排列的第一气缸20、第二气缸30和第三气缸40，第一气缸20是高压级气缸，第二气缸30和第三气缸40为低压级 气缸，其特征在于，压缩机还包括变容切换机构50，变容切换机构50控制第三气缸40卸载或加载，压缩机具有全运行模式和部分运行模式，当压缩机处于全运行模式时，变容切换机构50在压缩机的排气压力的作用下使第三气缸40加载；当压缩机处于部分运行模式时，变容切换机构50在压缩机的进气压力的作用下使第三气缸40卸载。
需要说明的是，上述所指的高压级气缸是指其内的气压相对于低压级气缸更高的气缸，也就是由低压级气缸内供给的气体在高压级气缸内再次压缩后以产生二次压缩的气体。同样地，低压级气缸是指其内的气压相对于高压级气缸更低的气缸。这里的高压或低压是相对比较而言的，与高压、低压的数值范围无关。
通过在压缩机内设置变容切换机构，以使至少一个气缸在变容切换机构50的作用下投入使用或卸载，从而使压缩机具有变容切换的功能、能够满足不同工况的运行要求、能够提高不同工况下的压缩机的制热能力、有效提高了压缩机的综合能效。通过采用变容切换的方式，以使压缩机在全运行模式和部分运行模式的工况下以不同的容量和容积比运行，从而使压缩机具有对不同工况的适应能力强、综合能效高的优点。
图1和图2所示的优选实施方式中，变容切换机构50用于对第三气缸40进行加载或卸载的控制。当然，变容切换机构50还可以选择对第二气缸30进行控制(图未示)。
如图1至图4所示，变容切换机构50包括压力控制部和锁止件52，压力控制部选择性地与压缩机的排气口或压缩机的进气口导通；压力控制部控制锁止件52与第三气缸40的滑片41的配合关系，当压力控制部与压缩机的进气口导通时锁止件52与第三气缸40的滑片41锁止以使第三气缸40卸载，当压力控制部与压缩机的排气口导通时锁止件52与第三气缸40的滑片41解锁以使第三气缸40加载。由于压缩机的排气压力较高，而压缩机的进气压力较低，因而在图1所示的状态下，压缩机的排气压力使锁止件52与第三气缸40的滑片41解锁，从而使第三气缸40加载，也就是投入使用，这时压缩机实现大排量小容积比双级压缩的全运行模式；在图2所示的状态下，压缩机的进气压力使锁止件52与第三气缸40的滑片41锁止，从而使第三气缸40卸载，也就是不压缩仅空转，这时压缩机实现小排量大容积比双级压缩的部分运行模式。
如图3和图4所示的具体实施方式中，变容切换机构50还包括弹性复位元件53，锁止件52的第一端与滑片41解锁或锁止，弹性复位元件53设置在锁止件52的与第一端相对的第二端上，且压力控制部控制锁止件52的第一端的压力。由于设置有弹性复位元件53，因而在弹性复位元件53的作用下，会给锁止件52提供一个向滑片41一侧的运动的支撑力，当压缩机的排气压力克服弹性复位元件53做功时，才会使锁止件52与滑片41解锁，从而使压缩机进入全运行模式。
优选地，弹性复位元件53是弹簧。
本发明中的锁止件52为具有头部的销钉，当销钉的头部与滑片41的卡槽卡合后，二者锁止。
为了进一步提高对锁止件52的压力控制，本发明中的变容切换机构50还包括稳压支路54，稳压支路54的第一端与压缩机的进气口连通，稳压支路54的第二端为锁止件52的第二端提供压力(请参考图1和图2)。由于稳压支路54始终为锁止件52的第二端提供压缩机的进气压力，因而保证仅当锁止件52的第一端在压缩机的排气压力作用下才会与滑片41解锁，从而使变容切换机构50具有易控性好的优点。
在图1和图2所示的优选实施方式中，压力控制部包括第一支路511、用于控制第一支路511通断的第一开关阀512、第二支路513和用于控制第二支路513通断的第二开关阀514，第一支路511的第一端与压缩机的进气口连通，第一支路511的第二端控制锁止件52的第一端的压力；第一开关阀512设置在第一支路511上；第二支路513的第一端与压缩机的排气口连通，第二支路513的第二端控制锁止件52的第一端的压力；第二开关阀514设置在第二支路513上。第一支路511用于将压缩机的排气压力提供给锁止件52，第二支路513用于将压缩机的排气压力提供给锁止件52，以实现锁止件52与滑片41的解锁或锁止的切换。
需要说明的是，图中的虚线表示该支路对应的开关阀处于关闭状态，该支路不通。
根据补气部件的不同，本发明提供了两种具体的实施方式。在第一个实施方式中压缩机采用混合器60，在第二个实施方式中，压缩机采用增焓部件100。下面将分别介绍这两个具体实施方式。
在第一个实施方式中，如图5至图14所示，压缩机还包括混合器60，混合器60的第一进气口61与第二气缸30的排气口连通，混合器60的混合器排气口62与第一气缸20的进气口连通，且混合器60的第二进气口63为补气口。如上述，闪蒸器500与混合器60的第二进气口63连接。
如图5所示，混合器60设置在压缩机的壳体11的外部。这样避免混合器60占用压缩机的内部空间，使二者合理布局。
如图6所示，壳体11的两端还设置有上盖组件12和下盖13。压缩机还包括定子组件14、设置在定子组件14内的转子组件15、设置在第一气缸20内的第一滚子21、设置在第二气缸30内的第二滚子33、设置在第三气缸40内的第三滚子43、设置在第二气缸30和第一气缸20之间的第三隔板16。
如图6所示，压缩机还包括第二法兰900，第二法兰900设置在第一气缸20的远离第二气缸30的一侧。
如图6所示，压缩机还包括第一隔板70，第一隔板70设置在第二气缸30与第三气缸40之间。本实施例中的压缩机采用第二气缸30下排气、混合器60(内有中压制冷剂)外置的结构，低压级气缸排出的中压制冷剂至高压级气缸吸气的流道由外部管路构成。
如图7、图9和图10所示，第一隔板70具有与第二气缸30的排气口连通的第一隔板空腔71，第二气缸30还具有与第一隔板空腔71连通的外部连通口31，混合器60的第一进气口61通过外部连通口31与第一隔板空腔71连通。
如图8至图14所示，第三气缸40具有与第三气缸40的压缩腔隔离的第一中间流道42，压缩机还包括第二隔板80和第一法兰90，第二隔板80设置在第一隔板70与第三气缸40之间，第二隔板80还具有使第三气缸40的第一中间流道42与第一隔板空腔71连通的第二隔板连通孔；第一法兰90设置在第三气缸40的远离第二气缸30的一侧，第一法兰90具有第一法兰空腔91，第一法兰空腔91与第三气缸40的排气口和第一中间流道42均连通。
其中，第二隔板80、第一隔板70和第二气缸30使第一隔板空腔71形成用于容纳第二气缸30的排气的制冷剂容纳腔。
如图6所示，压缩机还包括第一法兰盖板92，第一法兰90夹设在第三气缸40和第一法兰盖板92之间，以使第一法兰空腔91形成用于容纳第三气缸40的排气的制冷剂容纳腔。
此外，制冷剂的内部流道设置在第三气缸40、第一法兰90、第二隔板80、第二气缸30、第一隔板70上。压缩机的变容切换机构50的变容压力控制通道44设置在第三气缸40、第一法兰90和第一法兰盖板92上。
如图14所示，第三气缸40、第一法兰90和第一法兰盖板92均具有变容压力控制通道44(对锁止件52的第一端和第二端的压力进行控制)。
当压缩机处于部分运行模式时，第二气缸30的进气口、第二气缸30的排气口、第一隔板空腔71、第二气缸30的外部连通口31、混合器60、第一气缸20的进气口、第一气缸20的排气口顺次连通。此时，第一开关阀512导通、第二开关阀514关闭，压缩机运行小排量大容积比双缸双级模式。由分液器800供给的制冷剂气体送入第二气缸30内，经第一次压缩后的制冷剂气体排出至第一隔板空腔71内，再经过第二气缸30的外部连通口31进入到混合器60中；同时，由闪蒸器500一侧供给的补气通入混合器60的第二进气口63内，与混合器60内的气体混合后一同送入第一气缸20内进行第二次压缩，然后排出到壳体11的上部空间，再经过上盖组件12的排气管排出，至此压缩机完成制冷剂的整个压缩机过程。
当压缩机处于全运行模式时，第二气缸30的进气口、第二气缸30的排气口、第一隔板空腔71、第二气缸30的外部连通口31、混合器60、第一气缸20的进气口、第一气缸20的排气口顺次连通，且第三气缸40的进气口通过第三气缸40的排气口、第一法兰空腔91、第一中间流道42、第二隔板连通孔与第一隔板空腔71连通。此时，第二开关阀514导通，第一开关阀512关闭，压缩机运行大排量小容积比三缸双级模式。由分液器800供给的制冷剂气体送入第二气缸30内，经第一次压缩后的制冷剂气体排出至第一隔板空腔71内；同时，有分液器800供给的制冷剂同时送入第三气缸40内，经第一次压缩后的制冷剂气体排出至第一法兰空腔91，第一法兰空腔91中的制冷剂气体经第一法兰90、第二隔板80、第一隔板空腔71、第二气缸30的外部连通口31、进入至混合器60中；同时，由闪蒸器500一侧供给的补气通入混合器60的第二进气口63内，与混合器60内的气体混合后一同送入第一气缸20内进行第二次压缩，然后排出到壳体11的上部空间，再经过上盖组件12的排气管排出，至此压缩机完成制冷剂的整个压缩机过程。
在第二个实施方式中，如图15至图21所示，压缩机还包括增焓部件100，增焓部件100与第一气缸20的进气口连通。如上述，闪蒸器500与增焓部件100连接。如图16所示，壳体11的两端还设置有上盖组件12和下盖13。压缩机还包括定子组件14、设置在定子组件14内的转子组件15、设置在第一气缸20内的第一滚子21、设置在第二气缸30内的第二滚子33、设置在第三气缸40内的第三滚子43。
如图16所示，压缩机还包括第一隔板70和第三隔板16，第一隔板70设置在第二气缸30与第一气缸20之间，第三隔板16设置在第一气缸20与第一隔板70之间。本实施例中的压缩机采用第二气缸30上排气的结构，将中压冷媒流道设置在壳体11的内部，分别设置在第三气缸40、第一法兰90、第二隔板80、第二气缸30、第一隔板70、第三隔板16上。而压缩机的变容压力控制通道44设置在第三气缸40、第一法兰90和第一法兰盖板92上(对锁止件52的第一端和第二端的压力进行控制)。
如图16所示，压缩机还包括第二法兰900，第二法兰900设置在第一气缸20的远离第二气缸30的一侧。
如图16、图19和图20所示，第三隔板16具有第三隔板连通孔，第一隔板70具有与第二气缸30的排气口连通的第一隔板空腔71，且第一隔板空腔71通过第三隔板连通孔与第一气缸20的进气口连通。
如图17至图21所示，第三气缸40具有与第三气缸40的压缩腔隔离的第一中间流道42，第二气缸30还具有与第二气缸30的压缩腔隔离的第二中间流道32，第二中间流道32与第一隔板空腔71连通，压缩机还包括第二隔板80和第一法兰90，第二隔板80设置在第二气缸30与第三气缸40之间，第二隔板80还具有使第三气缸40的第一中间流道42与第二气缸30的第二中间流道32连通的第二隔板连通孔；第一法兰90设置在第三气缸40的远离第二气缸30的一侧，第一法兰90具有第一法兰空腔91，第一法兰空腔91与第三气缸40的排气口和第一中间流道42均连通。
其中，第一隔板70、第三隔板16和第二气缸30使第一隔板空腔71形成用于容纳第二气缸30的排气的制冷剂容纳腔。第一法兰90、第三气缸40、第一法兰盖板92使第一法兰空腔91形成用于容纳第三气缸40的排气制冷剂容纳腔。
当压缩机处于部分运行模式时，第二气缸30的进气口、第二气缸30的排气口、第一隔板空腔71、第三隔板连通孔、第一气缸20的进气口、第一气缸20的排气口顺次连通。此时，第二开关阀514关闭，第一开关阀512导通，压缩机运行小排量大容积比双缸双级模式。由分液器800供给的制冷剂气体送入第二气缸30内，经第一次压缩后的制冷剂气体排出至第一隔板空腔71内，并与由增焓部件100一侧补入的气体共同送入第一气缸20内以进行二次压缩，然后排出到壳体11的上部空间，再经过上盖组件12的排气管排出，至此压缩机完成制冷剂的整个压缩机过程。
当压缩机处于全运行模式时，第二气缸30的进气口、第二气缸30的排气口、第一隔板空腔71、第一气缸20的进气口、第一气缸20的排气口顺次连通，且第三气缸40的进气口通 过第三气缸40的排气口、第一法兰空腔91、第一中间流道42、第二隔板连通孔与第二中间流道32与第一隔板空腔71连通。此时，第二开关阀514导通，第一开关阀512关闭，压缩机运行大排量小容积比三缸双级模式。由分液器800供给的制冷剂气体送入第二气缸30内，经第一次压缩后的制冷剂气体排出至第一隔板空腔71内；同时，有分液器800供给的制冷剂同时送入第三气缸40内，经第一次压缩后的制冷剂气体排出至第一法兰空腔91，第一法兰空腔91中的制冷剂气体经第一法兰90、第二隔板80送入第一隔板空腔71中；此时，第一隔板空腔71内的气体和由增焓部件100一侧补入的气体共同送入第一气缸20内以进行二次压缩，然后排出到壳体11的上部空间，再经过上盖组件12的排气管排出，至此压缩机完成制冷剂的整个压缩机过程。
需要注意的是，这里所使用的术语仅是为了描述具体实施方式，而非意图限制根据本申请的示例性实施方式。如在这里所使用的，除非上下文另外明确指出，否则单数形式也意图包括复数形式，此外，还应当理解的是，当在本说明书中使用术语“包含”和/或“包括”时，其指明存在特征、步骤、工作、器件、组件和/或它们的组合。
需要说明的是，本申请的说明书和权利要求书及上述附图中的术语“第一”、“第二”等是用于区别类似的对象，而不必用于描述特定的顺序或先后次序。应该理解这样使用的数据在适当情况下可以互换，以便这里描述的本申请的实施方式能够以除了在这里图示或描述的那些以外的顺序实施。
以上所述仅为本发明的优选实施例而已，并不用于限制本发明，对于本领域的技术人员来说，本发明可以有各种更改和变化。凡在本发明的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本发明的保护范围之内。

Claims (14)

  1. 一种压缩机，包括曲轴(10)和沿所述曲轴(10)的轴向依次排列的第一气缸(20)、第二气缸(30)和第三气缸(40)，所述第一气缸(20)是高压级气缸，所述第二气缸(30)和所述第三气缸(40)为低压级气缸，其特征在于，所述压缩机还包括变容切换机构(50)，所述变容切换机构(50)控制所述第三气缸(40)卸载或加载，所述压缩机具有全运行模式和部分运行模式，
    当所述压缩机处于所述全运行模式时，所述变容切换机构(50)在所述压缩机的排气压力的作用下使所述第三气缸(40)加载；
    当所述压缩机处于所述部分运行模式时，所述变容切换机构(50)在所述压缩机的进气压力的作用下使所述第三气缸(40)卸载。
  2. 根据权利要求1所述的压缩机，其特征在于，所述变容切换机构(50)包括：
    压力控制部，所述压力控制部选择性地与所述压缩机的排气口或所述压缩机的进气口导通；
    锁止件(52)，所述压力控制部控制所述锁止件(52)与所述第三气缸(40)的滑片(41)的配合关系，当所述压力控制部与所述压缩机的进气口导通时所述锁止件(52)与所述第三气缸(40)的滑片(41)锁止以使所述第三气缸(40)卸载，当所述压力控制部与所述压缩机的排气口导通时所述锁止件(52)与所述第三气缸(40)的滑片(41)解锁以使所述第三气缸(40)加载。
  3. 根据权利要求2所述的压缩机，其特征在于，所述变容切换机构(50)还包括弹性复位元件(53)，所述锁止件(52)的第一端与所述滑片(41)解锁或锁止，所述弹性复位元件(53)设置在所述锁止件(52)的与所述第一端相对的第二端上，且所述压力控制部控制所述锁止件(52)的第一端的压力。
  4. 根据权利要求3所述的压缩机，其特征在于，所述变容切换机构(50)还包括稳压支路(54)，所述稳压支路(54)的第一端与所述压缩机的进气口连通，所述稳压支路(54)的第二端为所述锁止件(52)的第二端提供压力。
  5. 根据权利要求3所述的压缩机，其特征在于，所述压力控制部包括：
    第一支路(511)，所述第一支路(511)的第一端与所述压缩机的进气口连通，所述第一支路(511)的第二端控制所述锁止件(52)的第一端的压力；
    用于控制所述第一支路(511)通断的第一开关阀(512)，所述第一开关阀(512)设置在所述第一支路(511)上；
    第二支路(513)，所述第二支路(513)的第一端与所述压缩机的排气口连通，所述第二支路(513)的第二端控制所述锁止件(52)的第一端的压力；
    用于控制所述第二支路(513)通断的第二开关阀(514)，所述第二开关阀(514)设置在所述第二支路(513)上。
  6. 根据权利要求1至5中任一项所述的压缩机，其特征在于，所述压缩机还包括混合器(60)，所述混合器(60)的第一进气口(61)与所述第二气缸(30)的排气口连通，所述混合器(60)的混合器排气口(62)与所述第一气缸(20)的进气口连通，且所述混合器(60)的第二进气口(63)为补气口。
  7. 根据权利要求6所述的压缩机，其特征在于，所述压缩机还包括第一隔板(70)，所述第一隔板(70)设置在所述第二气缸(30)与所述第三气缸(40)之间。
  8. 根据权利要求7所述的压缩机，其特征在于，所述第一隔板(70)具有与所述第二气缸(30)的排气口连通的第一隔板空腔(71)，所述第二气缸(30)还具有与所述第一隔板空腔(71)连通的外部连通口(31)，所述混合器(60)的第一进气口(61)通过所述外部连通口(31)与所述第一隔板空腔(71)连通，当所述压缩机处于部分运行模式时，所述第二气缸(30)的进气口、所述第二气缸(30)的排气口、所述第一隔板空腔(71)、所述第二气缸(30)的外部连通口(31)、所述混合器(60)、所述第一气缸(20)的进气口、所述第一气缸(20)的排气口顺次连通。
  9. 根据权利要求8所述的压缩机，其特征在于，所述第三气缸(40)具有与所述第三气缸(40)的压缩腔隔离的第一中间流道(42)，所述压缩机还包括：
    第二隔板(80)，所述第二隔板(80)设置在所述第一隔板(70)与所述第三气缸(40)之间，所述第二隔板(80)还具有使所述第三气缸(40)的所述第一中间流道(42)与所述第一隔板空腔(71)连通的第二隔板连通孔；
    第一法兰(90)，所述第一法兰(90)设置在所述第三气缸(40)的远离所述第二气缸(30)的一侧，所述第一法兰(90)具有第一法兰空腔(91)，所述第一法兰空腔(91)与所述第三气缸(40)的排气口和所述第一中间流道(42)均连通，当所述压缩机处于全运行模式时，所述第二气缸(30)的进气口、所述第二气缸(30)的排气口、所述第一隔板空腔(71)、所述第二气缸(30)的外部连通口(31)、所述混合器(60)、所述第一气缸(20)的进气口、所述第一气缸(20)的排气口顺次连通，且所述第三气缸(40)的进气口通过所述第三气缸(40)的排气口、所述第一法兰空腔(91)、所述第一中间流道(42)、所述第二隔板连通孔与所述第一隔板空腔(71)连通。
  10. 根据权利要求1至5中任一项所述的压缩机，其特征在于，所述压缩机还包括增焓部件(100)，所述增焓部件(100)与所述第一气缸(20)的进气口连通。
  11. 根据权利要求10所述的压缩机，其特征在于，所述压缩机还包括：
    第一隔板(70)，所述第一隔板(70)设置在所述第二气缸(30)与所述第一气缸(20)之间；
    第三隔板(16)，所述第三隔板(16)设置在所述第一气缸(20)与所述第一隔板(70)之间。
  12. 根据权利要求11所述的压缩机，其特征在于，所述第三隔板(16)具有第三隔板连通孔，所述第一隔板(70)具有与所述第二气缸(30)的排气口连通的第一隔板空腔(71)，且所述第一隔板空腔(71)通过所述第三隔板连通孔与第一气缸(20)的进气口连通，当所述压缩机处于部分运行模式时，所述第二气缸(30)的进气口、所述第二气缸(30)的排气口、所述第一隔板空腔(71)、所述第三隔板连通孔、所述第一气缸(20)的进气口、所述第一气缸(20)的排气口顺次连通。
  13. 根据权利要求12所述的压缩机，其特征在于，所述第三气缸(40)具有与所述第三气缸(40)的压缩腔隔离的第一中间流道(42)，所述第二气缸(30)还具有与所述第二气缸(30)的压缩腔隔离的第二中间流道(32)，所述第二中间流道(32)与所述第一隔板空腔(71)连通，所述压缩机还包括：
    第二隔板(80)，所述第二隔板(80)设置在所述第二气缸(30)与所述第三气缸(40)之间，所述第二隔板(80)还具有使所述第三气缸(40)的所述第一中间流道(42)与所述第二气缸(30)的第二中间流道(32)连通的第二隔板连通孔；
    第一法兰(90)，所述第一法兰(90)设置在所述第三气缸(40)的远离所述第二气缸(30)的一侧，所述第一法兰(90)具有第一法兰空腔(91)，所述第一法兰空腔(91)与所述第三气缸(40)的排气口和所述第一中间流道(42)均连通，当所述压缩机处于全运行模式时，所述第二气缸(30)的进气口、所述第二气缸(30)的排气口、所述第一隔板空腔(71)、所述第一气缸(20)的进气口、所述第一气缸(20)的排气口顺次连通，且所述第三气缸(40)的进气口通过所述第三气缸(40)的排气口、所述第一法兰空腔(91)、所述第一中间流道(42)、所述第二隔板连通孔与所述第二中间流道(32)与所述第一隔板空腔(71)连通。
  14. 一种换热系统，包括压缩机，其特征在于，所述压缩机是权利要求1至13中任一项所述的压缩机。
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US20180231000A1 (en) 2018-08-16
CN106704189A (zh) 2017-05-24
EP3336359B1 (en) 2023-07-19
KR20180019187A (ko) 2018-02-23
JP6595700B2 (ja) 2019-10-23

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