WO2020029804A1 - 冷媒净化系统以及包含该冷媒净化系统的换热系统 - Google Patents

冷媒净化系统以及包含该冷媒净化系统的换热系统 Download PDF

Info

Publication number
WO2020029804A1
WO2020029804A1 PCT/CN2019/097726 CN2019097726W WO2020029804A1 WO 2020029804 A1 WO2020029804 A1 WO 2020029804A1 CN 2019097726 W CN2019097726 W CN 2019097726W WO 2020029804 A1 WO2020029804 A1 WO 2020029804A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
gas
purification system
cooling
compressor
Prior art date
Application number
PCT/CN2019/097726
Other languages
English (en)
French (fr)
Inventor
张宏胜
陈云
王达
吴晶晶
Original Assignee
麦克维尔空调制冷(武汉)有限公司
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 麦克维尔空调制冷(武汉)有限公司 filed Critical 麦克维尔空调制冷(武汉)有限公司
Publication of WO2020029804A1 publication Critical patent/WO2020029804A1/zh

Links

Images

Classifications

    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/04—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for withdrawing non-condensible gases
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/04—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for withdrawing non-condensible gases
    • F25B43/043—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for withdrawing non-condensible gases for compression type systems

Definitions

  • the present application relates to the technical field of air conditioning equipment, and in particular, to a refrigerant purification system and a heat exchange system including the refrigerant purification system.
  • a low-temperature environmentally friendly refrigerant such as R1233zd
  • the low-pressure section of the compressor is in a negative pressure state during operation, and non-condensable gases such as outside air easily penetrate the system.
  • non-condensable gas enters the condenser, it will accumulate on the top of the condenser, the condensation effect of the refrigerant in the condenser will decrease, the condensation pressure of the condenser will increase, and the efficiency and cooling capacity of the chiller will decrease. Therefore, a purification device is required to separate the non-condensable gas in the refrigeration system from the system.
  • the existing purification device uses the principle of low-temperature condensation.
  • the second refrigerant is used in the cooler to form a low-temperature environment.
  • the mixed gas of the first refrigerant and the non-condensable gas enters the low-temperature environment of the cooler.
  • the first refrigerant continuously condenses into a liquid.
  • the liquid accumulates to the bottom of the cooler by gravity, and returns to the system from the bottom when the liquid accumulates to a certain amount; the non-condensable gas accumulates to the top of the cooler, and when the non-condensable gas accumulates to a certain extent, it is discharged by a vacuum pump.
  • the inventor of the present application found that the existing cooling separator adopts the first-stage condensation separation method, and the second refrigerant used for refrigeration in the purification device directly returns to the compressor suction port after heat exchange.
  • the content of non-condensable gas in the non-condensable gas is high, the content of the first refrigerant gas in the cooler is low, and the second refrigerant used for refrigeration in the cooler cannot be completely gasified, so it returns to the compressor
  • the gas in the cooler needs to be evacuated, so that there will be more first refrigerant The form of gas is extracted from the heat exchange system, causing a large loss of the first refrigerant.
  • the present application provides a refrigerant purification system and a heat exchange system including the refrigerant purification system.
  • the mixed gas of the refrigerant and the non-condensable gas is subjected to two or more stages of condensation and separation, and the temperature of the condensation and separation of the latter stage is higher than that of the former stage.
  • the temperature of the condensation and separation is low, so that the efficiency of liquefaction of the refrigerant can be greatly improved, thereby improving the separation efficiency of the refrigerant and the non-condensable gas.
  • a refrigerant purification system including: a gas cooling separator that uses a second refrigerant to condense a liquid first refrigerant from a mixed gas; and a refrigerant supply device for The gas-cooled separator provides the second refrigerant, wherein the gas-cooled separator has: a mixed gas inlet for inputting the mixed gas; and a gas outlet for exhausting the gas-cooled separator.
  • a condensed liquid outlet for discharging the liquid first refrigerant in the gas-cooled separator; and at least two cooling chambers, the at least two cooling chambers are at the mixed gas inlet and the The gas outlets communicate in sequence, and the mixed gas flows through the at least two cooling chambers in sequence from the mixed gas inlet to the gas outlet, and each cooling chamber has a condensation evaporation tube, and the condensation evaporation tube
  • the second refrigerant flows through the medium to condense the gas in the cooling cavity.
  • Each condensation evaporation tube is connected to an expansion valve, and the expansion valve connects the refrigerant
  • the second refrigerant supplied by the supply device to the condensation evaporation tube is throttled to different evaporation pressures, wherein the closer to the gas outlet in the cooling cavity, the second refrigerant in the condensation evaporation tube is. The lower the evaporation pressure of the refrigerant.
  • the expansion valve of the condensation evaporation tube closest to the mixed gas inlet is a thermal expansion valve
  • the expansion valve of the condensation evaporation tube closest to the gas outlet is a constant pressure expansion valve
  • the gas-cooled separator has a cylindrical casing, and a deflector is arranged between the adjacent cooling chambers, and the deflector is provided for the mixed gas to circulate And a second opening through which the liquid first refrigerant flows.
  • a connection pipe portion is provided between adjacent cooling chambers, and a radial dimension of the connection pipe portions is smaller than a radial dimension of the cooling chamber.
  • the connecting pipe part allows the mixed gas to circulate and allows the liquid first refrigerant to flow to the condensed liquid outlet.
  • the refrigerant purification system further includes:
  • the air-exhaust pump has an air-exhaust end connected to the gas outlet for extracting gas from the gas-cooled separator, wherein the air-exhaust end of the air-exhaust pump is connected to a gas recovery device through a first valve.
  • the refrigerant purification system further includes:
  • the temperature of the second refrigerant flowing out of the condensing and evaporating tube of the gas outlet is taken as the second temperature (TS2), and the controller controls the opening and closing of the first valve according to the first temperature and the second temperature .
  • the controller when the difference between the first temperature and the second temperature is less than a first threshold, controls the opening of the first valve.
  • the controller when the difference between the first temperature and the second temperature is greater than a second threshold, performs the following control: closing the first valve; The refrigerant supply device stops supplying the second refrigerant; and stops inputting the mixed gas to the gas cooling separator.
  • the refrigerant purification system further includes: a circulating gas inlet provided in the gas cooling separator for introducing a gas discharged from the gas outlet into the gas cooling The separator, wherein an air outlet of the air pump is connected to the circulating gas inlet through a second valve.
  • the refrigerant supply device includes a compressor and a condenser, and the second refrigerant output by the condenser is throttled by each expansion valve, flows into each condensation evaporation pipe, and is removed from each The second refrigerant flowing out of the condensing and evaporating tube is input to the compressor, and the compressor compresses the second refrigerant and inputs it to the condenser.
  • each of the compressor and the condenser provides at least one of the condensation evaporation tubes.
  • the second refrigerant is described.
  • the compressor is a one-stage compressor, a two-stage compressor, or a multi-stage compressor, and when the compressor is a one-stage compressor, The second refrigerant flowing out of the condensing evaporation tube is mixed by the ejector and input to the first-stage compressor.
  • a heat exchange system having the refrigerant purification system according to any one of the first to twelfth aspects of the above embodiments.
  • the beneficial effect of the present application is that the separation efficiency of the refrigerant and the non-condensable gas can be improved.
  • FIG. 1 is a schematic diagram of a heat exchange system having a refrigerant purification system according to Embodiment 1 of the present application;
  • FIG. 2 is a schematic perspective perspective view of the gas-cooled separator of Embodiment 1 of the present application;
  • FIG 3 is another schematic diagram of the gas-cooled separator of Embodiment 1 of the present application.
  • FIG. 4 is another schematic diagram of a heat exchange system having a refrigerant purification system according to Embodiment 2 of the present application;
  • FIG. 5 is another schematic diagram of a heat exchange system having a refrigerant purification system according to Embodiment 2 of the present application;
  • FIG. 6 is another schematic diagram of a heat exchange system having a refrigerant purification system according to Embodiment 2 of the present application.
  • axial direction a direction extending along the central axis of the gas-cooled separator
  • radial direction a direction extending along the central axis of the gas-cooled separator
  • radial direction a direction extending along the central axis of the gas-cooled separator
  • radial direction a direction extending along the central axis of the gas-cooled separator
  • radial direction a direction extending along the central axis of the gas-cooled separator
  • radial direction The circumferential direction around this axis
  • the circumferential direction around this axis is referred to as the "circumferential direction”.
  • the direction from the mixed gas inlet to the gas outlet is referred to as the "upward direction”
  • the direction opposite to the "upward direction” is the “downward direction”
  • the components of the refrigerant purification system are oriented in the "upward direction”.
  • One side is called “upper side”
  • the side opposite to the upper side is called “lower side”.
  • FIG. 1 is a schematic diagram of a heat exchange system having the refrigerant purification system of this embodiment.
  • the refrigerant purification system 10 of this embodiment includes a gas cooling separator 11 and a refrigerant supply device 12.
  • the gas-cooled separator 11 may use a second refrigerant to condense a liquid first refrigerant from the mixed gas entering the gas-cooled separator 11; the refrigerant supply device 12 is configured to provide the gas-cooled separator 11 with a second refrigerant.
  • the second refrigerant is provided.
  • FIG. 2 is a schematic perspective perspective view of the gas-cooled separator of this embodiment.
  • the gas-cooled separator 11 has: a mixed gas inlet 21, a gas outlet 22, a condensed liquid outlet 23, and at least two cooling chambers. 24. Condensation evaporation tube 25, and expansion valve 26.
  • the mixed gas inlet 21 is used to input the mixed gas; the gas outlet 22 is used to discharge the gas in the gas cooling separator 11; the condensed liquid outlet 23 is used to discharge the liquid first refrigerant in the gas cooled separator 11 .
  • the gas-cooled separator 11 may have at least two cooling chambers 24 that communicate between the mixed gas inlet 21 and the gas outlet 22 in sequence, and the mixed gas flows from the mixed gas inlet 21 to the gas outlet 22 In the process, the at least two cooling chambers 24 can be sequentially flowed.
  • each cooling cavity 24 has a condensation evaporation tube 25.
  • the second refrigerant can flow through the condensation evaporation tube 25, and the second refrigerant passes through the condensation evaporation tube 25 and the cooling cavity.
  • the gas in the body 24 is heat-exchanged to condense the gas in the cooling cavity 24.
  • each condensation evaporation tube 25 may be connected to an expansion valve 26.
  • Each expansion valve 26 is used to throttle the second refrigerant provided by the refrigerant supply device 12 to the condensation evaporation tube 25 to a different evaporation pressure.
  • the mixed gas may have a gaseous first refrigerant and a non-condensable gas.
  • the content of the first refrigerant gas becomes smaller and smaller, and the corresponding partial pressure becomes lower and lower. Therefore, as the mixed gas is continuously condensed, a lower temperature is required to continuously condense the first refrigerant gas into a liquid.
  • the content of the first refrigerant gas in the mixed gas is relatively large, and a large amount of cooling is required in the condensation process.
  • the second refrigerant does not need a very low evaporation temperature to condense the first refrigerant gas from the mixed gas; in the latter stage of the condensation, that is, in the cooling cavity near the gas outlet 22, the content of the first refrigerant gas is being mixed The proportion of gas in the gas becomes smaller, and the amount of cooling required in the condensation process is relatively small.
  • the second refrigerant needs a lower evaporation temperature to cause the first refrigerant gas to condense out of the mixed gas.
  • each cooling cavity 24 in the direction from the mixed gas inlet 21 to the gas outlet 22, the evaporation pressure of the second refrigerant in each cooling cavity 24 is getting lower and lower, so it can be accompanied by the gaseous first refrigerant in the mixed gas.
  • the decrease of the proportion of the cooling cavity 24 also reduces the evaporation temperature of the second refrigerant in each cooling cavity 24. Therefore, each cooling cavity 24 can effectively condense the gaseous first refrigerant in the cooling cavity 24,
  • the first refrigerant in each of the cooling chambers 24 can be liquefied with high efficiency, so the separation efficiency of the first refrigerant and the non-condensable gas is improved.
  • a gas-cooled separator having two cooling chambers is taken as an example for explanation, and these descriptions are also applicable to the case of a gas-cooled separator having three or more cooling chambers.
  • the at least two cooling chambers 24 may be, for example, 241 and 242.
  • Each of the cooling chambers 24 has condensation evaporation tubes 251 and 252, and the condensation evaporation tubes 251 and 252 are respectively connected to the expansion valve 261. Connected to 262 (not shown in Figure 2).
  • the expansion valve 261 closest to the condensation evaporation tube 251 of the mixed gas inlet 21 may be a thermal expansion valve
  • the expansion valve 262 closest to the condensation evaporation tube 252 of the gas outlet 22 may be a constant pressure expansion valve.
  • the expansion valve 261 as a thermal expansion valve can throttle the second refrigerant to have a higher evaporation pressure
  • the expansion valve 262 as a constant pressure expansion valve can throttle the second refrigerant to have a lower evaporation pressure.
  • the expansion valve closest to the condensation evaporation tube 251 of the mixed gas inlet 21 may be set as a thermal expansion valve
  • other expansion valves may be set as constant pressure expansion valves.
  • the closer to the gas outlet 22, the constant-pressure expansion valve is provided to throttle the second refrigerant to a lower evaporation pressure.
  • the gas-cooled separator 11 may have a cylindrical casing 20, and the shape of a cross section of the cylindrical casing 20 perpendicular to the axial direction may be circular, or polygonal, For example, squares and so on.
  • the deflector 27 may have a first opening 271 through which the mixed gas circulates and a second opening 272 through which the liquid first refrigerant flows, wherein the first opening 271 may be located at the radial center of the deflector 27, for example, and the second The opening 272 may be located, for example, radially outward of the air guide plate 27.
  • FIG. 3 is another schematic diagram of the gas-cooled separator of this embodiment.
  • a connection pipe portion 31 may be provided between adjacent cooling chambers 241 and 242 of the gas cooling separator 11, and a radial dimension of the connection pipe portion 31 may be smaller than a diameter of the cooling chambers 241 and 242. In the dimension, that is, the connecting pipe portion 31 is thinner than the cooling chambers 241 and 242.
  • the connection pipe portion 31 may allow a mixed gas to flow, for example, allow the mixed gas to flow from the cooling cavity 241 to the cooling cavity 242.
  • the connecting pipe portion 31 may also allow the liquid first refrigerant to flow to the condensed liquid outlet. For example, the liquid first refrigerant at the bottom of the cooling cavity 242 flows to the cooling cavity 241 through the connecting tube portion 31.
  • the cooling chambers 241 and 242 may have spherical shells 20a and 20b, and thus, in the length direction of the gas-cooled separator 11, the spherical shell and the elongated
  • the connection pipe portions 31 may be alternately provided.
  • the housings 20a and 20b may not be spherical, but may be ellipsoidal or rectangular parallelepiped.
  • the condensing and evaporating tubes 251 and 252 may be spirally coiled in the cooling chambers 241 and 242, thereby increasing the exchange of the condensing and evaporating tubes 251 and 252 with the mixed gas. Thermal area.
  • the gas-cooled separator 11 may further include a flow restrictor 28, which is located at the gas outlet 22 and is used to limit the flow of the gas flowing out of the gas outlet 22. .
  • the housing of the gas-cooled separator 11 closest to the mixed gas inlet 21 may be provided with a liquid level sensor 32 and a sight glass 33, wherein the liquid level sensor 32 The liquid level of the first liquid refrigerant in the gas cooling separator 11 can be detected, and the sight glass 33 can facilitate a user to observe the liquid level of the first liquid refrigerant in the gas cooling separator 11 from the outside.
  • the refrigerant purification system 10 may further have a circulating gas inlet 29.
  • the circulating gas inlet 29 may be provided in the gas-cooled separator 11 and is used to introduce the gas discharged from the gas outlet 22 into the gas-cooled separator 11 to condense the discharged gas again to achieve cyclic condensation of the gas.
  • the circulating gas inlet 29 may be provided at a position of the housing 20 of the gas cooling separator 11 corresponding to the bottom of the cooling cavity 242.
  • the circulating gas inlet 29 may be provided at the connection pipe portion 31 of the casing 20 of the gas-cooled separator 11.
  • the refrigerant providing device 12 of the refrigerant purification system 10 may include a compressor 121 and a condenser 122, wherein the second refrigerant output by the condenser 122 may be respectively provided by each of the expansion valves 261 and 262. After throttling, it flows into each of the condensation evaporation pipes 251 and 252; the second refrigerant flowing out of each of the condensation evaporation pipes 251 and 252 is input to the compressor 121, and the compressor 121 compresses the second refrigerant and inputs it to the condenser 122. Thereby, the circulation of the second refrigerant in the refrigerant purification system 10 is achieved by the refrigerant supply device 12 and each of the condensation evaporation tubes 25.
  • the compressor 121 may be a two-stage compressor or a multi-stage compressor, where the multi-stage compressor refers to a compressor with three or more stages.
  • the second refrigerant flowing out of the condensing and evaporating tube 252 can be input to the suction port of the compressor 121, and the second refrigerant flowing out of the condensing and evaporating tube 251 and having a certain superheat degree after sufficient heat absorption enters the make-up port of the compressor 121 .
  • the refrigerant purification system 10 may further include a gas-liquid separator 14. Among them, at least the second refrigerant flowing out of the condensation evaporation tube 252 closest to the gas outlet 22 is sent to the gas-liquid separator 14 for gas-liquid separation, and the gaseous second refrigerant separated by the gas-liquid separator 14 is sent to compression.
  • the machine 121 is, for example, sent to the suction port of the compressor 121, thereby preventing the compressor 121 from sucking liquid.
  • the gas-liquid separator 14 may be a gas-liquid separator based on the principle of gravity, or a cyclone-type gas-liquid separator based on centrifugal action, which is not limited in this embodiment.
  • the refrigerant purification system 10 may further include a suction pump 13.
  • the suction end 131 of the suction pump 13 may be connected to the gas outlet 22 of the gas-cooled separator 11, and used to extract the gas in the gas-cooled separator 11.
  • the air outlet end 132 of the air pump 13 can be connected to the gas recovery device through the first valve S1. Therefore, when the first valve S1 is opened, the gas in the gas-cooled separator 11 can be extracted by the suction pump 13 and sent to the gas recovery device.
  • the air outlet end 132 of the air suction pump 13 can be connected to the circulating gas inlet 29 through the second valve S2. Therefore, when the first valve S1 is closed and the second valve S2 is opened, the air suction pump 13 is operated to condense the gas circulation. When the first valve S1 is opened and the second valve S2 is closed, the suction pump 13 is operated, and the gas can be discharged to the gas recovery device.
  • first valve S1 and the second valve S2 may be solenoid valves.
  • the suction pump 13 may be, for example, a vacuum pump.
  • the refrigerant purification system 10 further includes a first temperature sensor TS1, a second temperature sensor TS2, and a controller (not shown).
  • the first temperature sensor TS1 can detect the temperature of the second refrigerant flowing into the condensation evaporation tube 252 closest to the gas outlet 22 as the first temperature T1.
  • the second temperature sensor TS2 can detect the temperature of the second refrigerant flowing out of the condensation evaporation tube 252 closest to the gas outlet 22 as the second temperature T2.
  • the controller can control the opening and closing of the first valve S1 according to the first temperature T1 and the second temperature T2.
  • the controller may control the first valve S1 to open, thereby discharging the gas in the gas-cooled separator 11. .
  • the outlet temperature of the gas-liquid separator 14 is a saturation temperature under the evaporation pressure.
  • TS1 is the saturation temperature of the constant pressure expansion valve under constant pressure
  • TS2 is the temperature of the second refrigerant in the condensation and evaporation tube 252 after heat exchange.
  • the difference between the two is less than
  • the first threshold value indicates that enough non-condensable gas has accumulated in the cooling cavity 242 of the gas cooling separator 11 at this time
  • the first valve S1 is opened at this time, and the second valve S2 can be closed to start The gas evacuation operation in the gas cooling separator 11 is performed.
  • the controller when the difference between the first temperature and the second temperature is greater than a second threshold, performs the following control: closing the first valve S1 and causing the refrigerant to provide The device 12 stops supplying the second refrigerant, and stops inputting the mixed gas to the gas cooling separator 11.
  • the temperature TS1 and TS2 differ greatly.
  • the controller can stop the purification process of the refrigerant purification system 10, for example : Close the exhaust solenoid valve S3, which is used by the main system to control the output of the mixed gas, so as to stop inputting the mixed gas to the gas cooling separator 11; turn off the compressor in the refrigerant supply device 12, so that the refrigerant supply device 12 stops supplying the first Two refrigerants; and, turn off the suction pump 13.
  • the purification system is stopped for a period of time, the purification system is started again to detect the non-condensable gas in the main system.
  • the mixed gas input to the mixed gas inlet 21 may come from the condenser 80 of the heat exchange system, and whether the mixed gas in the condenser 80 is controlled by the exhaust solenoid valve S3 It is discharged to the mixed gas inlet 21.
  • the liquid first refrigerant flowing out from the condensed liquid outlet 23 may be delivered to the evaporator 90 of the heat exchange system, where the condensed liquid outlet 23 may have a solenoid valve S4 for The outflow of the liquid first refrigerant is controlled.
  • the heat exchange system having the refrigerant purification system 10 may further include a liquid collector J1, a solenoid valve S5, a drying filter G1, a sight glass Y1, an electronic expander P1, a main compressor Z1, and the like. You can refer to the prior art.
  • the first refrigerant may be low-pressure environmental protection such as R1233zd, and the types of the second refrigerant and the first refrigerant may be the same or different.
  • the evaporation pressure of the second refrigerant in each cooling cavity is getting lower and lower, so it can be accompanied by the proportion of the gaseous first refrigerant in the mixed gas.
  • Lowering, and the evaporation temperature of the second refrigerant in each cooling cavity is also reduced, so each cooling cavity can effectively condense the gaseous first refrigerant in the cooling cavity, and the first refrigerant in each cooling cavity Both can be liquefied with high efficiency, so the separation efficiency of the first refrigerant and the non-condensable gas is improved.
  • FIG. 4 is another schematic diagram of a heat exchange system having the refrigerant purification system of this embodiment.
  • FIG. 4 differs from FIG. 1 in that the compressor 121 of FIG. 1 is a two-stage or multi-stage compressor, and in FIG. 4, the compressor 121 a is a one-stage compressor.
  • the refrigerant purification system may further include an ejector 400, and the second refrigerant flowing out from each condensation evaporation pipe is mixed by the ejector 400 and input to the compressor 121 a.
  • the low-pressure second refrigerant gas generated after the second refrigerant flowing out of the condensing evaporation tube 252 is separated by the gas-liquid separator 14 is condensed by the condensing evaporation tube 251, and the second refrigerant gas having a higher pressure comes out.
  • the mixed gas of the two enters the suction port of the compressor 121a.
  • the suction pressure of the suction port of the compressor 121 can be increased, the pressure ratio can be effectively reduced, and the working efficiency of the compressor can be improved.
  • FIG. 5 is another schematic diagram of a heat exchange system having the refrigerant purification system of this embodiment.
  • the compressor 121a is a one-stage compressor. 5 is different from FIG. 4 in that FIG. 4 has only one pair of compressor 121a and condenser 122, and in FIG. 5, there are two or more pairs of compressor 121a and condenser 122, for example, two pairs.
  • each of the compressor 121 a and the condenser 122 provides a second refrigerant for at least one condensation evaporation tube.
  • the compressor 121a-1 and the condenser 122-1 provide a second refrigerant for the condensation evaporation tube 251; the compressor 121a-2 and the condenser 122-2 provide a second refrigerant for the condensation evaporation tube 252.
  • an ejector may not be provided.
  • At least one one-stage compressor 121 a may be replaced with a two-stage or multi-stage compressor 121.
  • FIG. 6 is another schematic diagram of a heat exchange system having the refrigerant purification system of this embodiment.
  • each of the refrigerant purification systems may have more than two pairs of compressors and condensers.
  • at least one pair of compressors and condensers used in the refrigerant purification system may be the compressor Z1 and the condenser 80 used in the main system, that is, the refrigerant purification system may share the compressor and the condenser with the main system .
  • Embodiment 3 of the present application provides a heat exchange system.
  • the heat exchange system includes the refrigerant purification system described in Embodiment 1 or Embodiment 2.
  • the schematic diagram of the heat exchange system can be as shown in Fig. 1, Fig. 4, Fig. 5 or Fig. 6,
  • the efficiency of liquefaction of the refrigerant can be greatly improved, thereby improving the separation efficiency of the refrigerant and the non-condensable gas, and avoiding the reduction of the refrigerant. waste.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)

Abstract

提供一种冷媒净化系统（10）以及包含该冷媒净化系统（10）的换热系统。冷媒净化系统（10）包括：气体冷却分离器（11）和冷媒提供装置（12）。气体冷却分离器（11）具有：混合气体入口（21），气体出口（22），冷凝液体出口（23），至少两个冷却腔体（24）。每个冷却腔体（24）中具有冷凝蒸发管（25），冷凝蒸发管（25）中流过第二冷媒，用于对该冷却腔体（24）内的气体进行冷凝，各冷凝蒸发管（25）和膨胀阀（26）相连，膨胀阀（26）将冷媒提供装置（12）提供给冷凝蒸发管（25）的第二冷媒节流到不同的蒸发压力，其中，越靠近气体出口的冷却腔体（24）中，冷凝蒸发管（25）中的第二冷媒的蒸发压力越低。

Description

冷媒净化系统以及包含该冷媒净化系统的换热系统 技术领域
本申请涉及空调设备技术领域，尤其涉及一种冷媒净化系统以及包含该冷媒净化系统的换热系统。
背景技术
目前，对于离心机冷水机组等换热系统在采用R1233zd等低压环保制冷剂为冷媒时，压缩机在运行时低压段处于负压状态，外界的空气等不凝性气体极易渗入到系统中。当不凝性气体进入到冷凝器时会积聚到冷凝器的顶部，冷媒在冷凝器中的冷凝效果下降，冷凝器的冷凝压力升高，冷水机组的效率和制冷能力都将下降。因此，需要净化装置将制冷系统中的不凝性气体从系统中分离出来。
现有的净化装置采用的是低温冷凝的原理，冷却器中采用第二冷媒形成低温环境，第一冷媒和不凝性气体的混合气体进入到冷却器的低温环境中遇冷放热，气态的第一冷媒不断冷凝为液体。液体依靠重力积聚到冷却器的底部，当液体积聚到一定量时从底部返回到系统中；不凝性气体积聚到冷却器的顶部，当不凝性气体积聚到一定程度时依靠真空泵排出。
应该注意，上面对技术背景的介绍只是为了方便对本发明的技术方案进行清楚、完整的说明，并方便本领域技术人员的理解而阐述的。不能仅仅因为这些方案在本发明的背景技术部分进行了阐述而认为上述技术方案为本领域技术人员所公知。
发明内容
本申请的发明人发现，现有的冷却分离器采用的是一级冷凝分离的方式，净化装置中用于制冷的第二冷媒换热后直接回到压缩机吸气口。当不凝性气体中的不凝性气体含量较高时，第一冷媒气体在冷却器中含量较低，不能使冷却器中用于制冷的第二冷媒完全气化，因此，回到压缩机的第二冷媒中存在液态的第二冷媒，即，压缩机将出现吸气带液现象。为防止压缩机吸气带液，当第一冷媒气体在冷却器中的含量还处 在较高值时，就需要将冷却器中的气体排空，这样，会有较多的第一冷媒以气体的形式从换热系统中被抽出，造成第一冷媒的较大损失。
本申请提供一种冷媒净化系统以及包含该冷媒净化系统的换热系统，对冷媒和不凝性气体的混合气体进行两级以上的冷凝分离，并且，后一级冷凝分离的温度比前一级冷凝分离的温度低，因此，能够使冷媒被液化的效率大大提高，从而提高冷媒和不凝性气体的分离效率。
根据本申请实施例的第一方面，提供一种冷媒净化系统，包括：气体冷却分离器，其使用第二冷媒从混合气体中冷凝出液态的第一冷媒；以及冷媒提供装置，其用于向所述气体冷却分离器提供所述第二冷媒，其中，所述气体冷却分离器具有：混合气体入口，其用于输入所述混合气体；气体出口，其用于排出所述气体冷却分离器中的气体；冷凝液体出口，其用于将所述气体冷却分离器中液态的第一冷媒排出；以及至少两个冷却腔体，所述至少两个冷却腔体在所述混合气体入口和所述气体出口之间依次连通，所述混合气体从所述混合气体入口到所述气体出口依次流经所述至少两个冷却腔体，每个冷却腔体中具有冷凝蒸发管，所述冷凝蒸发管中流过所述第二冷媒，用于对该冷却腔体内的气体进行冷凝，各冷凝蒸发管与膨胀阀相连，所述膨胀阀将所述冷媒提供装置提供给所述冷凝蒸发管的所述第二冷媒节流到不同的蒸发压力，其中，越靠近所述气体出口的所述冷却腔体中，所述冷凝蒸发管中的所述第二冷媒的蒸发压力越低。
根据本申请实施例的第二方面，其中，最靠近所述混合气体入口的冷凝蒸发管的膨胀阀是热力膨胀阀，最靠近所述气体出口的冷凝蒸发管的膨胀阀是恒压膨胀阀。
根据本申请实施例的第三方面，其中，所述气体冷却分离器具有筒状的壳体，相邻的所述冷却腔体之间具有导流板，所述导流板具有供混合气体流通的第一开口和供液态的第一冷媒流过的第二开口。
根据本申请实施例的第四方面，其中，相邻的所述冷却腔体之间设置有连接管部，所述连接管部的径向尺寸小于所述冷却腔体的径向尺寸，所述连接管部供混合气体流通，并供液态的所述第一冷媒流向所述冷凝液体出口。
根据本申请实施例的第五方面，其中，所述冷媒净化系统还具有：
抽气泵，其抽气端连接于所述气体出口，用于将所述气体冷却分离器中的气体抽出，其中，所述抽气泵的出气端通过第一阀门与气体回收装置连接。
根据本申请实施例的第六方面，其中，所述冷媒净化系统还具有：
第一温度传感器，其用于检测流入最靠近所述气体出口的所述冷凝蒸发管的第二冷媒的温度作为第一温度(TS1)，第二温度传感器，其用于检测从最靠近所述气体出口的所述冷凝蒸发管流出的第二冷媒的温度作为第二温度(TS2)，控制器，其根据所述第一温度和所述第二温度，控制所述第一阀门的打开和关闭。
根据本申请实施例的第七方面，其中，当所述第一温度和所述第二温度的差值小于第一阈值时，所述控制器控制所述第一阀门的打开。
根据本申请实施例的第八方面，其中，当所述第一温度和所述第二温度的差值大于第二阈值时，所述控制器进行如下控制：使所述第一阀门关闭；使所述冷媒提供装置停止提供所述第二冷媒；以及停止向所述气体冷却分离器输入所述混合气体。
根据本申请实施例的第九方面，其中，所述冷媒净化系统还具有：循环气体入口，其设置于所述气体冷却分离器，用于将从所述气体出口排出的气体导入所述气体冷却分离器，其中，所述抽气泵的出气端通过第二阀门与所述循环气体入口连接。
根据本申请实施例的第十方面，其中，所述冷媒提供装置包括压缩机和冷凝器，所述冷凝器输出的第二冷媒被各膨胀阀分别节流后，流入各冷凝蒸发管，从各冷凝蒸发管流出的第二冷媒被输入所述压缩机，压缩机对第二冷媒压缩后输入到冷凝器。
根据本申请实施例的第十一方面，其中，所述压缩机为至少一个，所述冷凝器为至少一个，每个所述压缩机和所述冷凝器为至少一个所述冷凝蒸发管提供所述第二冷媒。
根据本申请实施例的第十二方面，其中，所述压缩机为一级压缩机，二级压缩机或多级压缩机，其中，在所述压缩机为一个一级压缩机时，从各冷凝蒸发管流出的第二冷媒被引射器混合后输入到所述一级压缩机。
根据本申请实施例的第十三方面，提供一种换热系统，其具有如上述实施例第一方面至第十二方面中任一方面所述的冷媒净化系统。
本申请的有益效果在于：能够提高冷媒和不凝性气体的分离效率。
参照后文的说明和附图，详细公开了本申请的特定实施方式，指明了本申请的原理可以被采用的方式。应该理解，本申请的实施方式在范围上并不因而受到限制。在所附权利要求的精神和条款的范围内，本申请的实施方式包括许多改变、修改和等同。
附图说明
所包括的附图用来提供对本申请实施例的进一步的理解，其构成了说明书的一部分，用于例示本申请的实施方式，并与文字描述一起来阐释本申请的原理。显而易见地，下面描述中的附图仅仅是本申请的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图获得其他的附图。在附图中：
图1是具有本申请实施例1的冷媒净化系统的换热系统的一个示意图；
图2是本申请实施例1的气体冷却分离器的一个立体透视示意图；
图3是本申请实施例1的气体冷却分离器的另一个示意图；
图4是具有本申请实施例2的冷媒净化系统的换热系统的另一个示意图；
图5是具有本申请实施例2的冷媒净化系统的换热系统的又一个示意图；
图6是具有本申请实施例2的冷媒净化系统的换热系统的再一个示意图。
具体实施方式
参照附图，通过下面的说明书，本申请的前述以及其它特征将变得明显。在说明书和附图中，具体公开了本申请的特定实施方式，其表明了其中可以采用本申请的原则的部分实施方式，应了解的是，本申请不限于所描述的实施方式，相反，本申请包括落入所附权利要求的范围内的全部修改、变型以及等同物。
在本申请的下述说明中，为了说明的方便，将以沿气体冷却分离器的中心轴延伸的方向称为“轴向”，将以该轴为中心的半径方向称为“径向”，将以该轴为中心的圆周方向称为“周向”。在该轴向，将从混合气体入口指向气体出口的方向称为“上方向”，与“上方向”相反的方向为“下方向”，并且，冷媒净化系统各部件的朝向“上方向”的一侧称为“上侧”，与上侧相反的一侧称为“下侧”。需要说明的是，上述对于上方向、下方向、上侧以及下侧的定义只是为了说明的方便，并不限定该气体冷却分离器在使用时的朝向。
实施例1
本申请实施例提供了一种冷媒净化系统，图1是具有本实施例的冷媒净化系统的换热系统的一个示意图。
如图1所示，本实施例的冷媒净化系统10包括：气体冷却分离器11和冷媒提供 装置12。
在本实施例中，气体冷却分离器11可以使用第二冷媒从进入到该气体冷却分离器11中的混合气体中冷凝出液态的第一冷媒；冷媒提供装置12用于向气体冷却分离器11提供该第二冷媒。
图2是本实施例的气体冷却分离器的一个立体透视示意图，如图2所示，气体冷却分离器11具有：混合气体入口21，气体出口22，冷凝液体出口23，至少两个冷却腔体24，冷凝蒸发管25，以及膨胀阀26。
在本实施例中，混合气体入口21用于输入混合气体；气体出口22用于排出气体冷却分离器11中的气体；冷凝液体出口23用于将气体冷却分离器11中液态的第一冷媒排出。
该气体冷却分离器11可以具有至少两个冷却腔体24，该至少两个冷却腔体在混合气体入口21和气体出口22之间依次连通，混合气体在从混合气体入口21到气体出口22流动的过程中，可以依次流经该至少两个冷却腔体24。
如图2所示，在每个冷却腔体24中，都具有冷凝蒸发管25，该冷凝蒸发管25中可以流过该第二冷媒，该第二冷媒通过该冷凝蒸发管25与该冷却腔体24内的气体进行热交换，从而对该冷却腔体24内的气体进行冷凝。
如图1所示，各冷凝蒸发管25可以与膨胀阀26相连，各膨胀阀26用于将冷媒提供装置12提供给冷凝蒸发管25的第二冷媒节流到不同的蒸发压力，其中，越靠近气体出口22的冷却腔体24中，冷凝蒸发管中25的第二冷媒的蒸发压力越低，即，越靠近气体出口22的冷却腔体24中，冷凝蒸发管中25的第二冷媒的蒸发温度越低。
在本实施例中，该混合气体中可以具有气态的第一冷媒和不凝性气体。在该混合气体在气体冷却分离器11中被逐渐冷凝的过程中，第一冷媒气体的含量越来越少，其对应的分压力也越来越低。因此，随着混合气体的不断冷凝，需要更低的温度使第一冷媒气体不断冷凝为液体。
在本实施例中，在冷凝的前段，即，在靠近混合气体入口21的冷却腔体中，第一冷媒气体的含量在混合气体中的占比较大，冷凝过程需要较大的冷量，第二冷媒不需要很低的蒸发温度就能使第一冷媒气体从混合气体中冷凝出来；在冷凝的后段，即，在靠近气体出口22的冷却腔体中，第一冷媒气体的含量在混合气体中的占比变小，冷凝过程需要的冷量相对较少，但是，第二冷媒需要较低的蒸发温度才能使制第一冷 媒气体从混合气体中冷凝出来。
在本实施例中，在从混合气体入口21到气体出口22的方向上，各冷却腔体24中第二冷媒的蒸发压力越来越低，因此，能够伴随着混合气体中气态的第一冷媒的占比的降低，而使各冷却腔体24中第二冷媒的蒸发温度也降低，所以，各冷却腔体24都能够有效地对该冷却腔体24内的气态的第一冷媒进行冷凝，各冷却腔体24内的第一冷媒都能以较高的效率被液化，因而第一冷媒和不凝性气体的分离效率被提高。
在本实施例下面的描述中，将以具有两个冷却腔体的气体冷却分离器为例进行说明，这些说明同样适用于具有三个以上冷却腔体的气体冷却分离器的情况。
如图1和图2所示，至少两个冷却腔体24例如可以是241和242，各冷却腔体24中分别具有冷凝蒸发管251和252，各冷凝蒸发管251、252分别与膨胀阀261和262(图2未示出)相连。
在本实施例中，最靠近混合气体入口21的冷凝蒸发管251的膨胀阀261可以是热力膨胀阀，最靠近气体出口22的冷凝蒸发管252的膨胀阀262可以是恒压膨胀阀。其中，作为热力膨胀阀的膨胀阀261能够将第二冷媒节流到具有较高的蒸发压力，作为恒压膨胀阀的膨胀阀262能够将第二冷媒节流到具有较低的蒸发压力。此外，在具有三个以上冷却腔体的实施方式中，可以将最靠近混合气体入口21的冷凝蒸发管251的膨胀阀设置为热力膨胀阀，而将其它的膨胀阀设置为恒压膨胀阀，并且，越靠近气体出口22，恒压膨胀阀被设置为将第二冷媒节流到越低的蒸发压力。
在本实施例中，如图2所示，气体冷却分离器11可以具有筒状的壳体20，该筒状的壳体20的与轴向垂直的截面的形状可以是圆形，或多边形，例如，正方形等。
如图2所示，相邻的冷却腔体241和242之间可以具有导流板27。导流板27可以具有供混合气体流通的第一开口271和供液态的第一冷媒流过的第二开口272，其中，第一开口271例如可以位于导流板27的径向中心，第二开口272例如可以位于导流板27的径向外侧。
此外，在本实施例中，气体冷却分离器11也可以具有其它的形状。图3是本实施例的气体冷却分离器的另一个示意图。
如图3所示，气体冷却分离器11的相邻的冷却腔体241和242之间可以设置有连接管部31，该连接管部31的径向尺寸可以小于冷却腔体241和242的径向尺寸，即，该连接管部31比冷却腔体241和242更细。该连接管部31可以供混合气体流通， 例如，供混合气体从冷却腔体241流动到冷却腔体242。该连接管部31还可以供液态的第一冷媒流向冷凝液体出口，例如，冷却腔体242底部的液态的第一冷媒通过连接管部31流动到冷却腔体241。
在本实施例中，如图3所示，冷却腔体241和242可以具有球形的壳体20a和20b，由此，在气体冷却分离器11的长度方向上，球形的壳体和细长的连接管部31可以被交替设置。此外，壳体20a和20b也可以不是球形，而是椭球型或长方体等。
在本实施例中，如图2和图3所示，冷凝蒸发管251、252可以呈螺旋状盘绕在冷却腔体241、242中，由此，增加冷凝蒸发管251、252与混合气体的换热面积。
此外，在本实施例中，图2、图3所示，气体冷却分离器11还可以具有限流器28，限流器28位于气体出口22，用于限制从气体出口22流出的气体的流量。
此外，在本实施例中，如图3所示，气体冷却分离器11的最靠近混合气体入口21的壳体中，可以设置有液位传感器32和视液镜33，其中，液位传感器32能够检测气体冷却分离器11中液态的第一冷媒的液位，视液镜33能够便于用户从外侧观察气体冷却分离器11中液态的第一冷媒的液位。
在本实施例中，如图1、图2和图3所示，冷媒净化系统10还可以具有循环气体入口29。该循环气体入口29可以设置于气体冷却分离器11，用于将从气体出口22排出的气体导入气体冷却分离器11，从而对排出的气体再次进行冷凝，实现对气体的循环冷凝。在一个实施方式中，如图2所示，循环气体入口29可以被设置于气体冷却分离器11的壳体20的与冷却腔体242的底部对应的位置。在另一个实施方式中，如图3所示，循环气体入口29可以被设置于气体冷却分离器11的壳体20的连接管部31。
下面结合图1对冷媒净化系统的其它组成部分进行说明。
在本实施例中，如图1所示，冷媒净化系统10的冷媒提供装置12可以包括压缩机121和冷凝器122，其中：冷凝器122输出的第二冷媒可以被各膨胀阀261、262分别节流后，流入各冷凝蒸发管251、252；从各冷凝蒸发管251、252流出的第二冷媒被输入到压缩机121，压缩机121对第二冷媒压缩后输入到冷凝器122。由此，通过冷媒提供装置12和各冷凝蒸发管25，实现了第二冷媒在冷媒净化系统10中的循环。
在本实施例中，压缩机121可以是二级压缩机或多级压缩机，其中，多级压缩机 是指三级以上的压缩机。冷凝蒸发管252流出的第二冷媒可以被输入到压缩机121的吸气口，冷凝蒸发管251流出的经过充分吸热后带有一定过热度的气态的第二冷媒进入压缩机121的补气口。
如图1所示，冷媒净化系统10还可以具有气液分离器14。其中，至少最靠近气体出口22的冷凝蒸发管252流出的第二冷媒被送入该气液分离器14进行气液分离，该气液分离器14分离出的气态的第二冷媒被送入压缩机121，例如，被送入压缩机121的吸气口，由此，防止压缩机121吸气带液。
在本实施例中，气液分离器14可以是基于重力原理的气液分离器，也可以是基于离心作用的旋风式气液分离器，本实施例对此并不限制。
如图1所示，冷媒净化系统10还可以具有抽气泵13。抽气泵13的抽气端131可以连接于气体冷却分离器11的气体出口22，用于将气体冷却分离器11中的气体抽出。抽气泵13的出气端132可以通过第一阀门S1与气体回收装置连接。由此，在第一阀门S1打开的情况下，可以通过抽气泵13将气体冷却分离器11中的气体抽出，并输送到该气体回收装置。
此外，抽气泵13的出气端132可以通过第二阀门S2与循环气体入口29连接，由此，在第一阀门S1关闭，第二阀门S2打开时，抽气泵13工作，可以使气体循环冷凝。在第一阀门S1打开，第二阀门S2关闭时，抽气泵13工作，可以使气体排向该气体回收装置。
在本实施例中，第一阀门S1和第二阀门S2可以是电磁阀。抽气泵13例如可以是真空泵等。
如图1所示，冷媒净化系统10还具有第一温度传感器TS1，第二温度传感器TS2，以及控制器(未示出)。
其中，第一温度传感器TS1可以检测流入最靠近气体出口22的冷凝蒸发管252的第二冷媒的温度作为第一温度T1。
第二温度传感器TS2可以检测从最靠近气体出口22的冷凝蒸发管252流出的第二冷媒的温度作为第二温度T2。
在本实施例中，该控制器可以根据第一温度T1和第二温度T2，控制第一阀门S1的打开和关闭。
在一个实施方式中，当所述第一温度和所述第二温度的差值小于第一阈值时，该 控制器可以控制该第一阀门S1打开，从而将气体冷却分离器11中的气体排出。
例如，当混合气体在气体冷却分离器11的最靠近气体出口22的冷却腔体242中积聚量增多时，冷凝蒸发管252的第二冷媒吸收的热量逐渐减少，回气会出现吸热不足而带液的情况。当第二冷媒吸气带液时，气液分离器14出口温度为蒸发压力下的饱和温度。如图1所示，TS1为恒压膨胀阀恒定压力下的饱和温度，TS2为冷凝蒸发管252中的第二冷媒换热后的温度，当两者温度很接近，例如二者的差值小于第一阈值时，说明此时气体冷却分离器11的冷却腔体242内已经积聚了足够多的不凝性气体，此时，第一阀门S1开启，并且，可以将第二阀门S2关闭，开始进行气体冷却分离器11中的气体排空的工作。
在另一个实施方式中，当所述第一温度和所述第二温度的差值大于第二阈值时，所述控制器进行如下控制：使所述第一阀门S1关闭，使所述冷媒提供装置12停止提供所述第二冷媒，停止向所述气体冷却分离器11输入所述混合气体。
例如，当混合气体中的不凝性气体极少时，气态的第一冷媒的量较多，冷却腔体242中第二冷媒吸收的热量较多，第二冷媒带有一定的过热度，此时，温度TS1和TS2相差较大。当温度TS1和TS2的差值大于第二阈值，并且持续一段预定的时间的情况下，可以认为混合气体中不含有不凝性气体，因此，控制器可以停止冷媒净化系统10的净化过程，例如：使主系统用于控制混合气体输出的排气电磁阀S3关闭，从而停止向气体冷却分离器11输入混合气体；关闭冷媒提供装置12中的压缩机，从而使冷媒提供装置12停止提供该第二冷媒；以及，关闭抽气泵13。此外，当净化系统停机一段时间后，再次启动净化系统对主系统含有不凝性气体的情况进行检测。
在本实施例中，如图1所示，输入到混合气体入口21的混合气体可以来自于换热系统的冷凝器80，并且，通过排气电磁阀S3控制是否将冷凝器80中的混合气体排出到混合气体入口21。
在本实施例中，如图1所示，从冷凝液体出口23流出的液态的第一冷媒可以被输送到换热系统的蒸发器90，其中，冷凝液体出口23可以具有电磁阀S4，用于控制液态的第一冷媒的流出。
此外，具有该冷媒净化系统10的换热系统还可以具有集液器J1、电磁阀S5、干燥过滤器G1、视液镜Y1、电子膨胀器P1、主压缩机Z1等，关于这些部件的说明，可以参考现有技术。
在本实施例中，第一冷媒可以是R1233zd等低压环保，第二冷媒与第一冷媒的种类可以相同，也可以不同。
根据本实施例，在从混合气体入口到气体出口的方向上，各冷却腔体中第二冷媒的蒸发压力越来越低，因此，能够伴随着混合气体中气态的第一冷媒的占比的降低，而使各冷却腔体中第二冷媒的蒸发温度也降低，所以，各冷却腔体都能够有效地对该冷却腔体内的气态的第一冷媒进行冷凝，各冷却腔体内的第一冷媒都能以较高的效率被液化，因而第一冷媒和不凝性气体的分离效率被提高。
实施例2
图4是具有本实施例的冷媒净化系统的换热系统的另一个示意图。
图4与图1的区别在于，图1的压缩机121是二级或多级压缩机，而在图4中，压缩机121a是一级压缩机。
在图4中，冷媒净化系统还可以具有引射器400，从各冷凝蒸发管流出的第二冷媒被引射器400混合后输入到压缩机121a。
例如，在引射器400中，冷凝蒸发管252流出的第二冷媒经气液分离器14分离后生成的低压第二冷媒气体被冷凝蒸发管251冷凝后出来的较高压力的第二冷媒气体引射后两者的混合气体进入到压缩机121a的吸气口。通过引射作用可提高压缩机121吸气口的吸气压力，有效降低压比，提高压缩机的工作效率。
图5是具有本实施例的冷媒净化系统的换热系统的又一个示意图。
在图5和图4中，压缩机121a都是一级压缩机。图5与图4的区别在于，图4仅具有一对压缩机121a和冷凝器122，而在图5中，具有两对以上压缩机121a和冷凝器122，例如两对。
如图5所示，每个压缩机121a和冷凝器122为至少一个冷凝蒸发管提供第二冷媒。例如，压缩机121a-1和冷凝器122-1为冷凝蒸发管251提供第二冷媒；压缩机121a-2和冷凝器122-2为冷凝蒸发管252提供第二冷媒。
此外，如图5所示的冷媒净化系统中，可以不设置引射器。
此外，在图5中，也可以将至少一个一级压缩机121a替换为二级或多级压缩机121。
图6是具有本实施例的冷媒净化系统的换热系统的再一个示意图。
在图6和图5中，冷媒净化系统都可以具有两对以上压缩机和冷凝器。而在图6中，冷媒净化系统所使用的至少一对压缩机和冷凝器可以是主系统所使用的压缩机Z1和冷凝器80，即，冷媒净化系统可以与主系统共用压缩机和冷凝器。
实施例3
本申请实施例3提供一种换热系统，该换热系统包括实施例1或实施例2所述的冷媒净化系统。关于该换热系统的示意图，可以如图1、图4、图5或图6所示，
在本实施例中，由于采用了实施例1或实施例2的冷媒净化系统，能够使冷媒被液化的效率大大提高，从而提高冷媒和不凝性气体的分离效率，并且，能避减少冷媒的浪费。
以上结合具体的实施方式对本申请进行了描述，但本领域技术人员应该清楚，这些描述都是示例性的，并不是对本申请保护范围的限制。本领域技术人员可以根据本申请的精神和原理对本申请做出各种变型和修改，这些变型和修改也在本申请的范围内。

Claims (13)

  1. 一种冷媒净化系统，包括：
    气体冷却分离器，其使用第二冷媒从混合气体中冷凝出液态的第一冷媒；以及
    冷媒提供装置，其用于向所述气体冷却分离器提供所述第二冷媒，
    其中，所述气体冷却分离器具有：
    混合气体入口，其用于输入所述混合气体；
    气体出口，其用于排出所述气体冷却分离器中的气体；
    冷凝液体出口，其用于将所述气体冷却分离器中液态的第一冷媒排出；以及
    至少两个冷却腔体，所述至少两个冷却腔体在所述混合气体入口和所述气体出口之间依次连通，所述混合气体从所述混合气体入口到所述气体出口依次流经所述至少两个冷却腔体，
    每个冷却腔体中具有冷凝蒸发管，所述冷凝蒸发管中流过所述第二冷媒，用于对该冷却腔体内的气体进行冷凝，
    各冷凝蒸发管和膨胀阀相连，所述膨胀阀将所述冷媒提供装置提供给所述冷凝蒸发管的所述第二冷媒节流到不同的蒸发压力，
    其中，越靠近所述气体出口的所述冷却腔体中，所述冷凝蒸发管中的所述第二冷媒的蒸发压力越低。
  2. 如权利要求1所述的冷媒净化系统，其中，
    最靠近所述混合气体入口的冷凝蒸发管的膨胀阀是热力膨胀阀，
    最靠近所述气体出口的冷凝蒸发管的膨胀阀是恒压膨胀阀。
  3. 如权利要求1所述的冷媒净化系统，其中，
    所述气体冷却分离器具有筒状的壳体，
    相邻的所述冷却腔体之间具有导流板，
    所述导流板具有供混合气体流通的第一开口和供液态的第一冷媒流过的第二开口。
  4. 如权利要求1所述的冷媒净化系统，其中，
    相邻的所述冷却腔体之间设置有连接管部，
    所述连接管部的径向尺寸小于所述冷却腔体的径向尺寸，
    所述连接管部供混合气体流通，并供液态的所述第一冷媒流向所述冷凝液体出口。
  5. 如权利要求1所述的冷媒净化系统，其中，所述冷媒净化系统还具有：
    抽气泵，其抽气端连接于所述气体出口，用于将所述气体冷却分离器中的气体抽出，
    其中，所述抽气泵的出气端通过第一阀门与气体回收装置连接。
  6. 如权利要求5所述的冷媒净化系统，其中，所述冷媒净化系统还具有：
    第一温度传感器，其用于检测流入最靠近所述气体出口的所述冷凝蒸发管的第二冷媒的温度作为第一温度，
    第二温度传感器，其用于检测从最靠近所述气体出口的所述冷凝蒸发管流出的第二冷媒的温度作为第二温度，
    控制器，其根据所述第一温度和所述第二温度，控制所述第一阀门的打开和关闭。
  7. 如权利要求6所述的冷媒净化系统，其中，
    当所述第一温度和所述第二温度的差值小于第一阈值时，
    所述控制器控制所述第一阀门的打开。
  8. 如权利要求6所述的冷媒净化系统，其中，
    当所述第一温度和所述第二温度的差值大于第二阈值时，
    所述控制器进行如下控制：
    使所述第一阀门关闭；
    使所述冷媒提供装置停止提供所述第二冷媒；以及
    停止向所述气体冷却分离器输入所述混合气体。
  9. 如权利要求5所述的冷媒净化系统，其中，所述冷媒净化系统还具有：
    循环气体入口，其设置于所述气体冷却分离器，用于将从所述气体出口排出的气体导入所述气体冷却分离器，
    其中，
    所述抽气泵的出气端通过第二阀门与所述循环气体入口连接。
  10. 如权利要求1所述的冷媒净化系统，其中，
    所述冷媒提供装置包括压缩机和冷凝器，
    所述冷凝器输出的第二冷媒被各膨胀阀分别节流后，流入各冷凝蒸发管，
    从各冷凝蒸发管流出的第二冷媒被输入所述压缩机，所述压缩机对第二冷媒压缩后输入到所述冷凝器。
  11. 如权利要求10所述的冷媒净化系统，其中，
    所述压缩机为至少一个，所述冷凝器为至少一个，每个所述压缩机和所述冷凝器为至少一个所述冷凝蒸发管提供所述第二冷媒。
  12. 如权利要求11所述的冷媒净化系统，其中，
    所述压缩机为一级压缩机，二级压缩机或多级压缩机，
    其中，
    在所述压缩机为一个一级压缩机时，从各冷凝蒸发管流出的第二冷媒被引射器混合后输入到所述一级压缩机。
  13. 一种换热系统，其具有如权利要求1-12中任意一项所述的冷媒净化系统。
PCT/CN2019/097726 2018-08-09 2019-07-25 冷媒净化系统以及包含该冷媒净化系统的换热系统 WO2020029804A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201810902634.4 2018-08-09
CN201810902634.4A CN110822774A (zh) 2018-08-09 2018-08-09 冷媒净化系统以及包含该冷媒净化系统的换热系统

Publications (1)

Publication Number Publication Date
WO2020029804A1 true WO2020029804A1 (zh) 2020-02-13

Family

ID=69414497

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2019/097726 WO2020029804A1 (zh) 2018-08-09 2019-07-25 冷媒净化系统以及包含该冷媒净化系统的换热系统

Country Status (2)

Country Link
CN (1) CN110822774A (zh)
WO (1) WO2020029804A1 (zh)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114459164A (zh) * 2022-01-26 2022-05-10 上海哲雪冷链设备有限公司 一种冷冻冷藏用电压缩冷凝机组
CN114832571A (zh) * 2022-04-02 2022-08-02 西安交通大学 一种资源气体回收与脱除系统
CN115096012A (zh) * 2022-06-28 2022-09-23 鹏鸟科技(山东)有限公司 一种带气液中继器的制冷系统
CN115501637A (zh) * 2022-10-21 2022-12-23 深圳市德捷力低温技术有限公司 Voc冷凝回收系统及对应的voc冷凝回收方法

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2327081A (en) * 1941-11-06 1943-08-17 Roscoe E Walters Air purger
CN104748459A (zh) * 2013-12-30 2015-07-01 上海宝丰机械制造有限公司 用于制冷系统的空气分离器
CN105509378A (zh) * 2015-12-11 2016-04-20 南通航运职业技术学院 一种自动放空气器及使用方法
CN106322805A (zh) * 2015-07-10 2017-01-11 开利公司 制冷系统及其净化方法
CN107869882A (zh) * 2016-09-23 2018-04-03 潜江传家电子商务有限公司 一种用于制冷的空气分离器
CN207570168U (zh) * 2018-02-02 2018-07-03 南京万佛莱精密机械有限公司 用于分离制冷剂中不凝性气体的系统
CN208751086U (zh) * 2018-08-09 2019-04-16 麦克维尔空调制冷(武汉)有限公司 冷媒净化系统以及包含该冷媒净化系统的换热系统

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2327081A (en) * 1941-11-06 1943-08-17 Roscoe E Walters Air purger
CN104748459A (zh) * 2013-12-30 2015-07-01 上海宝丰机械制造有限公司 用于制冷系统的空气分离器
CN106322805A (zh) * 2015-07-10 2017-01-11 开利公司 制冷系统及其净化方法
CN105509378A (zh) * 2015-12-11 2016-04-20 南通航运职业技术学院 一种自动放空气器及使用方法
CN107869882A (zh) * 2016-09-23 2018-04-03 潜江传家电子商务有限公司 一种用于制冷的空气分离器
CN207570168U (zh) * 2018-02-02 2018-07-03 南京万佛莱精密机械有限公司 用于分离制冷剂中不凝性气体的系统
CN208751086U (zh) * 2018-08-09 2019-04-16 麦克维尔空调制冷(武汉)有限公司 冷媒净化系统以及包含该冷媒净化系统的换热系统

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114459164A (zh) * 2022-01-26 2022-05-10 上海哲雪冷链设备有限公司 一种冷冻冷藏用电压缩冷凝机组
CN114459164B (zh) * 2022-01-26 2024-02-09 上海哲雪冷链设备有限公司 一种冷冻冷藏用电压缩冷凝机组
CN114832571A (zh) * 2022-04-02 2022-08-02 西安交通大学 一种资源气体回收与脱除系统
CN115096012A (zh) * 2022-06-28 2022-09-23 鹏鸟科技(山东)有限公司 一种带气液中继器的制冷系统
CN115501637A (zh) * 2022-10-21 2022-12-23 深圳市德捷力低温技术有限公司 Voc冷凝回收系统及对应的voc冷凝回收方法

Also Published As

Publication number Publication date
CN110822774A (zh) 2020-02-21

Similar Documents

Publication Publication Date Title
WO2020029804A1 (zh) 冷媒净化系统以及包含该冷媒净化系统的换热系统
US7559212B2 (en) Refrigerant pressurization system with a two-phase condensing ejector
CN108344214B (zh) 排气装置、制冷空调系统和不凝性气体的排气方法
WO2018035268A1 (en) Gas discharge apparatus, refrigerating and air-conditioning unit, and method of discharging non-condensable gas
US20130186128A1 (en) Chiller
CN107192153B (zh) 带喷射器的双级蒸发制冷系统
US20080302129A1 (en) Refrigeration system for transcritical operation with economizer and low-pressure receiver
KR20020008807A (ko) 극저온 냉동시스템
WO2021120689A1 (zh) 空调机组
CN102230681B (zh) 一种蒸发器出口零过热度运行的制冷系统
US10920760B2 (en) Air compressor having an oil separator, an oil cooler, first and second evaporators, and wherein intake air and the oil are simultaneously cooled in the first and second evaporators
WO2019080523A1 (zh) 压缩机、制冷系统及空调器
CN208751086U (zh) 冷媒净化系统以及包含该冷媒净化系统的换热系统
CN105240962A (zh) 一种风温范围宽泛的水冷调温除湿机
KR20110097367A (ko) 칠러
CN104949397A (zh) 涡轮制冷机的蒸发器以及具备该蒸发器的涡轮制冷机
CN107655238B (zh) 压缩式制冷机用冷凝器
CN108375233A (zh) 一种带回热和喷射降压的复叠式制冷系统
CN110573810A (zh) 具有吸入管线液体分离器的蒸气压缩系统
WO2023109130A1 (zh) 多级压缩机及空调机组
CN107421156A (zh) 一种带冷回收功能的烟草烘烤热泵
CN108626916B (zh) 压缩式制冷机用冷凝器
JP2001056157A (ja) 冷凍装置
CN202133171U (zh) 一种蒸发器出口零过热度运行的制冷系统
CN109442778B (zh) 空调系统

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 19846681

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 19846681

Country of ref document: EP

Kind code of ref document: A1