阅读说明：本技术 回热器及具有其的制冷系统 (Heat regenerator and refrigerating system with same ) 是由 王书森 王铁伟 张捷 杨明威 于 2020-12-31 设计创作，主要内容包括：本发明公开了一种回热器和具有其的制冷系统。回热器包括：外壳体,其围成气液分离室；和内壳体,其位于气液分离室内并围成与气液分离室隔开的储液室,在储液室内布置有多个换热管,换热管具有第一端和第二端,第一端与气液分离室连通,其中,在外壳体上设有：气态冷媒输入接口,其定位靠近气液分离室的下部并且与换热管的第二端连通；至少一个气态冷媒输出接口,其延伸到气液分离室内的上部；液态冷媒输入接口和液态冷媒输出接口,液态冷媒输入接口延伸到储液室内的上部,并且液态冷媒输出接口延伸到储液室内的下部。该回热器集合气液分离器和储液器功能,克服了传统气液分离器分离出来的冷媒不易蒸发的问题。对应的制冷系统具有更高的能效比。(The invention discloses a heat regenerator and a refrigeration system with the same. The regenerator includes: an outer shell enclosing a gas-liquid separation chamber; and an inner shell, which is positioned in the gas-liquid separation chamber and encloses into a liquid storage chamber separated from the gas-liquid separation chamber, a plurality of heat exchange tubes are arranged in the liquid storage chamber, the heat exchange tubes are provided with a first end and a second end, the first end is communicated with the gas-liquid separation chamber, and the outer shell is provided with: a gaseous refrigerant input interface positioned adjacent the lower portion of the gas-liquid separation chamber and communicating with the second end of the heat exchange tube; at least one gaseous refrigerant output port extending to an upper portion of the gas-liquid separation chamber; the liquid refrigerant input interface extends to the upper part in the liquid storage chamber, and the liquid refrigerant output interface extends to the lower part in the liquid storage chamber. The heat regenerator integrates the functions of the gas-liquid separator and the liquid accumulator, and solves the problem that the refrigerant separated by the traditional gas-liquid separator is not easy to evaporate. The corresponding refrigeration system has higher energy efficiency ratio.)

1. A regenerator, characterized in that the regenerator comprises:

an outer shell enclosing a gas-liquid separation chamber; and

an inner shell positioned in the gas-liquid separation chamber and enclosing a liquid storage chamber separated from the gas-liquid separation chamber, wherein a plurality of heat exchange tubes are arranged in the liquid storage chamber, the heat exchange tubes are provided with a first end and a second end, the first end is communicated with the gas-liquid separation chamber,

wherein, be equipped with on the shell body: a gaseous refrigerant input interface positioned proximate a lower portion of the gas-liquid separation chamber and in communication with the second end of the heat exchange tube; at least one gaseous refrigerant output port extending to an upper portion of the gas-liquid separation chamber; the liquid refrigerant input interface extends to the upper part in the liquid storage chamber, and the liquid refrigerant output interface extends to the lower part in the liquid storage chamber.

2. The regenerator of claim 1 wherein a plurality of baffles are disposed in the gas-liquid separation chamber in a staggered and horizontal arrangement with respect to each other, the baffles being positioned above the inner shell.

3. The regenerator of claim 2, wherein a spray device is further disposed in the gas-liquid separation chamber above the inner shell, and a spray port is disposed on the outer shell in communication with the spray device.

4. The regenerator of claim 3 wherein the showers are secured to the lower bottom surface of the baffle adjacent the inner shell.

5. The regenerator of claim 1 wherein a gaseous refrigerant distribution chamber is disposed between the gaseous refrigerant input port and the inner shell, the gaseous refrigerant distribution chamber being in communication with the gaseous refrigerant input port and the second end of each of the heat exchange tubes, respectively.

6. The regenerator of claim 1 further comprising a level gauge port in communication with the reservoir chamber in the outer housing.

7. The regenerator of claim 1 further comprising a bypass port in communication with the bottom of the gas-liquid separation chamber in the outer shell.

8. A refrigeration system, comprising:

at least one magnetically levitated compressor;

a condenser;

an expansion valve;

a plurality of indoor air coolers connected in parallel; and

the regenerator of any of claims 1-7, wherein the gaseous refrigerant input interface is configured to be connected to the plurality of indoor air coolers, each of the at least one gaseous refrigerant output interface is configured to be connected to a gas suction pipe of a corresponding one of the magnetically levitated compressors, the liquid refrigerant input interface is configured to be connected to the condenser, and the liquid refrigerant output interface is configured to be connected to the expansion valve.

9. The refrigerant system as set forth in claim 8, wherein said at least one magnetically levitated compressor includes two magnetically levitated compressors connected in parallel.

10. The refrigeration system of claim 9, wherein the condenser is an evaporative condenser or a finned tube condenser, and each indoor air cooler includes a refrigerant evaporating coil.

Technical Field

The invention relates to a refrigeration system, in particular to a regenerator and a refrigeration system with the regenerator.

Background

A vapor compression refrigeration system generally includes four basic components, a compressor, a condenser, an expansion device, and an evaporator, interconnected to form a refrigeration circuit that allows a refrigerant to circulate therethrough. In the refrigeration cycle, the compressor sucks a low-temperature and low-pressure gaseous refrigerant through the suction port and compresses the refrigerant into a high-temperature and high-pressure gaseous refrigerant. The high-temperature and high-pressure gaseous refrigerant is discharged from a discharge port of the compressor and flows into the condenser along a refrigerant line. In the condenser, a high-temperature and high-pressure gaseous refrigerant is condensed into a medium-temperature and high-pressure liquid refrigerant by means of an air cooling or water cooling method. The medium-temperature high-pressure liquid refrigerant flows from the condenser to the expansion device along the refrigerant pipeline, and is throttled in the expansion device into low-temperature low-pressure liquid refrigerant. The low-temperature and low-pressure liquid refrigerant flows to the evaporator along the refrigerant pipeline. In the evaporator, the liquid refrigerant is evaporated into a low-temperature and low-pressure gaseous refrigerant by absorbing heat of the room air, and the room air is cooled. The low-temperature and low-pressure gaseous refrigerant is then sucked and compressed again by the compressor, thereby starting a new refrigeration cycle. Conventional compressors, such as scroll compressors, centrifugal compressors, screw compressors, etc., often require lubricating oil to provide lubrication and seal protection to the moving parts thereof during operation. When the refrigeration system works, part of lubricating oil circulates in the refrigeration loop along with a refrigerant, so that the conditions of oil shortage of a compressor and the like caused by poor oil return effect are easy to occur. Therefore, the compressor with the lubricating oil is prone to failure, and accordingly, the maintenance cost is high. Meanwhile, the system is oilless, and the oilless film on the surface of the heat exchange tube generates thermal resistance, so that the heat transfer efficiency outside the tube is improved.

Separate liquid and vapor-liquid separators are also typically provided in existing vapor compression refrigeration systems. The accumulator is generally disposed between the condenser and the expansion device, and the medium-temperature and high-pressure liquid refrigerant from the condenser flows into the accumulator and then flows from the accumulator to the expansion device. Therefore, the liquid accumulator can be used for adjusting the circulation quantity of the refrigerant in the system and storing redundant refrigerant. The gas-liquid separator is typically arranged between the evaporator and the suction of the compressor. Gaseous refrigerant from the evaporator first flows into a gas-liquid separator to remove liquid refrigerant and lubricating oil therefrom by gravity. The separated gaseous refrigerant is sucked by the compressor, so that the liquid impact phenomenon of the compressor can be prevented. However, the refrigerant separated by the conventional gas-liquid separator is not easy to evaporate, and the suction and liquid entrainment of the compressor are easily caused under the condition of poor separation.

Accordingly, there is a need in the art for a new solution to the above problems.

Disclosure of Invention

In order to solve the above problems in the prior art, that is, to solve the problem that the refrigerant separated by the conventional gas-liquid separator is not easy to evaporate and not well separated, and the gas suction and liquid carrying of the compressor are easily caused, the present invention provides a heat regenerator, which includes: an outer shell enclosing a gas-liquid separation chamber; and an inner shell, which is positioned in the gas-liquid separation chamber and encloses into a liquid storage chamber separated from the gas-liquid separation chamber, wherein a plurality of heat exchange tubes are arranged in the liquid storage chamber, each heat exchange tube is provided with a first end and a second end, the first end is communicated with the gas-liquid separation chamber, and the outer shell is provided with: a gaseous refrigerant input interface positioned proximate a lower portion of the gas-liquid separation chamber and in communication with the second end of the heat exchange tube; at least one gaseous refrigerant output port extending to an upper portion of the gas-liquid separation chamber; the liquid refrigerant input interface extends to the upper part in the liquid storage chamber, and the liquid refrigerant output interface extends to the lower part in the liquid storage chamber.

The heat regenerator is formed by combining a liquid accumulator and a gas-liquid separator, wherein a liquid refrigerant input interface can be connected to a condenser of a refrigeration system to receive medium-temperature and high-pressure liquid refrigerant from the condenser, and a liquid refrigerant output interface can be connected to an expansion device of the refrigeration system; the gaseous refrigerant input interface may be connected to an evaporator of the refrigeration system to receive low temperature and low pressure gaseous refrigerant from the evaporator, and the gaseous refrigerant output interface may be connected to a suction port of a compressor of the refrigeration system. The low-temperature low-pressure gaseous refrigerant flowing in through the gaseous refrigerant input interface flows through the heat exchange tube in the liquid storage chamber, so that heat exchange can be generated between the low-temperature low-pressure gaseous refrigerant and the medium-temperature high-pressure liquid refrigerant positioned outside the heat exchange tube in the liquid storage chamber. Through the design of the heat regenerator, the supercooling degree of the liquid refrigerant flowing to the expansion device and the superheat degree of the low-temperature gaseous refrigerant to be sucked by the compressor can be improved simultaneously, and the problems that the refrigerant separated by the traditional gas-liquid separator is not easy to evaporate and the compressor is easy to suck gas and carry liquid under the condition of poor separation are further solved.

In a preferred technical solution of the above regenerator, a plurality of baffles are arranged in the gas-liquid separation chamber, the baffles being staggered with each other and arranged horizontally, and the baffles being located above the inner shell. The baffle plate interferes the flow direction of the gaseous refrigerant, so that the gas-liquid separation effect of the gaseous refrigerant can be improved.

In the preferable technical scheme of the heat regenerator, a spraying device positioned above the inner shell is further arranged in the gas-liquid separation chamber, and a spraying interface communicated with the spraying device is arranged on the outer shell. The spraying device can be used for preventing the problem that the superheat degree of low-temperature gaseous refrigerant sucked by the compressor is overhigh.

In the above preferred embodiment of the regenerator, the spraying device is fixed to the lower bottom surface of the baffle plate close to the inner casing. This can simplify the mounting structure of the shower apparatus.

In the preferable technical scheme of the heat regenerator, a gaseous refrigerant distribution chamber is arranged between the gaseous refrigerant input interface and the inner shell, and the gaseous refrigerant distribution chamber is respectively communicated with the gaseous refrigerant input interface and the second end of each heat exchange tube. The gaseous refrigerant distribution chamber may help the gaseous refrigerant to be uniformly distributed to the respective heat exchange tubes.

In the preferable technical scheme of the heat regenerator, a liquid level meter interface communicated with the liquid storage chamber is further arranged on the outer shell. The liquid level meter which is convenient for observing the refrigerant quantity in the liquid storage chamber can be installed on the outer shell through the liquid level meter interface.

In the preferable technical scheme of the heat regenerator, a bypass interface communicated with the bottom of the gas-liquid separation chamber is further arranged on the outer shell. The bypass interface can be used for being connected to a load balance pipeline of the compressor and a bypass pipeline for reducing the pressure ratio of the refrigerating system so as to receive high-temperature gaseous refrigerant from the compressor and gasify low-temperature liquid refrigerant at the bottom of the gas-liquid separation chamber by using the high-temperature gaseous refrigerant.

The present invention also provides a refrigeration system comprising: at least one magnetically levitated compressor; a condenser; an expansion valve; a plurality of indoor air coolers connected in parallel; and a heat regenerator according to any of the above, wherein the gaseous refrigerant input interface is configured to be connected to the plurality of indoor air coolers, each of the at least one gaseous refrigerant output interface is configured to be connected to a gas suction pipe of a corresponding one of the magnetically levitated compressors, the liquid refrigerant input interface is configured to be connected to the condenser, and the liquid refrigerant output interface is configured to be connected to the expansion valve.

As will be appreciated by those skilled in the art, the refrigeration system of the present invention is an oil-free refrigeration system by employing a magnetic levitation compressor, thereby facilitating maintenance, reducing noise, and providing a high energy efficiency ratio. The refrigerating system can simultaneously increase the superheat degree and the supercooling degree of a system refrigerant by using the heat regenerator, thereby further improving the energy efficiency ratio of the whole system. Furthermore, the refrigeration system drives a plurality of indoor air coolers by the magnetic suspension compressor, is applicable to industries including but not limited to edible fungus cultivation, and can obviously reduce energy consumption.

In a preferred embodiment of the above refrigeration system, the at least one magnetically levitated compressor includes two magnetically levitated compressors connected in parallel. The two magnetic suspension compressors with a plurality of indoor air coolers can achieve better energy-saving effect.

In the preferable technical scheme of the refrigeration system, the condenser is an evaporative condenser or a finned tube condenser, and each indoor air cooler comprises a refrigerant evaporation coil. The indoor air cooler adopts the refrigerant evaporating coil pipe, can realize the purpose of direct cooling, namely directly reduces the temperature of the indoor air through the evaporation of the refrigerant in the evaporating coil pipe.

Drawings

Preferred embodiments of the present invention are described below with reference to the accompanying drawings, in which:

FIG. 1 is a schematic view of an embodiment of a refrigeration system of the present invention;

FIG. 2 is a schematic perspective view of an embodiment of the regenerator of the present invention;

FIG. 3 is a first partially sectioned isometric view of an embodiment of the regenerator of the present invention;

FIG. 4 is a second partially sectioned isometric view of an embodiment of the regenerator of the present invention;

fig. 5 is a third schematic partially cross-sectional perspective view of an embodiment of the regenerator of the present invention;

fig. 6 is a fourth partially cut-away perspective view of an embodiment of the regenerator of the present invention.

List of reference numerals

1. A refrigeration system; 10. a heat regenerator; 101. an outer housing; 101a, an outer housing top wall; 101b, an outer housing first side wall; 101c, an outer housing second side wall; 102. a gaseous refrigerant output interface; 102a, a first gaseous refrigerant output interface; 102b, a first gaseous refrigerant output interface; 103. a liquid refrigerant input interface; 104. a gaseous refrigerant input interface; 105. a bypass interface; 106. a liquid refrigerant output interface; 107. a liquid level meter interface; 108. a spray interface; 109. a base of the regenerator; 110. a gas-liquid separation chamber; 111. a baffle plate; 111a, a lower bottom surface of the baffle plate; 112. an inner housing; 112a, an inner housing top wall; 112b, inner housing first side wall; 112c, an inner housing second side wall; 113. a liquid storage chamber; 114. a heat exchange pipe; 114a, a first end of the heat exchange tube; 114b, a second end of the heat exchange tube; 115. a spraying device; 116. a dispensing chamber; 117. a dispensing chamber housing; 117a, dispensing chamber housing top wall; 117b, the dispensing chamber housing back wall; 118. spraying holes; 119. a dispensing aperture; 120. cooling the electronic expansion valve; 121. a liquid level meter; 20. a condenser; 201. a heat exchange coil; 202. a spray chamber; 203. a shower head; 204. a fan; 205. a cooling water tank; 206. a water pump; 207. a water pipe; 30. a magnetic suspension compressor; 30a, a first magnetic suspension compressor; 30b, a second magnetic suspension compressor; 301a, a first inspiratory tube; 301b, a second suction pipe; 302a, a first exhaust pipe; 302b, a second exhaust pipe; 303a, a first one-way valve; 303b, a second one-way valve; 304. a load balancing tube; 305a, a first load balancing valve; 305b, a second load balancing valve; 306. a compressor bypass pipe; 307a, a first bypass electronic expansion valve; 307b, a second bypass electronic expansion valve; 308a, a first bypass solenoid valve; 308b, a second bypass solenoid valve; 309a, a first air supply loop electromagnetic valve; 309b, a second air supply loop electromagnetic valve; 40. an indoor air cooler; 40a, a first indoor air cooler; 40b, a second indoor air cooler; 40c, a third indoor cooling fan; 40d, a fourth indoor air cooler; 40f, a fifth indoor air cooler; 50. an expansion valve; 50a, a first expansion valve; 50b, a second expansion valve; 50c, a third expansion valve; 50d, a fourth expansion valve; 50f, a fifth expansion valve; 61. an economizer; 62. an economizer electronic expansion valve; 71. a condenser liquid tube; 72. an air cooler air duct; 73. a regenerator drain pipe; 74. a load balancing connection pipe; 75. a compressor cooling tube; 76. a regenerator cooling branch; 77. an economizer bypass; 78. an air cooler liquid tube; 79. a gas supply loop connecting pipe; 80. liquid stop valve.

Detailed Description

Preferred embodiments of the present invention are described below with reference to the accompanying drawings. It should be understood by those skilled in the art that these embodiments are only for explaining the technical principle of the present invention, and are not intended to limit the scope of the present invention.

The invention provides a heat regenerator 10, which aims to solve the technical problems that refrigerants separated by a traditional gas-liquid separator are not easy to evaporate and the problem that the gas suction and the liquid carrying of a compressor are easy to cause when the refrigerants are not well separated. Regenerator 10 includes: an outer casing 101 enclosing a gas-liquid separation chamber 110; and an inner case 112 located in the gas-liquid separation chamber 110 and enclosing a liquid storage chamber 113 partitioned from the gas-liquid separation chamber 110, a plurality of heat exchange tubes 114 arranged in the liquid storage chamber 113, the heat exchange tubes 114 having a first end 114a and a second end 114b, the first end 114a communicating with the gas-liquid separation chamber 110, wherein on the outer case 101, there are provided: a gaseous refrigerant input port 104 positioned near a lower portion of the gas-liquid separation chamber 110 and communicating with the second end 114b of the heat exchange pipe 114; at least one gaseous refrigerant outlet port 102 extending to an upper portion of the gas-liquid separation chamber 110; the liquid refrigerant input interface 103 extends to the upper part of the liquid storage chamber 113, and the liquid refrigerant output interface 106 extends to the lower part of the liquid storage chamber 113.

The refrigerant mentioned herein refers to a refrigerant that can circulate in a refrigeration circuit when the refrigeration system is in operation, such as R134A. The liquid-carrying gas-suction of the compressor means that the gas refrigerant sucked by the compressor contains liquid refrigerant during gas suction.

In order to solve the problems that the traditional refrigeration system with oil is easy to break down, high in maintenance cost and high in energy consumption, the invention further provides a refrigeration system 1. The refrigeration system 1 includes: at least one magnetically levitated compressor 30; a condenser 20; an expansion valve 50; a plurality of indoor air coolers 40 connected in parallel; and a thermal regenerator 10 according to any of the above, wherein the gaseous refrigerant input interface 104 is configured to be connected to a plurality of indoor air coolers 40, each of the at least one gaseous refrigerant output interface 102 is configured to be connected to a gas suction pipe of a corresponding one of the magnetically levitated compressors 30, the liquid refrigerant input interface 103 is configured to be connected to the condenser 20, and the liquid refrigerant output interface 106 is configured to be connected to the expansion valve 50.

FIG. 1 is a schematic diagram of an embodiment of the refrigeration system of the present invention. As shown in fig. 1, in one or more embodiments, the refrigeration system 1 includes two parallel magnetically levitated compressors 30, a condenser 20, a heat regenerator 10, an economizer 61, an expansion valve 50, and five parallel indoor air coolers 40. In alternative embodiments, the refrigeration system 1 may include one magnetically levitated compressor 30 or more than two magnetically levitated compressors 30. In alternative embodiments, the refrigeration system 1 may comprise two parallel indoor air coolers 40, three parallel indoor air coolers 40, four parallel indoor air coolers 40, or more than five parallel indoor air coolers 40, matched to the power of the magnetically levitated compressor 30, so as to be usable for cooling a plurality of rooms. The maglev compressor 30, the condenser 20, the regenerator 10, and the economizer 61 together form an outdoor main portion, and the indoor air-cooler 40 and the expansion valve 50 together form an indoor portion.

As shown in fig. 1, the two magnetic levitation compressors 30 are a first magnetic levitation compressor 30a and a second magnetic levitation compressor 30b, respectively. The first and second magnetically levitated compressors 30a and 30b are connected in parallel. The first magnetic levitation compressor 30a sucks a low-temperature and low-pressure gaseous refrigerant through the first suction pipe 301a, and discharges a compressed high-pressure and high-temperature gaseous refrigerant through the first discharge pipe 302 a. A suction pressure sensor may be disposed at a position of the first suction pipe 301a near a suction port of the first magnetically levitated compressor 30 a. A first check valve 303a is disposed on the first exhaust pipe 302a to prevent the gaseous refrigerant from flowing from the first exhaust pipe 302a into an exhaust port (not shown) of the first magnetic levitation compressor 30a when the first magnetic levitation compressor 30a is stopped. Exhaust pressure sensors (not shown) may be disposed upstream and downstream of the first check valve 303a, respectively. The second magnetic levitation compressor 30b sucks a low-temperature and low-pressure gaseous refrigerant through the second suction pipe 301b, and discharges a compressed high-pressure and high-temperature gaseous refrigerant through the second discharge pipe 302 b. A suction pressure sensor may be disposed at a position of the second suction pipe 301b adjacent to a suction port of the second magnetically levitated compressor 30 b. A second check valve 303b is disposed on the second exhaust pipe 302b to prevent the gaseous refrigerant from flowing from the second exhaust pipe 302b into an exhaust port (not shown) of the second magnetic levitation compressor 30b when the second magnetic levitation compressor 30b is stopped. Exhaust pressure sensors (not shown) may be disposed upstream and downstream of the second check valve 303b, respectively.

In order to balance the load between the first and second magnetically levitated compressors 30a, 30b, a balancing load pipe 304 is provided between the first and second magnetically levitated compressors 30a, 30 b. As shown in fig. 1, the balanced load tube 304 has both ends connected to the first exhaust pipe 302a and the second exhaust pipe 302b, respectively, and the connection points are located downstream of the first check valve 303a and the second check valve 303b, respectively. A first load balancing valve 305a for the first magnetically levitated compressor 30a and a second load balancing valve 305b for the second magnetically levitated compressor 30b are respectively provided on the balanced load pipe 304. The first load balancing valve 305a and the second load balancing valve 305b are used for energy regulation and surge control of the first magnetically levitated compressor 30a and the second magnetically levitated compressor 30b, respectively.

As shown in fig. 1, a compressor bypass pipe 306 is provided between the first and second magnetically levitated compressors 30a and 30 b. The compressor bypass pipe 306 is also connected at both ends to the first and second discharge pipes 302a and 302b, respectively, and the connection points are located upstream of the first and second check valves 303a and 303b, respectively, i.e., between the discharge port of the corresponding compressor and the corresponding check valve. The compressor bypass pipe 306 is provided with: a first electronic expansion valve 307a and a first bypass solenoid valve 308a for the first magnetically levitated compressor 30 a; a second electronic expansion valve 307b for the second magnetically levitated compressor 30b and a second bypass solenoid valve 308 b. The first electronic expansion valve 307a and the first bypass solenoid valve 308a, and the second electronic expansion valve 307b and the second bypass solenoid valve 308b are both used to reduce the pressure ratio in the refrigeration system 1, thereby assisting the start and stop of the first magnetic suspension compressor 30a and the second magnetic suspension compressor 30 b.

As shown in fig. 1, the first and second magnetically levitated compressors 30a and 30b are also respectively connected to the air make-up circuit connection pipe 79. The air supply circuit connecting pipe 79 is connected to air supply interfaces (not labeled in the figure) on the first magnetic levitation compressor 30a and the second magnetic levitation compressor 30b, respectively. The air supply circuit connecting pipe 79 is provided with: a first air supply loop electromagnetic valve 309a for controlling the on-off between the first magnetic suspension compressor 30 a; and a second air replenishing loop electromagnetic valve 309b for controlling the on-off between the second air replenishing loop electromagnetic valve and the second magnetic suspension compressor 30 b. As shown in fig. 1, a compressor cooling inlet (not shown) is provided on each of the first and second magnetically levitated compressors 30a and 30 b. The first and second magnetically levitated compressors 30a and 30b are respectively connected to a compressor cooling pipe 75 through corresponding compressor cooling inlets for cooling heat generating components such as a motor and an inverter in the compressor when necessary. An electromagnetic valve and a throttle orifice are generally disposed in a cooling inlet of a compressor, the electromagnetic valve is used for controlling whether to allow the refrigerant for cooling to enter, and the throttle orifice is used for performing expansion throttling on the entering refrigerant. When the temperature inside the compressor and the temperature of the frequency converter reach or exceed a preset temperature threshold value, the electromagnetic valve is opened; when the temperature inside the compressor and the temperature of the frequency converter are lower than a preset temperature threshold value, the electromagnetic valve is closed.

As shown in fig. 1, the high-temperature and high-pressure refrigerant from the first exhaust pipe 302a and the second exhaust pipe 302b is discharged into the condenser 20. In one or more embodiments, the condenser 20 is an evaporative condenser. In an alternative embodiment, the condenser 20 may also be a finned tube condenser or other suitable form of condenser. As shown in fig. 1, the condenser 20 includes: an evaporation chamber 202; an evaporation coil 201 which is located in the evaporation chamber 202 and allows a high-temperature and high-pressure refrigerant to flow therein; a cooling water tank 205 located at the bottom of the evaporation chamber 202; a fan 204 located above the evaporation chamber 202; a shower head 203 positioned at the top inside the evaporation chamber 202; a water pump 206 for pumping cooling water from a cooling water tank 205 to the shower head 203. The water pump 206 is connected to the showerhead 203 through a water pipe 207. During operation of the condenser 20, both the water pump 206 and the fan 204 are activated. The water pump 206 circulates cooling water between the shower head 203 and the cooling water tank 205, and the fan 204 blows air to cool the cooling water. The cooling water flows over the outer surface of the evaporation coil 201 and takes away heat of the refrigerant in the evaporation coil 201, so that the high-temperature and high-pressure gaseous refrigerant in the evaporation coil 201 is condensed into a high-temperature and high-pressure liquid refrigerant. As shown in fig. 1, the high-temperature and high-pressure liquid refrigerant leaving the condenser 20 enters the regenerator 10 along the condenser liquid pipe 71.

As shown in fig. 1, the medium-temperature high-pressure liquid refrigerant exiting from regenerator 10 enters economizer 61 along regenerator outlet pipe 73. The medium-temperature high-pressure liquid refrigerant is divided into two parts before entering the economizer 61: a main flow portion and a bypass portion. The main flow portion directly enters the economizer 61, and the bypass portion flows into the economizer bypass 77 and is throttled and expanded by the economizer electronic expansion valve 62 on the economizer bypass 77 into a low-temperature and low-pressure liquid refrigerant. The bypass portion of the liquid refrigerant changed to the low temperature and low pressure then flows into the economizer 61, and lowers the temperature of the main flow portion by absorbing heat of the main flow portion in the economizer 61, while evaporating itself into the gaseous refrigerant of the low temperature and low pressure. The reduced temperature main stream portion exits the economizer 61 and flows along the air cooler liquid tube 78 to the indoor unit portion via a liquid shut-off valve 80 (e.g., a solenoid valve). The bypass portion of the gaseous refrigerant evaporated to a low temperature and a low pressure is sucked into the corresponding magnetic levitation compressor in an operating state through the supplement circuit connection pipe 79 to be compressed. The liquid refrigerant of the main flow part is stabilized by a bypass expansion refrigeration mode, and the capacity and the efficiency of the refrigeration system can be improved. In an alternate embodiment, depending on the actual configuration of the refrigerant system, the economizer may be eliminated.

As shown in fig. 1, the liquid refrigerant enters the indoor unit portion along the air cooler liquid tube 78. In the indoor unit section, the liquid refrigerant is distributed to the started indoor cooling fans 40 and the corresponding expansion valves 50 according to the number of started indoor cooling fans 40 and the load. In one or more embodiments, indoor cold air blower 40 includes a first indoor cold air blower 40a and a corresponding first expansion valve 50a, a second indoor cold air blower 40b and a corresponding second expansion valve 50b, a third indoor cold air blower 40c and a corresponding third expansion valve 50c, a fourth indoor cold air blower 40d and a corresponding fourth expansion valve 50d, a fifth indoor cold air blower 40f and a corresponding fifth expansion valve 50 f. These indoor air-cooling fans are arranged in parallel in different rooms. In one or more embodiments, each of the indoor air coolers employs a refrigerant evaporator coil (e.g., a finned tube evaporator) for the purpose of directly cooling the air in the room. The expansion valve 50 may be an electronic expansion valve or a thermostatic expansion valve. The medium-temperature high-pressure liquid refrigerant is first expanded into a low-temperature low-pressure liquid refrigerant by the corresponding expansion valve 50, and then enters the corresponding indoor air cooler 40 to cool the air in the room, and the refrigerant is evaporated into a low-temperature low-pressure gaseous refrigerant. The low-temperature and low-pressure gaseous refrigerants from the different indoor air coolers 40 are collected and enter the regenerator 10 along the air cooler gas pipes 72, and undergo gas-liquid separation in the regenerator 10. The gas-liquid separated refrigerant gas may be sucked into the corresponding maglev compressors through the first suction pipe 301a and the second suction pipe 301b, respectively.

The regenerator of the present invention is described below with reference to fig. 2 to 6. Fig. 2 is a schematic perspective view of an embodiment of the regenerator of the present invention, fig. 3 is a schematic perspective view, partially in cross-section, of the embodiment of the regenerator of the present invention, fig. 4 is a schematic perspective view, partially in cross-section, of the embodiment of the regenerator of the present invention, fig. 5 is a schematic perspective view, partially in cross-section, of a third embodiment of the regenerator of the present invention, and fig. 6 is a schematic perspective view, partially in cross-section, of a fourth embodiment of the regenerator of the present invention. As shown in fig. 2 to 6, the regenerator 10 includes a base 109, an outer casing 101 on the base 109 and enclosing a gas-liquid separation chamber 110, and an inner casing 112 enclosing a liquid storage chamber 113. The inner case 112 is located at a lower portion in the gas-liquid separation chamber 110, and the gas-liquid separation chamber 110 and the reservoir 113 are separated from each other. A plurality of heat exchange tubes 114 are disposed in the liquid storage chamber 113 in parallel and spaced arrangement with each other, the heat exchange tubes 114 having a first end 114a and a second end 114b, the first end 114a communicating with the gas-liquid separation chamber 110.

As shown in fig. 2 to 6, in one or more embodiments, on the outer case 101 are provided: a gaseous refrigerant input port 104 positioned near a lower portion of the gas-liquid separating chamber 110 and communicating with the second end 114b of the heat exchange pipe 114; two gaseous refrigerant output ports 102 extending to an upper portion of the gas-liquid separation chamber 110; a liquid refrigerant input interface 103 and a liquid refrigerant output interface 106, the liquid refrigerant input interface 103 extending to the upper portion of the liquid storage chamber 113, and the liquid refrigerant output interface 106 extending to the lower portion of the liquid storage chamber 113; a bypass port 105 connected to the bottom of the gas-liquid separation chamber 110; a level meter port 107 communicating with an upper portion inside the reservoir 113; a spray connection 108 which is connectable to an upper portion of the interior of the gas-liquid separation chamber 110. The number of gaseous refrigerant outlet ports 102 corresponds to the number of compressors in the refrigeration system. When the number of the compressors is one, the number of the gaseous refrigerant output interfaces 102 is also one. When the number of compressors exceeds two, the number of gaseous refrigerant output ports 102 also exceeds two.

As shown in fig. 2 to 6, in one or more embodiments, two baffles 111 are disposed at an upper portion inside the gas-liquid separation chamber 110, which are vertically staggered from each other. Alternatively, more baffles 111 may be disposed within the gas-liquid separation chamber 110. The baffle 111 is located above the inner case 112. The two baffles 111 are vertically spaced apart from each other and horizontally extend from two opposite sidewalls of the outer shell 101 toward each other and beyond each other, respectively, so as to disturb the upward flow of the gaseous refrigerant in the gas-liquid separation chamber 110, so that the liquid refrigerant entrained therein is separated from the gaseous refrigerant by gravity. As shown in fig. 3 to 6, a shower device 115 is further provided in the gas-liquid separation chamber 110. In one or more embodiments, the spray device 115 is a generally rectangular box with a plurality of spray holes 118 disposed in a bottom wall of the rectangular box. In one or more embodiments, the spray assembly 115 is secured directly to the lower bottom surface 111a of the baffle 111 proximate the top wall 112a of the inner housing 112. Alternatively, the shower device 115 may be fixed to the side wall of the outer case 101 by a separate connecting device.

As shown in fig. 3 to 6, the outer case 101 is a box-like body having a top wall 101a, four side walls, and a bottom wall. In one or more embodiments, the liquid refrigerant input interface 103 and the two gaseous refrigerant output interfaces 102 are disposed on the top wall 101a of the outer housing 101. The two gaseous refrigerant outlet ports 102 extend through the top wall 101a of the outer casing 101 and terminate at or near the top of the gas-liquid separation chamber 110. Referring to fig. 1, two gaseous refrigerant output interfaces 102 may be connected to the first suction pipe 301a and the second suction pipe 301b, respectively. As shown in fig. 4 to 6, the liquid refrigerant inlet port 103 extends through the top wall 101a of the outer housing 101, the gas-liquid separation chamber 110, and the top wall 112a of the inner housing 112 in this order, and terminates at an upper portion in the liquid reservoir 113. Referring to fig. 1, a liquid refrigerant input port 103 may be connected to the condenser liquid tube 71.

As shown in fig. 2, 5, and 6, in one or more embodiments, the gaseous refrigerant input interface 104 is positioned on a lower portion of the first sidewall 101b of the outer housing 101. As shown in fig. 5 and 6, a distribution chamber 116 is formed between the first side wall 101b of the outer case 101 and the first side wall 112b of the inner case 112. The distribution chamber 116 is surrounded by a distribution chamber housing 117, and the distribution chamber housing 117 includes a distribution chamber housing top wall 117a and a distribution chamber housing back wall 117b such that the distribution chamber 116 is partitioned from the gas-liquid separation chamber 110 and the liquid reservoir 113, respectively. The gaseous refrigerant inlet port 104 communicates with the distribution chamber 116 through the first sidewall 101b of the outer casing 101. Distribution holes 119 corresponding to the second end 114b of each heat exchange tube 114 are distributed on the distribution chamber housing back wall 117b so that the gaseous refrigerant introduced from the gaseous refrigerant input port 104 can be uniformly distributed into each heat exchange tube 114. Referring to fig. 1, a gaseous refrigerant inlet port 104 may be connected to the air cooler gas tube 72.

As shown in fig. 2 to 5, in one or more embodiments, the liquid refrigerant output interface 106, the liquid level meter interface 107, and the shower interface 108 are all positioned on the second side wall 101c of the outer casing 101. The liquid refrigerant outlet port 106 is located on a lower portion of the second sidewall 101c of the outer housing 101, and extends through the second sidewall 101c of the outer housing 101, the gas-liquid separation chamber 110, and a lower portion of the second sidewall 112c of the inner housing 112 in sequence to communicate with a lower portion or bottom of the liquid reservoir 113. Referring to fig. 1, liquid refrigerant output port 106 may be connected to regenerator outlet pipe 73. The level gauge port 107 extends through the second side wall 101c of the outer housing 101, the gas-liquid separation chamber 110, and the second side wall 112c of the inner housing 112 in this order to communicate with the upper portion of the reservoir 113. Referring to fig. 1, an upper end of the liquid level meter 121 may be connected to the liquid level meter port 107, and a lower end of the liquid level meter 121 may be connected to the liquid refrigerant output port 106. The shower interface 108 extends through the second side wall 101c of the outer casing 101 into an upper portion of the gas-liquid separation chamber 110 to communicate with the shower device 115. Referring to fig. 1, spray interface 108 may be connected to regenerator cooling branch 76 that branches from regenerator outlet pipe 73. A cooling electronic expansion valve 120 is disposed on the cooling branch 76 of the heat regenerator for cooling when the superheat degree of the gaseous refrigerant in the gas-liquid separation chamber 110 is too high.

As shown in fig. 2, 3, and 5, in one or more embodiments, the bypass interface 105 is located near the bottom of the first sidewall 101b of the outer casing 101, and extends through the first sidewall 101b to communicate with the bottom of the gas-liquid separation chamber 110. Referring to FIG. 1, the bypass interface 105 is generally in communication with the load balance tube 304 and the compressor bypass tube 306, respectively, via the load balance connection tube 74. The lowest part of the gas-liquid separation chamber is usually liquid refrigerant. When the compressor is turned on or off or the compressor is in surge, the corresponding control valve is opened, and the high-temperature gaseous refrigerant is introduced from the corresponding compressor to the bottom of the gas-liquid separation chamber 110 through the load balance connection pipe 74, so that the liquid refrigerant (if any) at the bottom is vaporized.

Referring to fig. 1, in one or more embodiments, a cooling interface (not labeled) may also be provided on the bottom of the sidewall of the outer housing 101. The cooling port extends through the sidewall of the outer housing, the gas-liquid separation chamber, and the sidewall of the inner housing 112 in this order to communicate with the lower portion or bottom of the liquid storage chamber 113. The cooling interface may be connected to a cooling inlet of the corresponding compressor by a compressor cooling line 75 to direct high pressure liquid refrigerant from the reservoir 113 to the compressor cooling inlet when desired.

In the design of the heat regenerator 10 of the present invention, the liquid reservoir is placed inside the gas-liquid separator, and the inside of the liquid reservoir is penetrated by the heat exchange tube 114, so that the low-temperature gaseous refrigerant evaporated from the indoor air cooler firstly penetrates through the heat exchange tube 114 in the liquid reservoir and then enters the gas-liquid separator. Therefore, the low-temperature gaseous refrigerant has the superheat degree improved by absorbing the heat of the liquid refrigerant in the liquid reservoir, and the liquid refrigerant in the liquid reservoir has the supercooling degree improved by being cooled by the low-temperature gaseous refrigerant.

So far, the technical solutions of the present invention have been described in connection with the preferred embodiments shown in the drawings, but it is easily understood by those skilled in the art that the scope of the present invention is obviously not limited to these specific embodiments. Equivalent changes or substitutions of related technical features can be made by those skilled in the art without departing from the principle of the invention, and the technical scheme after the changes or substitutions can fall into the protection scope of the invention.