Composite compression evaporative condenser

Abstract

The utility model belongs to the technical field of thermally-driven refrigeration / heat pumps, and particularly relates to a composite compression evaporative condenser which comprises a shell, tube box shell sections and end sockets, the tube box shell sections and the end sockets are located at the two ends of the shell, partition plates are arranged in the tube box shell sections and the end sockets at the two ends respectively, and circulating water inlets are formed in the upper area and the lower area, separated by the partition plates, of the end socket at one end. Circulating water outlets are formed in upper and lower areas, separated by the partition plate, of the seal head at the other end; the interior of the shell is divided into an upper condensation cavity and a lower evaporation cavity corresponding to the partition plates at the two ends, two sets of cooling pipe bundles and liquid level switch plates are alternately arranged between the condensation cavity and the evaporation cavity, and a plurality of heat exchange pipes communicated with the end sockets at the two ends are arranged in the condensation cavity and the evaporation cavity. The composite compression evaporative condenser integrates the functions of the hydraulic turbine compressor, the auxiliary condenser, the auxiliary evaporator and the expansion valve B, the problems mentioned in the background technology can be solved, the cost of the equipment and pipelines can be reduced, and the occupied area of a unit is greatly reduced.

Description

Technical Field

[0001] The utility model belongs to the technical field of heat-driven refrigeration / heat pumps, and particularly relates to a composite compression evaporation condenser. Background Art

[0002] like Figure 1 As shown, the heat-driven refrigeration unit uses low-grade waste heat to drive the thermal working fluid, and performs refrigeration through the phase change of the working fluid (such as ammonia). The main equipment includes generators, condensers, evaporators, absorbers, solution pumps, etc. After the circulating water takes away the heat from the refrigeration unit, the temperature rises, and then enters the cooling tower to return to normal temperature, and then continues the subsequent circulation. The temperature of the circulating water is greatly affected by the wet-bulb temperature of the air in the season. Because the wet-bulb temperature of the air is higher in summer, the temperature of the circulating water is also higher. The heat transfer temperature difference between it and the refrigeration unit is small. For a refrigeration unit with a certain heat exchange area, the heat it takes away is very limited. Therefore, the refrigeration efficiency of the refrigeration unit is affected or deep cooling (refrigeration at a lower temperature) cannot be achieved.

[0003] In addition, the above refrigeration process also has the following problems:

[0004] 1. Most of the heat coming out of the refrigeration unit is discharged or returned to the user's pipe network system, and the utilization rate of the heat source is not high.

[0005] 2. High-pressure liquid refrigerant is throttled and decompressed by the expansion valve to become low-pressure liquid refrigerant. Due to adiabatic throttling and decompression, flash evaporation is bound to occur, turning the original pure liquid low-pressure refrigerant into a gas-liquid saturated refrigerant (including flash vapor).

[0006] 3. The low-pressure lean liquid in the absorber of the refrigeration unit comes from the high-pressure lean liquid coming out of the generator, which is throttled and reduced in pressure by the pressure reducing valve. The throttling and reduction in pressure increase the entropy of the high-pressure lean liquid and reduce its working capacity. This part of the high-pressure energy is not utilized.

[0007] To solve the above problems, we propose a composite compression evaporation condenser. Utility Model Content

[0008] The present invention provides a composite compression evaporation condenser, which integrates the functions of a hydraulic turbine compressor, an auxiliary condenser, an auxiliary evaporator and an expansion valve B, which can not only solve the problems mentioned in the background technology, but also reduce the cost of equipment and pipelines, and greatly reduce the floor space of the unit.

[0009] The above purpose is achieved by the following preparation process:

[0010] A composite compression evaporation condenser comprises a shell and tube sheets, tube box barrel sections and heads sequentially located at two ends of the shell, wherein a partition is provided inside the tube box barrel sections and heads at both ends, wherein the upper and lower areas of the head separated by the partition are provided with circulating water inlets, and the upper and lower areas of the head separated by the partition are provided with circulating water outlets; wherein the upper circulating water inlet is connected to the circulating water outlet of the condenser, and the upper circulating water outlet is connected to the circulating water inlet of the first type of heat pump; the lower circulating water inlet is connected to the circulating water outlet of the first type of heat pump, and the lower circulating water outlet is connected to the circulating water inlet of the absorber;

[0011] The partitions at the two ends of the shell body are divided into an upper condensation chamber and a lower evaporation chamber. Two groups of cooling tube bundles and liquid level switch plates are alternately arranged between the condensation chamber and the evaporation chamber. The condensation chamber and the evaporation chamber are both provided with a plurality of heat exchange tubes connected with the end caps at both ends. The heat exchange tubes are provided with circulating water. The circulating water temperature of the condensation chamber is lower than that of the evaporation chamber.

[0012] The condensing chamber is provided with a refrigerant pipeline, a lean liquid pipeline is provided on one side of the refrigerant pipeline, and an impeller transmission structure is provided between the refrigerant pipeline and the lean liquid pipeline; wherein the inlet end of the lean liquid pipeline is connected to the lean liquid outlet of the generator, and the outlet end of the lean liquid pipeline is connected to the lean liquid inlet of the absorber;

[0013] A connecting pipe 1 is provided between the evaporation chamber and the cooling tube bundle of the lower layer, and a connecting pipe 2 is provided between the cooling tube bundle of the lower layer and the cooling tube bundle of the upper layer, and the outlet of the cooling tube bundle of the upper layer is connected to the absorber; wherein the end of the connecting pipe 2 is a gaseous refrigerant outlet, which is connected to the gaseous refrigerant inlet of the absorber.

[0014] As a further improvement of the above technical solution, the impeller transmission structure includes cavities respectively arranged on the refrigerant pipeline and the lean liquid pipeline, an impeller is arranged in the cavity, and a transmission structure is arranged between the impellers in the refrigerant pipeline and the lean liquid pipeline.

[0015] As a further improvement of the above technical solution, the liquid level switch plate includes an upper distribution orifice plate fixedly connected to both ends of the shell and a movable lower distribution orifice plate, and a liquid level switch assembly located between the upper and lower distribution orifice plates, and the holes on the upper distribution orifice plate and the lower distribution orifice plate are staggered.

[0016] As a further improvement of the above technical solution, the liquid level switch assembly includes a switch plug plate located below the hole of the lower distribution orifice plate, and an elastic member is provided between the upper end of the switch plug plate and the upper distribution orifice plate.

[0017] As a further improvement of the above technical solution, the cooling tube bundle includes parallel distribution pipes for gaseous refrigerant to enter and a collection pipe for gaseous refrigerant to discharge, and a plurality of spiral coils are distributed between the distribution pipes and the collection pipe.

[0018] As a further improvement of the above technical solution, the refrigerant pipeline includes a flash gas inlet at an upper end and a high-pressure gas refrigerant outlet at a lower end, wherein the high-pressure gas refrigerant outlet is connected to the condensation chamber.

[0019] As a further improvement of the above technical solution, the lean liquid pipeline includes a low-pressure lean liquid outlet at the upper end and a high-pressure lean liquid inlet at the lower end.

[0020] The beneficial effects of the utility model are:

[0021] (1) The composite compression condensation evaporator in the utility model integrates the functions of the hydraulic turbine compressor, auxiliary condenser, auxiliary evaporator and expansion valve B, which can reduce the cost of equipment and pipelines, greatly reduce the footprint of the unit, and is conducive to the skid-mounting of the unit.

[0022] (2) The compound compression condensation evaporator is equipped with upper and lower liquid level switch components instead of expansion valve B, so that the high-pressure liquid refrigerant is gradually decompressed. The upper and lower cooling tube bundles are also set up to use the coldness of the low-temperature gaseous refrigerant obtained after evaporation to gradually supercool the high-pressure liquid refrigerant before the gradual decompression. The flash gas generated by throttling and decompression can be greatly reduced to obtain more pure liquid low-pressure refrigerant, thereby improving the evaporation efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 It is a schematic diagram of the process flow of a heat-driven refrigeration unit in the prior art;

[0024] Figure 2 This is a front view of the interior of the composite compression condensation evaporator in the utility model;

[0025] Figure 3 yes Figure 2 AA cross-section diagram of ;

[0026] Figure 4 yes Figure 3 A partial enlarged schematic diagram of

[0027] Figure 5 yes Figure 2 Schematic diagram of the top view of the middle and upper cooling tube bundles.

[0028] Figure 6 It is a schematic diagram of the process of a heat-driven refrigeration unit including the composite compression-condensation evaporator;

[0029] Figure 7 It is another schematic diagram of the process of heat-driven refrigeration unit.

[0030] In the figure: 10, shell; 101, tube box cylinder section; 102, head; 103, tube sheet; 104, partition; 105, connecting pipe one; 106, connecting pipe two; 107, refrigerant pipeline; 108, lean liquid pipeline; 109, impeller; 110, cavity; 111, transmission structure; 20, liquid level switch plate; 201, upper distribution orifice plate; 202, lower distribution orifice plate; 203, elastic member; 204, switch plug plate; 30, cooling tube bundle; 301, distribution pipe; 302, spiral coil; 303, collection pipe; 40, heat exchange tube. DETAILED DESCRIPTION

[0031] The present application is further described in detail below in conjunction with the accompanying drawings. It is necessary to point out here that the following specific implementation methods are only used to further illustrate the present application and cannot be understood as limiting the scope of protection of the present application. Technical personnel in this field can make some non-essential improvements and adjustments to the present application based on the above application content.

[0032] like Figure 7 The heat-driven refrigeration unit shown in the figure has a refrigeration process comprising the following steps:

[0033] (1) The working fluid solution enters the generator and begins to atomize, establishing a working fluid cycle. When the generator reaches a certain liquid level, a heat source is provided to enter the generator to evaporate the amount of gaseous refrigerant required by the unit; the refrigerant flow of the condenser-sub-condenser-evaporator-sub-evaporator-absorber-generator is connected to establish a refrigerant cycle, and the refrigerant is cooled to provide cooling for the user end;

[0034] The high-pressure lean liquid from the generator is introduced into the hydraulic turbine compressor, and the flash gas generated by the high-pressure liquid refrigerant through the throttling and decompression of the expansion valve A is extracted, and the flash gas is compressed into a high-pressure gaseous refrigerant and enters the auxiliary condenser to continue to condense into a pure liquid low-pressure liquid refrigerant and enter the auxiliary evaporator to continue the subsequent refrigeration cycle;

[0035] (2) The auxiliary evaporator-first type heat pump-generator process is connected, and the circulating water flows out of the auxiliary condenser and enters the first type heat pump as a low-temperature heat source. The heat source from the generator enters the first type heat pump as a driving heat source to heat the heat carrier to provide heating for the user end;

[0036] Among them, the circulating water from the first type of heat pump enters the auxiliary evaporator, and the high-pressure liquid refrigerant from the auxiliary condenser is throttled and reduced in pressure by the expansion valve B to become a low-pressure liquid refrigerant containing flash gas, and enters the auxiliary evaporator, absorbs the heat of the circulating water, vaporizes into a low-pressure gaseous refrigerant and enters the absorber. The circulating water is cooled again in the auxiliary evaporator and enters the absorber to continue the refrigeration cycle.

[0037] The above process has the following advantages:

[0038] First, use the first type of heat pump to replace the cooling tower, use the circulating water as the low-temperature heat source, and the heat source from the generator as the driving heat source, and use the first type of heat pump to produce medium-temperature hot water for domestic heating. This not only recovers the low-grade heat contained in the circulating water, but also improves the utilization rate of heat sources and energy, and reduces the energy consumption of the cooling tower.

[0039] Second, the high-pressure lean liquid from the generator is driven by the hydraulic turbine compressor to extract the flash gas produced by throttling and decompression, so that the pure liquid low-pressure refrigerant enters the evaporator, which will greatly improve the evaporation efficiency. At the same time, the hydraulic turbine compressor compresses the flash gas into high-pressure gaseous refrigerant, which is condensed into high-pressure liquid refrigerant in the auxiliary condenser. The high-pressure liquid refrigerant can be decompressed into low-pressure liquid refrigerant through the expansion valve. The circulating water is secondary cooled in the auxiliary evaporator, so that the temperature of the circulating water entering the refrigeration unit is lower, which can further improve the refrigeration efficiency of the unit and produce deep cold (refrigeration at a lower temperature). The pressure energy of the high-pressure lean liquid is used to extract and compress the flash gas, so that the flash gas produced by the original throttling and decompression is used for secondary refrigeration to achieve secondary cooling of the circulating water. The deep utilization of internal energy in the refrigeration unit is realized, and the refrigeration performance of the unit is improved.

[0040] Example 1

[0041] like Figure 6 The heat-driven refrigeration unit shown includes a generator, a condenser, an absorber, an evaporator, and a solution pump. An expansion valve A is provided at the liquid refrigerant outlet of the condenser. The hydraulic turbine compressor, auxiliary condenser, auxiliary evaporator, and expansion valve B in the above process are replaced by a compound compression evaporation condenser.

[0042] like Figure 2 As shown, the main structure of the composite compression condensation evaporator is a fixed tube sheet heat exchanger composed of a head 102, a tube box barrel section 101, a tube sheet 103, a heat exchange tube 40 and a shell 10. The left and right heads 102 and the tube box barrel section 101 are welded and fixed on the left and right tube sheets 103 respectively. The shell 10 is welded and fixed between the left and right tube sheets 103, and the heat exchange tube 40 is welded and fixed on the left and right tube sheets 103. Partitions 104 (with an insulation layer applied on the outside) are provided in both the left and right tube boxes. The shell side shell 10 is divided into two upper and lower chambers, the upper one is the condensation chamber C, and the lower one is the evaporation chamber E. The upper cooling tube bundle 30, the upper liquid level switch plate 20, the lower cooling tube bundle 30, and the lower liquid level switch plate 20 are arranged in sequence between the condensation chamber C and the evaporation chamber E.

[0043] like Figure 3As shown, a refrigerant pipe 107 is provided on the condensing chamber C, and the refrigerant pipe 107 is provided with a flash gas inlet (the outlet end of the refrigerant pipe 107 is connected to the liquid refrigerant pipe between the condenser and the evaporator), an impeller 109, a cavity 110 and a high-pressure gas refrigerant outlet from top to bottom, wherein the high-pressure gas refrigerant outlet is connected to the condensing chamber C. A low-pressure gas refrigerant outlet 1 is provided in the middle of the evaporating chamber E, and a low-pressure gas refrigerant outlet 2 is provided in the middle of the condensing chamber C. The low-pressure gas refrigerant outlet 1 is connected to the lower cooling tube bundle 30 through a connecting pipe 105, and the upper and lower cooling tube bundles 30 are connected through a connecting pipe 2 106, and the lower cooling tube bundle 30 is connected to the low-pressure gas refrigerant outlet 2.

[0044] A lean liquid pipeline 108 is provided on one side of the refrigerant pipeline 107. The lean liquid pipeline 108 is provided with a high-pressure lean liquid inlet, a cavity 110, an impeller 109 and a low-pressure lean liquid outlet from bottom to top. The impeller 109 of the refrigerant pipeline 107 is connected to the impeller 109 of the lean liquid pipeline 108 by a transmission structure 111 (transmission shaft).

[0045] like Figure 4 As shown, the liquid level switch plate 20 includes an upper distribution orifice plate 201 fixedly connected to both ends of the housing 10, a movable lower distribution orifice plate 202, and a liquid level switch assembly located between the upper and lower distribution orifice plates 202, and the holes on the upper distribution orifice plate 201 and the lower distribution orifice plate 202 are staggered. The liquid level switch assembly includes a switch plug plate 204 located below the holes of the lower distribution orifice plate 202, and an elastic member 203 is provided between the upper end of the switch plug plate 204 and the upper distribution orifice plate 201.

[0046] That is, an upper cooling tube bundle 30, an upper upper distribution orifice plate 201, an upper lower distribution orifice plate 202, a plurality of evenly distributed upper liquid level switch assemblies, a lower cooling tube bundle 30, a lower upper distribution orifice plate 201, a lower lower distribution orifice plate 202 and a plurality of evenly distributed lower liquid level switch assemblies are sequentially arranged between the condensation chamber C and the evaporation chamber E.

[0047] The two ends of the upper and lower distribution orifice plates 202 are respectively welded and fixed between the left and right tube plates 103. The liquid level switch assembly consists of an elastic member 203 (spring) and a switch plug plate 204. The upper end of the elastic member 203 is fixed to the distribution orifice plate, and the lower end of the elastic member 203 is provided with a switch plug plate 204. A certain tension is reserved in the elastic member 203. When the liquid level in the condensation chamber C does not reach the set height H1, because the tension in the elastic member 203 is greater than (pressure + gravity), the switch plug plate 204 is closed, and the liquid level switch assembly is in a closed state. When the liquid level in the cooling chamber reaches the set height H1, because the combined force of (pressure + gravity + static pressure of the liquid column) is slightly greater than the tension of the elastic member 203, the switch plug plate 204 is slightly opened. The high-pressure liquid refrigerant is throttled and reduced in pressure to medium-pressure liquid refrigerant (including flash gas) through the micro-opening between the switch plug plate 204 and the lower distribution orifice plate 202. As the medium-pressure liquid refrigerant accumulates continuously, when its liquid level reaches H2, the switch plug plate 204 is slightly opened because the combined force of (pressure + gravity + static pressure of liquid column) is slightly greater than the pulling force of the elastic member 203. The medium-pressure liquid refrigerant is throttled and decompressed into low-pressure liquid refrigerant (including flash gas) through the micro-opening between the switch plug plate 204 and the lower distribution orifice plate 202;

[0048] The left and right pipe boxes of the condensing chamber C are respectively provided with interfaces for circulating water (from the condenser) and outlets for circulating water (to the first type of heat pump). The left and right pipe boxes of the evaporating chamber E are respectively provided with interfaces for circulating water (from the first type of heat pump) and outlets for circulating water (to the absorber).

[0049] like Figure 5 As shown, the upper and lower cooling tube bundles 30 are composed of a distribution pipe 301, a collection pipe 303, a plurality of groups of spiral coils 302, and a low-pressure gaseous refrigerant inlet and outlet. A plurality of groups of spiral coils 302 are arranged between the distribution pipe 301 and the collection pipe 303, and the distribution pipe 301 and the collection pipe 303 are respectively provided with a low-pressure gaseous refrigerant inlet and outlet.

[0050] The compound compression condensation evaporator works as follows:

[0051] The high-pressure lean liquid from the generator drives the impeller 109 in the lean liquid pipeline 108 to rotate at a high speed. The high-pressure lean liquid drives the impeller 109 to do work and turns itself into low-pressure lean liquid. The impeller 109 drives the impeller 109 of the refrigerant pipeline 107 to rotate through the transmission shaft. The high-speed rotation of the impeller 109 forms a vacuum in the cavity 110 of the refrigerant pipeline 107, extracts the flash gas generated by the throttling and decompression of the high-pressure liquid refrigerant through the expansion valve A, and the impeller 109 does work on the flash gas to increase the pressure energy of the flash gas, and turns the flash gas into a high-pressure gaseous refrigerant in the cavity 110, and introduces it into the shell 10 of the condensing chamber C.

[0052] The circulating water coming out of the condenser enters the heat exchange tube 40 of the condensation chamber C, and the high-pressure gaseous refrigerant is condensed into high-pressure liquid refrigerant through the heat exchange tube 40.

[0053] The circulating water flows out of the right pipe box of the condensing chamber C and enters the first type of heat pump as a low-temperature heat source. The heat source from the generator enters the first type of heat pump as a driving heat source, thereby producing medium-temperature hot water (heat carrier) for domestic heating. The first type of heat pump recovers the heat in the circulating water, and the circulating water is cooled. The heat source from the generator is reused in the first type of heat pump and then flows out of the boundary. Therefore, the circulating water temperature of the condensing chamber C is lower than the circulating water temperature of the evaporating chamber E.

[0054] When the high-pressure liquid refrigerant in the condensing chamber C does not reach the set height H1, because the pulling force in the elastic member 203 is greater than (pressure + gravity), the switch plug plate 204 is closed and the liquid level switch assembly is in a closed state. When the liquid level in the condensing chamber C reaches the set height H1, because the combined force of (pressure + gravity + static pressure of the liquid column) is slightly greater than the pulling force of the elastic member 203, the switch plug plate 204 is slightly opened. The high-pressure liquid refrigerant is throttled and decompressed into medium-pressure liquid refrigerant (including flash gas) through the micro-opening between the switch plug plate 204 and the lower distribution orifice plate 202. As the medium-pressure liquid refrigerant continues to accumulate, when its liquid level reaches H2, because the combined force of (pressure + gravity + static pressure of the liquid column) is slightly greater than the pulling force of the elastic member 203, the switch plug plate 204 is slightly opened. The medium-pressure liquid refrigerant is throttled and reduced in pressure through the micro-opening between the switch plug plate 204 and the lower distribution orifice plate 202 to become a low-pressure liquid refrigerant (including flash gas). The low-pressure liquid refrigerant obtained by throttling and reducing the pressure through several evenly distributed liquid level switch components falls on the outer surface of the heat exchange tube 40 in the evaporation chamber E to form a liquid film.

[0055] The heat of the circulating water from the first type of heat pump in the heat exchange tube 40 is absorbed, and the low-pressure liquid refrigerant itself vaporizes into a low-pressure gaseous refrigerant, flows out through the low-pressure gaseous refrigerant outlet 1, enters the distribution pipe 301 in the lower cooling tube bundle 30 through the connecting pipe 1 105, absorbs the heat of the medium-pressure liquid refrigerant through a plurality of groups of spiral coils 302, and the medium-pressure liquid refrigerant is supercooled. At the same time, the low-pressure gaseous refrigerant flows out of the lower cooling tube bundle 30 through the collecting pipe 303, and enters the distribution pipe 301 in the upper cooling tube bundle 30 through the connecting pipe 2 106, and absorbs the heat of the high-pressure liquid refrigerant again through a plurality of groups of spiral coils 302, and the high-pressure liquid refrigerant is supercooled. The low-pressure gaseous refrigerant flows out through the low-pressure gaseous refrigerant outlet 2 and is absorbed by the absorber.

[0056] The composite compression evaporation condenser of this embodiment has the following advantages:

[0057] The compound compression condensation evaporator integrates the functions of hydraulic turbine compressor, auxiliary condenser, auxiliary evaporator and expansion valve B, which can reduce the cost of equipment and pipelines, greatly reduce the footprint of the unit, and is conducive to the skid-mounting of the unit.

[0058] The composite compression condensation evaporator is provided with upper and lower liquid level switch plates 20 instead of expansion valve B, so that the high-pressure liquid refrigerant is decompressed step by step. The upper and lower cooling tube bundles 30 are provided, and the coldness of the low-temperature gaseous refrigerant obtained after evaporation is used to subcool the high-pressure liquid refrigerant before the step-by-step decompression step by step. The flash gas generated by throttling and decompression can be greatly reduced to obtain more pure liquid low-pressure refrigerant, thereby improving the evaporation efficiency.

[0059] The above-mentioned embodiments only express several implementation methods of the utility model, and the description is relatively specific and detailed, but it cannot be understood as limiting the scope of the patent of the utility model. It should be pointed out that for ordinary technicians in this field, several improvements can be made without departing from the concept of the utility model, which all belong to the protection scope of the utility model.

Claims

1. A composite compression evaporation condenser, comprising a shell and a tube sheet, a tube box barrel section and a head located at both ends of the shell in sequence, characterized in that: A partition is provided inside the tube box cylinder section and the head at both ends, wherein the upper and lower areas of the head at one end separated by the partition are provided with a circulating water inlet, and the upper and lower areas of the head at the other end separated by the partition are provided with a circulating water outlet; The partitions at the two ends of the shell are divided into an upper condensation chamber and a lower evaporation chamber. Two groups of cooling tube bundles and liquid level switch plates are alternately arranged between the condensation chamber and the evaporation chamber. The condensation chamber and the evaporation chamber are each provided with a plurality of heat exchange tubes connected to the end caps at both ends. Circulating water flows through the heat exchange tubes. A refrigerant pipeline is provided on the condensing chamber, a lean liquid pipeline is provided on one side of the refrigerant pipeline, and an impeller transmission structure is provided between the refrigerant pipeline and the lean liquid pipeline; A connecting pipe 1 is provided between the evaporation chamber and the cooling tube bundle of the lower layer, a connecting pipe 2 is provided between the cooling tube bundle of the lower layer and the cooling tube bundle of the upper layer, and the outlet of the cooling tube bundle of the upper layer is connected to the absorber; wherein the end of the connecting pipe 2 is the outlet of the gaseous refrigerant.

2. The composite compression evaporation condenser according to claim 1, characterized in that: The impeller transmission structure comprises cavities respectively arranged on the refrigerant pipeline and the lean liquid pipeline, an impeller is arranged in the cavity, and a transmission structure is arranged between the impellers in the refrigerant pipeline and the lean liquid pipeline.

3. The composite compression evaporation condenser according to claim 1, characterized in that: The liquid level switch plate comprises an upper distribution orifice plate fixedly connected to both ends of the housing, a movable lower distribution orifice plate and a liquid level switch assembly located between the upper and lower distribution orifice plates, and the holes on the upper distribution orifice plate and the lower distribution orifice plate are staggered.

4. The composite compression evaporation condenser according to claim 3, characterized in that: The liquid level switch assembly comprises a switch plug plate located below the hole of the lower distribution orifice plate, and an elastic member is arranged between the upper end of the switch plug plate and the upper distribution orifice plate.

5. The composite compression evaporation condenser according to claim 4, characterized in that: The cooling tube bundle comprises a distribution tube arranged in parallel and used for gaseous refrigerant to enter and a collection tube for gaseous refrigerant to discharge, and a plurality of spiral coils are distributed between the distribution tube and the collection tube.

6. The composite compression evaporation condenser according to any one of claims 1 to 5, characterized in that: The refrigerant pipeline comprises a flash gas inlet at an upper end and a high-pressure gas refrigerant outlet at a lower end, wherein the high-pressure gas refrigerant outlet is communicated with the condensing chamber.

7. The composite compression evaporation condenser according to any one of claims 1 to 5, characterized in that: The lean liquid pipeline comprises a low-pressure lean liquid outlet at an upper end and a high-pressure lean liquid inlet at a lower end.

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