Double-effect condenser of thermosyphon screw refrigerating unit

Abstract

The utility model discloses a double-effect condenser of a thermosyphon screw refrigerating unit, which comprises a horizontal cylinder, and a heat exchange tube bundle is integrally arranged in the middle of an inner cavity of the horizontal cylinder, so that the inner cavity of the horizontal cylinder is divided into an upper gas storage space and a lower liquid storage space; a gas inlet is formed in one side of the top of the horizontal cylinder and is used for receiving high-temperature and high-pressure refrigerant gas from the oil separator; an air return port is formed in the other side of the top of the horizontal cylinder and is used for receiving refrigerant gas returned by the oil cooler; an auxiliary liquid supply pipe is arranged on one side of the bottom of the horizontal barrel and used for conveying refrigerant liquid to the oil cooler. A main liquid supply pipe is arranged on the other side of the bottom of the horizontal barrel and used for conveying refrigerant liquid to the evaporator. The auxiliary liquid supply pipe is flush with the inner wall of the bottom of the horizontal barrel, and the main liquid supply pipe extends into the inner wall of the bottom of the horizontal barrel, so that a height difference is formed between the two pipe openings. The thermosyphon condenser can have the functions of a condenser and a thermosyphon liquid reservoir, so that a liquid reservoir is omitted, the unit structure is more compact and reasonable, and the unit manufacturing cost is lower.

Description

Technical Field

[0001] The utility model relates to equipment in a screw refrigeration unit, in particular to a dual-function condenser of a thermosiphon screw refrigeration unit. Background Art

[0002] Conventional screw refrigeration units primarily consist of a screw compressor, oil separator, oil cooler, coarse oil filter, oil pump, fine oil filter, condenser, evaporator, and corresponding circulation piping and valves. They are widely used in industries such as refrigeration, air conditioning, chemicals, food, and medicine. Oil coolers typically use water as a coolant to cool the lubricating oil discharged from the screw compressor during operation, making them primarily suitable for use in areas with abundant water resources. However, in areas where water resources are scarce, the operating cost of using water to cool the lubricating oil is very high. Furthermore, oil coolers using water as a coolant have high water quality requirements. Impurities in the water can cause scaling on the inner walls of the oil cooler's heat exchange tubes, reducing the heat transfer coefficient. Periodic inspection and cleaning of the heat exchange tubes is necessary, increasing maintenance and repair costs, and raising unit operating costs.

[0003] To address the aforementioned issues, those skilled in the art have designed a thermosiphon oil cooler that uses refrigerant as a cooling medium, replacing conventional oil coolers that use water as a cooling medium. The thermosiphon oil cooler has a horizontal shell-and-tube structure, with lubricating oil flowing outside the heat exchange tubes (shell side) and refrigerant flowing inside the heat exchange tubes (tube side) and in the tube box. The refrigerant liquid, condensed from the condenser, is diverted before the throttling mechanism into the tube side of the thermosiphon oil cooler, absorbing heat from the lubricating oil outside the heat exchange tubes and evaporating along the way. The density of the refrigerant liquid gradually decreases during evaporation. The density of the gas-liquid mixed refrigerant in the return pipe of the thermosiphon oil cooler is lower than the density of the liquid refrigerant in the supply pipe of the thermosiphon oil cooler. The pressure difference created by this imbalance allows the liquid refrigerant to continuously flow into the thermosiphon oil cooler, continuously absorbing heat from the lubricating oil and cooling the lubricating oil.

[0004] The screw refrigeration unit using a thermosiphon oil cooler constitutes a thermosiphon screw refrigeration unit. Due to the reasonable optimization of the liquid supply and return air methods of the thermosiphon oil cooler, it does not need to frequently clean the heat exchange tubes during operation, thereby being able to meet the needs of low-cost and economical operation of the refrigeration unit in areas with poor water quality or water shortage.

[0005] However, to ensure stable operation of thermosyphon screw refrigeration units, a thermosyphon liquid receiver is often required to collect the refrigerant liquid condensed by the condenser. This receiver maintains a sufficiently high pressure to deliver the refrigerant liquid to the thermosyphon oil cooler while collecting the refrigerant liquid. In existing refrigeration units, the condenser is often supported above the evaporator by a frame. The addition of a thermosyphon liquid receiver not only complicates the unit's piping and creates an awkward layout, but also increases production costs and refrigerant charge, significantly increasing both investment and maintenance costs. Summary of the Invention

[0006] The purpose of the present invention is to overcome the deficiencies of the above-mentioned prior art and to provide a dual-function condenser for a thermosyphon screw refrigeration unit, which can have the functions of both a condenser and a thermosyphon liquid reservoir, thereby eliminating the liquid reservoir, making the unit structure more compact and reasonable, and lowering the unit manufacturing cost.

[0007] To achieve the above-mentioned purpose, the dual-function condenser of the thermosyphon screw refrigeration unit designed in the present invention comprises a horizontal cylinder, end tube sheets are provided at both ends of the horizontal cylinder, a tube box head is provided on the outside of the end tube sheet, and a cooling water baffle, a cooling water inlet and a cooling water outlet are provided on one of the tube box heads, a heat exchange tube bundle connected to the cooling water inlet and the cooling water outlet is provided in the longitudinal direction of the inner cavity of the horizontal cylinder, and both ends of the heat exchange tube bundle are supported on the end tube sheets; its special features are:

[0008] The heat exchange tube bundle is integrated and arranged in the middle of the inner cavity of the horizontal cylinder, thereby dividing the inner cavity of the horizontal cylinder into an upper gas storage space and a lower liquid storage space; an air inlet is provided on one side of the top of the horizontal cylinder for receiving high-temperature and high-pressure refrigerant gas from the oil separator; an air return port is provided on the other side of the top of the horizontal cylinder for receiving high-temperature refrigerant gas or gas-liquid mixture returned by the oil cooler; an auxiliary liquid supply pipe is provided on one side of the bottom of the horizontal cylinder for conveying condensed refrigerant liquid to the oil cooler; a main liquid supply pipe is provided on the other side of the bottom of the horizontal cylinder for conveying condensed refrigerant liquid to the evaporator; the pipe mouth of the auxiliary liquid supply pipe is flush with the inner wall of the bottom of the horizontal cylinder, and the pipe mouth of the main liquid supply pipe extends into the inner wall of the bottom of the horizontal cylinder, thereby forming a height difference between the two pipe mouths.

[0009] The dual-function condenser of this utility model operates as follows: high-temperature, high-pressure refrigerant gas separated from the oil separator enters the upper gas storage space of the horizontal cylinder through the air inlet, undergoes heat exchange with the circulating cooling water within the heat exchange tube bundle, and after condensation and cooling, it becomes refrigerant liquid and falls into the lower liquid storage space of the horizontal cylinder. The refrigerant liquid is then discharged in two ways: one way, through the auxiliary liquid supply pipe, enters the tube side of the oil cooler, where it undergoes heat exchange with the high-temperature lubricating oil from the oil separator in the shell side. The refrigerant liquid absorbs heat from the high-temperature lubricating oil and evaporates. During the evaporation process, the refrigerant liquid gradually decreases in density, creating a pressure differential between the front and rear ends of the tube side due to the different refrigerant densities. This creates a thermosiphon effect in the oil cooler, ensuring stable refrigerant flow. The evaporated high-temperature refrigerant gas or gas-liquid mixture then returns to the upper gas storage space through the return port, repeating the cycle. The other way, through the main liquid supply pipe, flows into the evaporator, where it evaporates into low-temperature, low-pressure refrigerant gas, which then returns to the intake port of the screw compressor, completing the refrigeration cycle. Since there is a height difference between the auxiliary liquid supply pipe and the main liquid supply pipe, the nozzle plane of the auxiliary liquid supply pipe is lower than the nozzle plane of the main liquid supply pipe. Therefore, the refrigerant liquid in the lower liquid storage space always gives priority to supplying the oil cooler. Only when the liquid level in the lower liquid storage space exceeds the nozzle plane of the main liquid supply pipe, will refrigerant liquid be supplied to the evaporator, thereby ensuring that there is always refrigerant supplying the oil cooler when the unit is running, and ensuring normal air return from the oil cooler.

[0010] As a preferred embodiment, the height from the bottom inner wall of the horizontal cylinder to the top of the lower liquid storage space is at least 170 mm, and the height difference between the two nozzles of the auxiliary liquid supply pipe and the main liquid supply pipe is 140 to 160 mm. Maintaining a height of at least 170 mm in the lower liquid storage space of the horizontal cylinder and avoiding the placement of heat exchange tube bundles in this space ensures that this space serves as the minimum liquid storage space for the thermosyphon condenser, thus functioning as a thermosyphon liquid storage. The nozzle of the main liquid supply pipe extends into the bottom inner wall of the horizontal cylinder, its nozzle lower than the top of the lower liquid storage space but 140 to 160 mm higher than the nozzle of the auxiliary liquid supply pipe. This is designed based on the fact that the liquid storage capacity of the thermosyphon condenser is approximately 20% greater than the refrigerant flow rate required for heat exchange in the oil cooler. This design prioritizes liquid supply to the oil cooler over that to the evaporator, preventing abnormal operation of the screw refrigeration unit due to insufficient liquid supply to the oil cooler.

[0011] Specifically, the height from the bottom inner wall of the horizontal cylinder to the top of the lower liquid storage space is 170 mm, and the height difference between the two pipe openings is 150 mm. Practice has proven that a condenser employing these design parameters can simultaneously function as a thermosyphon reservoir, eliminating the need for a reservoir. Furthermore, refrigerant liquid can flow uninterruptedly to the oil cooler, achieving a reliable thermosyphon effect.

[0012] As a preferred solution, the air inlet is staggered with the auxiliary liquid supply pipe, and the air return port is staggered with the main liquid supply pipe. This not only appropriately reduces the inlet flow rate of high-temperature and high-pressure refrigerant, keeping the liquid level as stable as possible, but also prevents refrigerant gas from the oil separator from flowing into the oil cooler.

[0013] Furthermore, an anti-collision plate is installed in the upper gas storage space of the horizontal cylinder, corresponding to the air inlet. This not only reduces the impact of high-temperature, high-pressure refrigerant gas on the heat exchange tube bundle when it enters at high speed, but also allows the refrigerant gas flow to be diverted to the left and right, effectively enhancing the heat exchange effect.

[0014] Furthermore, a gas phase balance interface is provided on the top of the horizontal cylinder, so that gas and liquid can be evenly distributed among multiple condensers arranged in parallel, providing corresponding possibilities for multiple containers to work in parallel.

[0015] Furthermore, a sight glass is provided on the outer wall of the horizontal cylinder corresponding to the lower liquid storage space, so that the liquid level in the inner cavity of the horizontal cylinder can be visually checked to adjust the unit to the optimal operating state.

[0016] Furthermore, the horizontal cylinder is equipped with a vent valve and a safety valve at the top, and a drain valve at the bottom. The vent valve can be used for maintenance and cleaning after the entire horizontal cylinder is emptied. The safety valve can effectively discharge heated gases in an emergency, maintaining a constant pressure within the entire horizontal cylinder. The drain valve is located at the lowest point of the bottom, allowing for easy removal of impurities within the horizontal cylinder.

[0017] The utility model has the following advantages:

[0018] First, the layout of the heat exchange tube bundle of the condenser is optimized and integrated in the middle of the inner cavity of the horizontal cylinder. The upper and lower parts of the cylinder both have a certain amount of space without heat exchange tubes, which respectively constitute the upper gas storage space and the lower liquid storage space. In this way, the condenser can have the function of a thermal siphon liquid storage device while maintaining its own condensation function, thereby eliminating the liquid storage device configured in the thermal siphon screw refrigeration unit, making the unit structure more reasonable and compact, reducing the unit manufacturing cost, effectively reducing the refrigerant charge amount, and also reducing the later maintenance cost of the oil cooler.

[0019] Secondly, the auxiliary liquid supply pipe of the condenser is designed to be flush with the inner wall of the bottom of the horizontal cylinder, and the main liquid supply pipe extends into the inner wall of the bottom of the horizontal cylinder. The nozzle plane of the main liquid supply pipe is higher than the nozzle plane of the auxiliary liquid supply pipe. In this way, the liquid supply to the oil cooler always takes precedence over the liquid supply to the evaporator, that is, as long as there is refrigerant liquid at the bottom of the horizontal cylinder, the oil cooler can be supplied with liquid, and the evaporator will only be supplied with liquid when the liquid level exceeds the nozzle plane of the main liquid supply pipe. This ensures that there is always refrigerant to supply liquid to the oil cooler when the screw refrigeration unit is running, and also ensures the flow rate of liquid supply to the oil cooler, avoiding excessively high lubricating oil temperature due to insufficient liquid supply, which leads to a reduction in the cooling capacity of the screw unit, thereby maintaining the stable operation of the unit.

[0020] Third, since the condenser omits the matching thermosyphon liquid storage device, it can maintain a reasonable appearance of the screw refrigeration unit while ensuring the condensing function, liquid storage effect and liquid supply height, meeting the installation needs of some customers with small workshops and insufficient overall space, and can significantly save the investment cost required for site renovation. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 This is a schematic diagram of the main structure of the dual-function condenser of the thermosyphon screw refrigeration unit of the present invention.

[0022] Figure 2 for Figure 1 Schematic diagram of the longitudinal cross-section structure.

[0023] Figure 3 for Figure 1 Schematic diagram of the left view structure.

[0024] Figure 4 for Figure 1 Schematic diagram of the transverse cross-sectional structure.

[0025] Figure 5 for Figure 1 The figure shows a schematic diagram of the connection structure between the dual-function condenser and other components in the thermosyphon screw refrigeration unit.

[0026] The components in the figure are numbered as follows:

[0027] Pipe box head 1, return air port 2, vent valve 3, safety valve 4, gas phase balance interface 5, heat exchange tube bundle 6, horizontal cylinder 7 (including: upper gas storage space S, lower liquid storage space P), anti-collision plate 8, air inlet 9, cooling water baffle 10, end tube sheet 11, auxiliary liquid supply pipe 12, cylinder support 13, sight glass 14, main liquid supply pipe 15, drain valve 16, cooling water inlet 17, cooling water outlet 18, height difference H between the auxiliary liquid supply pipe and the main liquid supply pipe.

[0028] Screw compressor 100; oil separator 200; oil cooler 300; dual-function condenser 400; evaporator 500. DETAILED DESCRIPTION

[0029] The present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments, but these embodiments should not be construed as limiting the present invention.

[0030] like Figures 1 to 5 As shown, the dual-function condenser 400 for a thermosyphon screw refrigeration unit described in this embodiment comprises a horizontal barrel 7, which is mounted and fixed on a pair of barrel supports 13. End tube sheets 11 are mounted on the left and right ends of the horizontal barrel 7. A pipe box header 1 is mounted on the outer side of the end tube sheets 11. The right pipe box header 1 is provided with a cooling water baffle 10, a cooling water inlet 17, and a cooling water outlet 18. A heat exchange tube bundle 6 is longitudinally arranged within the interior of the horizontal barrel 7, communicating with the cooling water inlet 17 and the cooling water outlet 18. Both ends of the heat exchange tube bundle 6 are supported on the end tube sheets 11.

[0031] Specifically, the heat exchange tube bundle 6 is integrated within the interior of the horizontal cylinder 7, dividing the interior of the horizontal cylinder 7 into an upper gas storage space S and a lower liquid storage space P. The dimensions of the upper gas storage space S and lower liquid storage space P can be designed based on the requirements of the oil cooler 300 configured for the screw refrigeration unit. The tube sheet layout can be adjusted to ensure a reasonable amount of gas storage space at the top of the cylinder and sufficient liquid storage space at the bottom of the cylinder. An air inlet 9 is provided on the top right side of the horizontal cylinder 7 for receiving high-temperature, high-pressure refrigerant gas from the oil separator 200. A return air port 2 is provided on the top left side of the horizontal cylinder 7 for receiving high-temperature refrigerant gas or a gas-liquid mixture returned from the oil cooler 300. An auxiliary liquid supply pipe 12 is provided on the bottom right side of the horizontal cylinder 7 for transporting condensed refrigerant liquid to the oil cooler 300. A main liquid supply pipe 15 is provided on the bottom left side of the horizontal cylinder 7 for transporting condensed refrigerant liquid to the evaporator 500.

[0032] More specifically, the opening of the auxiliary liquid supply pipe 12 is flush with the bottom inner wall of the horizontal cylinder 7, while the opening of the main liquid supply pipe 15 extends into the bottom inner wall of the horizontal cylinder 7, creating a height difference H between the two openings. This height difference H is designed to ensure that liquid supply to the oil cooler 300 takes precedence over liquid supply to the evaporator 500, ensuring that the oil cooler 300 always has normal liquid supply and return air. Failure to ensure sufficient liquid supply space will result in insufficient cooling of the lubricating oil, and excessively high oil temperature will reduce the cooling capacity of the screw compressor 100.

[0033] Generally speaking, the height from the bottom inner wall of the horizontal cylinder 7 to the top of the lower liquid storage space P is designed to be at least 170 mm. This ensures that the lower liquid storage space P serves as the minimum liquid storage space for the dual-function condenser 400, acting as a substitute for a thermosyphon liquid storage system. The height difference H between the opening of the auxiliary liquid supply pipe 12 and the opening of the main liquid supply pipe 15 is designed to be 140-160 mm. This is designed based on the fact that the liquid storage capacity of the dual-function condenser 400 is approximately 20% greater than the refrigerant flow rate required for heat exchange in the oil cooler 300, thus preventing insufficient liquid supply to the oil cooler 300.

[0034] In this embodiment, the height from the bottom inner wall of the horizontal cylinder 7 to the top of the lower liquid storage space P is designed to be 170 mm, with a height difference H = 150 mm between the two pipe openings. Because the opening of the auxiliary liquid supply pipe 12 is flush with the bottom inner wall of the horizontal cylinder 7, any refrigerant liquid in the lower liquid storage space P can be used to supply the oil cooler 300. As long as the screw compressor 100 is operating, the liquid refrigerant in the dual-action condenser 400 continuously flows into the oil cooler 300, absorbing heat from the lubricating oil and cooling the lubricating oil. The refrigerant flow is driven by the heat provided by the high-temperature lubricating oil in the oil cooler 300. Once the screw compressor 100 stops operating and no longer produces hot oil, the flow of refrigerant in the oil cooler 300 also ceases. Refrigerant liquid only supplies the evaporator 500 when the refrigerant liquid level in the lower liquid storage space P exceeds H = 150 mm. That is, the liquid supply to the oil cooler 300 is prioritized to prevent abnormal operation of the unit due to insufficient liquid supply to the oil cooler 300.

[0035] In this embodiment, the air inlet 9 is staggered with the auxiliary liquid supply pipe 12, and the air return port 2 is staggered with the main liquid supply pipe 15. This staggered arrangement reduces the inlet flow rate of the high-temperature, high-pressure refrigerant, keeps the liquid level in the horizontal cylinder 7 as stable as possible, and prevents refrigerant gas from the oil separator 200 from flowing into the oil cooler 300.

[0036] A bumper plate 8 is provided in the upper gas storage space S of the horizontal cylinder 7 corresponding to the air inlet 9, which can slow down the intake flow rate of the high-temperature and high-pressure refrigerant gas, reduce the impact on the heat exchange tube bundle 6, and divert the high-temperature and high-pressure refrigerant gas to the left and right sides, thereby enhancing the heat exchange effect.

[0037] As an alternative, a gas phase balance interface 5 is provided on the top of the horizontal cylinder 7 for achieving even distribution of gas and liquid among a plurality of condensers arranged in parallel, thus providing corresponding possibilities for a plurality of containers to operate in parallel.

[0038] A sight glass 14 is provided on the outer wall of the horizontal cylinder 7 corresponding to the lower liquid storage space P, which is used to observe the liquid level and condensation condition of the refrigerant in the horizontal cylinder 7. The operator can adjust or control the refrigerant filling amount according to the refrigerant condition displayed, thereby ensuring that the refrigerant medium in the horizontal cylinder 7 always operates within the normal range.

[0039] A vent valve 3 and a safety valve 4 are located at the top of the horizontal cylinder 7, and a drain valve 16 is located at the bottom of the horizontal cylinder 7. The vent valve 3 is used for vacuuming the equipment, performing pressure tests, and performing maintenance and cleaning after the cylinder is emptied. The safety valve 4 can be used to promptly discharge high-pressure refrigerant gas in an emergency to maintain a constant pressure throughout the equipment. The drain valve 16 is used to remove impurities from the interior of the horizontal cylinder 7.

[0040] During operation of the dual-function condenser 400 of the present invention, the high-temperature, high-pressure refrigerant gas separated from the oil separator 200 enters the upper gas storage space S of the horizontal cylinder 7 through the air inlet 9, undergoes heat exchange with the circulating cooling water within the heat exchange tube bundle 6, and after condensation and cooling, it becomes refrigerant liquid and falls into the lower liquid storage space P of the horizontal cylinder 7. The refrigerant liquid is then discharged in two ways: one way, through the auxiliary liquid supply pipe 12, enters the tube side of the oil cooler 300, where it undergoes heat exchange with the high-temperature lubricating oil from the oil separator 200 in the shell side. The refrigerant liquid absorbs heat from the high-temperature lubricating oil and evaporates. During the evaporation process, the refrigerant liquid gradually decreases in density, generating a pressure differential between the front and rear ends of the tube side due to the different refrigerant densities. This creates a thermosiphon effect within the oil cooler 300, ensuring stable refrigerant flow. The evaporated high-temperature refrigerant gas or gas-liquid mixture then returns to the upper gas storage space S through the return port 2, and this cycle repeats. Another refrigerant liquid flows into the evaporator 500 through the main liquid supply pipe 15, where it evaporates into low-temperature, low-pressure refrigerant gas. It then returns to the intake port of the screw compressor 100, completing the refrigeration cycle. Because there is a height difference H = 150 mm between the auxiliary liquid supply pipe 12 and the main liquid supply pipe 15, and the nozzle plane of the auxiliary liquid supply pipe 12 is lower than the nozzle plane of the main liquid supply pipe 15, the refrigerant liquid in the lower liquid storage space P always prioritizes supply to the oil cooler 300. Only when the liquid level in the lower liquid storage space P exceeds the nozzle plane of the main liquid supply pipe 15 will refrigerant liquid be supplied to the evaporator 500. This ensures that refrigerant is always supplied to the oil cooler 300 during unit operation, and also ensures that the oil cooler 300 returns air normally.

[0041] In summary, with the help of the technical solution of the present invention, the dual-function condenser 400 can have the function of a normal water-cooled condenser while also having the function of a thermal siphon liquid reservoir, that is, it can supply liquid to the oil cooler and return air, thereby eliminating the thermal siphon liquid reservoir, reducing the spatial size of the screw refrigeration unit, adapting to the installation needs of narrow sites, and reducing the refrigerant charge amount, making the unit structure more compact and reasonable, and the unit manufacturing cost lower.

[0042] The above merely describes the preferred embodiments of the present application and is not intended to limit the present application. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1. A dual-function condenser for a thermosyphon screw refrigeration unit, comprising a horizontal cylinder (7), end tube sheets (11) being provided at both ends of the horizontal cylinder (7), a tube box head (1) being provided on the outside of the end tube sheet (11), and a cooling water baffle (10), a cooling water inlet (17) and a cooling water outlet (18) being provided on one of the tube box heads (1), a heat exchange tube bundle (6) being provided in longitudinal direction in the inner cavity of the horizontal cylinder (7) and being connected to the cooling water inlet (17) and the cooling water outlet (18), and both ends of the heat exchange tube bundle (6) being supported on the end tube sheets (11); characterized in that: The heat exchange tube bundle (6) is integrated and arranged in the middle of the inner cavity of the horizontal cylinder (7), thereby dividing the inner cavity of the horizontal cylinder (7) into an upper gas storage space (S) and a lower liquid storage space (P); an air inlet (9) is provided on one side of the top of the horizontal cylinder (7) for receiving high-temperature and high-pressure refrigerant gas from the oil separator (200); a return air port (2) is provided on the other side of the top of the horizontal cylinder (7) for receiving high-temperature refrigerant gas or gas-liquid mixture returned from the oil cooler (300); An auxiliary liquid supply pipe (12) is provided on one side of the bottom of the horizontal cylinder (7) for conveying condensed refrigerant liquid to the oil cooler (300); a main liquid supply pipe (15) is provided on the other side of the bottom of the horizontal cylinder (7) for conveying condensed refrigerant liquid to the evaporator (500); the pipe opening of the auxiliary liquid supply pipe (12) is flush with the inner wall of the bottom of the horizontal cylinder (7), and the pipe opening of the main liquid supply pipe (15) extends into the inner wall of the bottom of the horizontal cylinder (7), thereby forming a height difference (H) between the two pipe openings.

2. The dual-function condenser of the thermosyphon screw refrigeration unit according to claim 1, characterized in that: The height from the bottom inner wall of the horizontal cylinder (7) to the top of the lower liquid storage space (P) is at least 170 mm, and the height difference (H) formed between the two pipe openings is 140-160 mm.

3. The dual-function condenser of the thermosyphon screw refrigeration unit according to claim 2, characterized in that: The height from the bottom inner wall of the horizontal cylinder (7) to the top of the lower liquid storage space (P) is 170 mm, and the height difference (H) formed between the two pipe openings is 150 mm.

4. The dual-function condenser of the thermosyphon screw refrigeration unit according to claim 1, 2 or 3, characterized in that: The air inlet (9) and the auxiliary liquid supply pipe (12) are arranged in a staggered manner, and the air return port (2) and the main liquid supply pipe (15) are arranged in a staggered manner.

5. The dual-function condenser of the thermosyphon screw refrigeration unit according to claim 1, 2 or 3, characterized in that: An anti-collision plate (8) is provided in the upper air storage space (S) of the horizontal cylinder (7) corresponding to the air inlet (9).

6. The dual-function condenser of the thermosyphon screw refrigeration unit according to claim 1, 2 or 3, characterized in that: A gas phase equilibrium interface (5) is provided on the top of the horizontal cylinder (7).

7. The dual-function condenser of the thermosyphon screw refrigeration unit according to claim 1, 2 or 3, characterized in that: A sight glass (14) is provided on the outer wall of the horizontal cylinder (7) corresponding to the lower liquid storage space (P).

8. The dual-function condenser of the thermosyphon screw refrigeration unit according to claim 1, 2 or 3, characterized in that: The top of the horizontal cylinder (7) is provided with a vent valve (3) and a safety valve (4), and the bottom of the horizontal cylinder (7) is provided with a sewage valve (16).

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