Fluorine pump compression refrigeration system with balancing function

Abstract

The application provides a fluorine pump compression refrigeration system with a balancing function, comprising a compressor, an oil separator, a condenser, a liquid storage tank, a fluorine pump, an ejector, an oil return pipeline, a suction pipeline, a first pipeline and a second pipeline. The ejector comprises an inlet end, a suction end and an outlet end. One end of the first pipeline is in communication with the inside of the top end of the liquid storage tank, and the other end is in communication with the inlet end. One end of the oil return pipeline is in communication with the inner bottom of the oil separator, and the other end is in communication with the suction end. One end of the second pipeline is in communication with the suction pipeline, and the other end is in communication with the outlet end. At least part of the gas in the liquid storage tank can be guided back to the suction pipeline through the first pipeline, the ejector and the second pipeline after the compressor stops. According to the application, the pressure between the high pressure and the low pressure of the system can be balanced as soon as possible, and the pressure of the outdoor unit is prevented from rising, so that the refrigerant liquid in the liquid storage tank is prevented from being excessively pressed back to the evaporator of the indoor unit.

Description

Technical Field

[0001] This invention relates to the field of refrigeration technology, and more specifically to a fluorine pump compression refrigeration system with a balancing function. Background Technology

[0002] With the widespread application of 4G and the gradual popularization of 5G, the heat generated by various data processing devices is increasing, and data centers are placing higher and higher demands on the cooling capacity and energy efficiency of their air conditioning equipment.

[0003] Using outdoor natural cold sources during transitional seasons and cold winters to cool data centers can significantly reduce the operating costs of air conditioning equipment. A common approach is to use refrigerant pump air conditioning, which activates the refrigerant pump mode in winter, stops the compressor from running, and uses the refrigerant pump to drive the refrigerant to achieve heat pipe cooling, greatly reducing the operating costs of the equipment.

[0004] The refrigerant pump compression refrigeration system is a composite system. The refrigerant pump heat pipe system shares the evaporator and condenser with the compression refrigeration system, as well as some shared refrigerant pipes and system components.

[0005] In the aforementioned composite system operating under refrigerant pump refrigeration mode, the refrigerant gas at the evaporator outlet may carry a large amount of unevaporated refrigerant liquid. This refrigerant liquid can easily accumulate in the gas pipes before entering the condenser, causing liquid blockage and obstructing the flow of refrigerant gas in certain channels. This affects the uniformity of gas distribution and heat exchange efficiency of the condenser. Liquid blockage also affects the flow resistance of the refrigerant pump's heat pipe circulation, potentially disrupting the pump's stable operation. Therefore, it is necessary to retain the refrigerant liquid at the evaporator outlet to prevent it from returning to the condenser. However, the more refrigerant liquid is retained, the less refrigerant liquid remains in the receiver tank, threatening the reliability of the refrigerant pump. It is crucial to return the retained refrigerant liquid to the system circulation as soon as possible.

[0006] The prior patent application 202211620118.5 describes a gas-liquid separator with a level gauge and an electrically controlled heater. The level gauge detects the liquid level inside the separator, determining the heating power of the heater to vaporize the accumulated liquid and prevent excessive liquid buildup. However, this design wastes energy, directly heats and vaporizes unevaporated refrigerant, wasting cooling capacity and reducing the overall energy efficiency of the system.

[0007] Patent 201320424549.4 uses a gas-liquid separator and a liquid level controller to solve the liquid accumulation problem. It is applied to a power heat pipe system and adopts a delayed start-up method. When there is no liquid in the gas-liquid separator, opening the solenoid valve will cause the gaseous refrigerant to return directly to the pump suction port from the return liquid line, which is an unreasonable control method.

[0008] The aforementioned existing technologies employ multi-functional gas-liquid separators and level controllers, resulting in poor component versatility and complex control schemes. Furthermore, in refrigerant pump compression refrigeration systems, the high and low pressure balancing is too slow after the compressor stops in compression refrigeration mode. This leads to excessive refrigerant liquid in the receiver tank being forced back into the indoor unit's evaporator. Alternatively, during shutdown, the outdoor unit's temperature gradually increases, causing its pressure to rise and further forcing excessive refrigerant liquid back into the indoor unit's evaporator. Excessive refrigerant liquid in the indoor evaporator can cause liquid slugging when the compressor restarts, posing a significant danger to its safe operation. Therefore, the problems of refrigerant liquid retention, transfer, and control in refrigerant pump compression refrigeration systems urgently need to be addressed.

[0009] Because existing refrigerant pump compression refrigeration systems have technical problems such as slow high and low pressure balancing after the compressor stops in compression refrigeration mode, and excessive pressure of refrigerant liquid in the receiver tank being forced back into the evaporator of the indoor unit, this invention studies and designs a refrigerant pump compression refrigeration system with balancing function. Summary of the Invention

[0010] Therefore, the technical problem to be solved by the present invention is to overcome the defects of the prior art fluorine pump compression refrigeration system, which has a slow high and low pressure balance after the compressor stops in the compression refrigeration mode, resulting in excessive pressure of high-pressure refrigerant liquid in the liquid receiver being pushed back to the evaporator of the indoor unit. Thus, a fluorine pump compression refrigeration system with a balancing function is provided.

[0011] To address the above problems, the present invention provides a fluorine pump compression refrigeration system with a balancing function, comprising:

[0012] The system includes a compressor, an oil separator, a condenser, a liquid receiver, a refrigerant pump, an injector, an oil return line, a suction line, a first line, and a second line. The oil separator is connected between the compressor's exhaust port and the condenser. The liquid receiver is connected between the condenser and the refrigerant pump. The compressor's suction port is connected to the suction line. The injector includes an inlet end, a suction end, and an outlet end. One end of the first line connects to the top interior of the liquid receiver, and the other end connects to the inlet end. One end of the oil return line connects to the inner bottom of the oil separator, and the other end connects to the suction end. One end of the second line connects to the suction line, and the other end connects to the outlet end. This allows at least a portion of the gas in the liquid receiver to be returned to the suction line via the first line, the injector, and the second line after the compressor stops.

[0013] In some implementations...

[0014] It also includes a third pipeline, one end of which is connected to the first pipeline and the other end of which is connected to the return oil pipeline. The return oil pipeline, the third pipeline, and the first pipeline can also guide the liquid in the oil separator to the storage tank in the fluorine pump mode.

[0015] In some implementations...

[0016] In compressor operation mode, the injector can guide at least a portion of the gas in the storage tank back to the suction line through the first line, the injector and the second line, and can also inject the fluid in the third line into the first line, and can also draw the fluid in the oil separator through the oil return line.

[0017] In some implementations...

[0018] The third pipeline is connected to the return oil pipeline at a junction. The return oil pipeline is equipped with a throttling device A and a throttling device B. The throttling device A is located between the junction and the oil separator, and the throttling device B is located between the junction and the suction end of the injector.

[0019] In some implementations...

[0020] The third pipeline is connected to the first pipeline at the second junction. A U-shaped bend is also provided on the first pipeline between the second junction and the injector. The U-shaped bend has a first highest point and a second highest point. The first highest point is connected to the inlet end of the injector, and the second highest point is connected to the second junction. The height of the first highest point is lower than the height of the second highest point.

[0021] In some implementations...

[0022] The throttling device A has a capillary structure, and the throttling device B has a capillary structure.

[0023] In some implementations...

[0024] It also includes an evaporator and a throttle valve. The refrigerant pump is connected between the liquid storage tank and the throttle valve. The throttle valve is connected between the evaporator and the refrigerant pump. One end of the evaporator is connected to the throttle valve, and the other end is connected to the suction port of the compressor through the suction pipe.

[0025] In some implementations...

[0026] It also includes a fourth pipeline, which is connected in parallel at both ends of the fluorine pump. The fourth pipeline is equipped with a one-way valve A, which is configured to allow fluid to flow only between the throttle valve and the fluorine pump.

[0027] In some implementations...

[0028] It also includes a fifth pipeline and a one-way valve B. One end of the fifth pipeline is connected to the suction pipeline and is located between the suction port of the compressor and the evaporator. The other end of the fifth pipeline is connected to the discharge port of the compressor. The one-way valve B is located on the fifth pipeline and can only allow fluid to flow from the evaporator to the oil separator.

[0029] In some implementations...

[0030] The oil separator is internally equipped with a liquid-flow-and-gas-blocking structure, which includes a floating structure. The density of the floating structure is lower than that of the liquid in the oil separator, allowing it to float on the liquid surface. The bottom of the oil separator is connected to the return oil pipeline. The height of the floating structure can move up and down with the liquid level. When the liquid level is higher than the bottom of the oil separator, the liquid in the oil separator can support the floating structure, allowing the liquid in the oil separator to enter the return oil pipeline and flow down. At the same time, the floating structure and the liquid prevent gas above the liquid surface from entering the return oil pipeline. When the liquid level drops to the same level as the bottom of the oil separator, the floating structure descends to the bottom of the oil separator, preventing gas entering above the floating structure from entering the return oil pipeline.

[0031] In some implementations...

[0032] A gap exists between the outer peripheral wall of the floating structure and the inner peripheral wall of the oil separator, allowing liquid to pass through the gap from above the floating structure to the space below it; and / or,

[0033] The floating structure is a floating disk, and the liquid-passing and gas-blocking structure also includes a positioning rod. The positioning rod is connected to the lower end of the floating disk and extends downward. The lower end of the positioning rod can be inserted into the return oil pipeline, so that the positioning rod can move up and down in the return oil pipeline as the floating disk floats.

[0034] In some implementations...

[0035] The inner wall of the oil separator is also provided with a blocking structure. One end of the blocking structure is connected to the inner wall of the oil separator, and the other end extends into the internal space of the oil separator. The blocking structure is located above the floating structure so as to limit the highest position of the upward movement of the floating structure.

[0036] In some implementations...

[0037] The blocking structure is a block; there are multiple blocking structures, which are spaced apart on the inner wall of the oil separator; or the blocking structure is an annular structure extending on the inner wall of the oil separator.

[0038] In some implementations...

[0039] When the floating structure is a floating disk, and the liquid-passing and gas-blocking structure further includes a positioning rod: the height of the bottom of the stop block from the upper end of the return oil pipeline is H, the height of the floating disk is D, the length of the positioning rod is L, and HD is present. <L。

[0040] The fluorine pump compression refrigeration system with balancing function provided by this invention has the following beneficial effects:

[0041] 1. This invention, through a first pipeline, one end of which connects to the top of the liquid receiver tank and the other end, via an ejector and a second pipeline, connects to the compressor's suction pipeline. This allows high-pressure gas from the liquid receiver tank to be guided back to the suction pipeline after the compressor stops, effectively forming a gas balance pipeline structure. This ensures that when the compressor stops in refrigeration mode or when the outdoor temperature gradually rises, the high-pressure gas in the high-pressure section of the liquid receiver tank is guided back to the low-pressure section's suction pipeline, effectively achieving rapid pressure balance between the high and low pressures of the system. This prevents excessive refrigerant liquid from being forced back into the indoor unit's evaporator due to increased outdoor unit pressure. It solves the problem of refrigerant liquid migration caused by pressure differences when the compressor stops. Excessive refrigerant liquid in the indoor evaporator can easily cause liquid slugging when the refrigeration compressor restarts. Due to the ejector design, during compressor operation, the high-pressure refrigerant gas in the receiver tank is fully utilized for throttling and pressure reduction within the ejector to eject and draw lubricating oil back to the compressor suction port. When the compressor stops, the high and low pressure difference in the system is quickly balanced through the gas balance pipeline, minimizing the amount of refrigerant liquid from the high-pressure receiver tank entering the evaporator. No changes are needed to the controller hardware and software of the refrigerant pump compression refrigeration system, nor are additional circuit control components and technologies required. The increased cost is minimal, but it effectively solves the problem of refrigerant liquid migration caused by pressure differences when the refrigerant pump compression refrigeration system stops, improving the operational reliability and safety of the refrigerant pump compression refrigeration system.

[0042] 2. This invention also incorporates a third pipeline, allowing the oil return pipeline to connect with the suction pipeline. This enables the liquid (including oil) separated from the oil separator to be returned to the compressor, ensuring its normal operation. Furthermore, in refrigerant pump mode, the liquid in the oil separator can be guided to the liquid receiver via the oil return pipeline, the third pipeline, and the first pipeline, effectively forming a liquid balance pipeline. This effectively solves the problem of liquid shortage in the refrigerant pump and evaporator caused by liquid retention in the oil separator during refrigerant pump compression refrigeration systems in refrigerant pump mode. This achieves both gas and liquid balance functions in the refrigerant pump compression refrigeration system. Moreover, the invention, through the third pipeline, also allows for liquid balance even when the compressor is stopped. The gas entering through the inlet of the ejector is ejected, and the fluid in the third ejector line is drawn into the first ejector line, further increasing the amount of gas returning to the suction line and improving the gas balance effect. Due to the ejector, when the compressor is running, it can also make full use of the throttling and pressure reduction effect of the high-pressure refrigerant gas in the liquid receiver tank within the ejector to eject and draw lubricating oil back to the compressor suction port. There is no need to change the controller hardware and software of the fluorine pump compression refrigeration system, nor is there any need to add special circuit control components and control technology. The increased cost is small, but it can effectively solve the two major problems of the fluorine pump compression refrigeration system and improve the operational reliability and safety of the fluorine pump compression refrigeration system.

[0043] 3. This invention also utilizes a liquid-flow-and-gas-blocking structure within the oil separator to allow only liquid to enter the return oil line while preventing gas from entering. This achieves automatic flow and closure of the liquid balance line, preventing some high-pressure refrigerant gas from bypassing the return oil line and returning to the compressor suction port in an oil-free state. This avoids performance degradation of the compressor, thereby fully utilizing the compressor's output capacity and improving the operating efficiency of the refrigeration system. In refrigerant pump mode, it also prevents some gas from the oil separator from returning to the refrigerant pump from the liquid balance line when there is no liquid, thus avoiding cavitation in the refrigerant pump and ensuring its operational reliability. Attached Figure Description

[0044] Figure 1 This is a system structure diagram of the fluorine pump compression refrigeration system with balancing function of the present invention;

[0045] Figure 2 This is an enlarged structural diagram of the liquid-flow and gas-blocking structure inside the oil separator in the fluorine pump compression refrigeration system of the present invention. Figure 1 (A magnified view of point M in the image).

[0046] The attached figures are labeled as follows:

[0047] 1. Compressor; 2. Oil separator; 3. Condenser; 4. Liquid receiver; 5. Evaporator; 6. Throttling valve; 7. Refrigerant pump; 8. Throttling device A; 9. Throttling device B; 10. Ejector; 10a. Inlet end; 10b. Suction end; 10c. Outlet end; 11. Check valve A; 12. Check valve B; 13. U-bend; 131. First highest point; 132. Second highest point; 100. Oil return line; 200. Suction line; 101. First line; 102. Second line; 103. Third line; 104. Fourth line; 105. Fifth line; O. Joint one; P. Joint two; 15. Liquid flow and gas blockage structure; 16. Floating structure; 17. Positioning rod; 18. Gap; 19. Blocking structure; 20. External fan; 21. Internal fan. Detailed Implementation

[0048] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0049] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0050] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of the invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0051] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0052] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0053] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0054] like Figure 1 and Figure 2 As shown, the present invention provides a fluorine pump compression refrigeration system with a balancing function, comprising:

[0055] The system comprises a compressor 1, an oil separator 2, a condenser 3, a liquid receiver 4, a refrigerant pump 7, an injector 10, an oil return line 100, a suction line 200, a first line 101, and a second line 102. The oil separator 2 is connected between the exhaust port of the compressor 1 and the condenser 3. The liquid receiver 4 is connected between the condenser 3 and the refrigerant pump 7. The suction port of the compressor 1 is connected to the suction line 200. The injector 10 includes an inlet end 10a, a suction end 10b, and an outlet end 10c. One end of the first line 101 can connect to the top of the liquid receiver 4, and the other end can... The oil return pipeline 100 is connected to the inlet end 10a. One end of the oil return pipeline 100 is connected to the inner bottom of the oil separator 2, and the other end is connected to the suction end 10b. One end of the second pipeline 102 is connected to the suction pipeline 200, and the other end is connected to the outlet end 10c. This allows at least a portion of the gas (mainly high-pressure gas) in the liquid storage tank 4 to be returned to the suction pipeline 200 through the first pipeline 101, the ejector 10, and the second pipeline 102 after the compressor 1 stops. The oil separator 2 can also be suctioned through the oil return pipeline 100.

[0056] This invention utilizes a first pipeline, one end of which connects to the top of the liquid receiver tank, and the other end, via an ejector and a second pipeline, connects to the compressor's suction line. This allows the gas in the liquid receiver tank to be guided back to the suction line after the compressor stops, effectively forming a gas balance pipeline structure. This ensures that when the compressor stops in refrigeration mode or when the outdoor temperature gradually rises, the high-pressure gas in the high-pressure section of the liquid receiver tank is guided back to the low-pressure section's suction line. This effectively achieves rapid pressure balance between the high and low pressures of the system, preventing excessive refrigerant liquid from being forced back into the indoor unit's evaporator due to increased outdoor unit pressure. It solves the problem of refrigerant liquid migration caused by pressure differences when the compressor stops, thus addressing the issue of refrigerant liquid migration caused by pressure differences between the high and low pressures. Excessive refrigerant liquid in the internal evaporator can easily cause liquid slugging when the refrigeration compressor restarts. Due to the ejector design, during compressor operation, the high-pressure refrigerant gas in the receiver tank is fully utilized for throttling and pressure reduction within the ejector to eject and draw in lubricating oil, which then returns to the compressor suction port. When the compressor stops, the high and low pressure difference in the system is quickly balanced through the gas balance pipeline, minimizing the amount of refrigerant liquid from the high-pressure receiver tank entering the evaporator. No changes are required to the controller hardware and software of the refrigerant pump compression refrigeration system, nor are additional circuit control components and technologies necessary. The increased cost is minimal, but it effectively solves the problem of refrigerant liquid migration caused by pressure differences when the refrigerant pump compression refrigeration system stops, improving the operational reliability and safety of the refrigerant pump compression refrigeration system.

[0057] In some implementations...

[0058] It also includes a third pipeline 103, one end of which is connected to the first pipeline 101 and the other end of which is connected to the return oil pipeline 100. The return oil pipeline 100, the third pipeline 103 and the first pipeline 101 can also guide the liquid in the oil separator 2 to the storage tank 4 in the fluorine pump mode.

[0059] This invention also incorporates a third pipeline, allowing the oil return pipeline to connect with the suction pipeline. This enables the return of liquid (including oil) separated from the oil separator to the compressor, ensuring its normal operation. Furthermore, in refrigerant pump mode, the liquid in the oil separator can be guided to the receiver tank via the oil return pipeline, the third pipeline, and the first pipeline, effectively forming a liquid balance pipeline. This effectively solves the problem of liquid shortage in the refrigerant pump and evaporator caused by liquid retention in the oil separator during refrigerant pump compression refrigeration systems. This adds gas and liquid balance functions to the refrigerant pump compression refrigeration system. Moreover, the third pipeline, even when the compressor is stopped, allows for gas injection and suction from the third pipeline via the inlet of the ejector, further increasing the amount of gas returning to the suction pipeline and improving the gas balance effect. This requires no changes to the controller hardware or software of the refrigerant pump compression refrigeration system, nor does it require additional circuit control components or technology. The increased cost is minimal but effectively solves two major problems of refrigerant pump compression refrigeration systems, improving their operational reliability and safety.

[0060] In some implementations...

[0061] In compressor operation mode, the ejector 10 can guide at least a portion of the gas in the liquid storage tank 4 back to the suction pipe 200 through the first pipe 101, the ejector 10, and the second pipe 102. It can also inject fluid from the third pipe 101 into the first pipe 101 and draw fluid from the oil separator 2 through the oil return pipe 100. Due to the ejector, this invention also allows the gas entering through the ejector inlet and the fluid from the third pipe to enter the first pipe during compressor operation, further increasing the amount of gas returning to the suction pipe and improving gas balance. It fully utilizes the throttling and pressure reduction effect of the high-pressure refrigerant gas in the liquid storage tank within the ejector to both inject and draw lubricating oil back to the compressor suction port.

[0062] This invention adds only one ejector, one capillary tube, and one U-bend to a conventional refrigerant pump compression refrigeration system, along with modifications to the corresponding connecting pipes. A simple modification to the oil separator is also made to achieve gas and liquid balance functions in the refrigerant pump compression refrigeration system. This requires no changes to the controller hardware or software, nor the addition of specialized circuit control components or technologies. The increased cost is minimal, but it effectively solves two major problems of refrigerant pump compression refrigeration systems, improving their operational reliability and safety. Furthermore, the modified oil separator not only addresses liquid balance issues but also prevents high-pressure refrigerant gas from bypassing the oil return line and returning to the compressor suction port in oil-free conditions, thus fully utilizing the compressor's output capacity.

[0063] The following technical problems were solved:

[0064] 1) The refrigerant pump compression refrigeration system has a high and low pressure difference, which solves the problem of refrigerant liquid migration caused by the pressure difference;

[0065] 2) Liquid shortage caused by liquid retention in the fluorine pump compression refrigeration system in fluorine pump mode, and liquid blockage in the gas pipeline causing a decrease in the refrigeration performance of the fluorine pump.

[0066] like Figure 1 As shown, the refrigerant pump compression refrigeration system of the present invention comprises a compressor, an oil separator, a condenser, a liquid receiver, a refrigerant pump, a throttling valve, and an evaporator connected in sequence; one-way valve A is connected in parallel to bypass the refrigerant pump, and the flow direction of one-way valve A is only allowed from the inlet of the refrigerant pump to the outlet of the refrigerant pump; one-way valve B is connected in parallel to bypass the compressor, and the flow direction of one-way valve B is only allowed from the suction port of the compressor to the discharge port of the compressor; the oil return pipe of the oil separator is connected to the suction port of the compressor through a throttling device A. The above connection relationship constitutes a conventional refrigerant pump compression refrigeration system, but it has at least two unavoidable problems:

[0067] The first problem to be solved is that the high and low pressure balance of the refrigeration system is too slow after the compressor refrigeration cycle stops, which causes excessive refrigerant liquid in the receiver tank to be pushed back to the evaporator of the indoor unit. Alternatively, when the system is off, the outdoor unit's temperature gradually increases, causing the outdoor unit's pressure to rise, which in turn pushes excessive refrigerant liquid in the receiver tank back to the evaporator of the indoor unit. Excessive refrigerant liquid in the indoor evaporator can easily cause liquid slugging when the refrigeration compressor starts, which is very dangerous for the compressor's safe operation. The second problem to be solved is that in the refrigerant pump refrigeration mode, the incompletely evaporated refrigerant liquid at the evaporator outlet enters the oil separator through the one-way valve B. The refrigerant is separated and stored in the oil separator and / or enters the condenser, which increases the flow resistance of the gas pipeline between the evaporator and the condenser and is not conducive to the uniform distribution of gas in the condenser gas distribution pipe assembly. Obviously, the refrigerant liquid that has not been completely evaporated at the evaporator outlet can easily cause the performance of the fluorine pump refrigeration system to degrade. Excessive liquid refrigerant stored in the oil separator will affect the safe operation of the fluorine pump, because insufficient liquid in the liquid tank can easily cause the fluorine pump to operate without liquid, resulting in the risk of cavitation. In fact, if too much liquid refrigerant accumulates in the oil separator, it may block the refrigerant gas from flowing out of the oil separator and into the condenser (that is, if the liquid level in the oil separator is too high, liquid blockage may occur).

[0068] To solve the above two problems, Figure 1 The embodiment modifies the return oil line by adding an ejector, a capillary tube, and a U-bend to a conventional refrigerant pump compression refrigeration system, and adds related connecting lines to provide both gas balance piping (solving the first problem) and liquid balance piping (solving the second problem).

[0069] A series throttling device B is added to the outlet of the throttling device A in the oil return line. A pipeline is led out from the middle of the two capillary tubes and connected to the high inlet of the U-bend. The low outlet of the U-bend is connected to the inlet of the ejector. The outlet of the ejector is connected to the suction port of the compressor, while the outlet of the throttling device B is connected to the ejector inlet. The high-pressure refrigerant gas at the top of the liquid receiver is led out and connected to the high inlet of the U-bend.

[0070] Gas balance pipeline: top of liquid storage tank → U-bend and / or throttling device B → ejector → compressor suction port.

[0071] Liquid balance pipeline: oil separator → throttling device A → top of storage tank.

[0072] Figure 1In the compression refrigeration mode, or when the compressor stops but the high and low pressures of the system are not balanced, the high-pressure refrigerant gas in the system returns to the low-pressure pipeline through the aforementioned gas balance pipeline and enters the evaporator and the compressor suction port. When the compressor is running, it makes full use of the throttling and pressure reduction effect of the high-pressure refrigerant gas in the liquid receiver tank in the ejector to eject and draw lubricating oil back to the compressor suction port. When the compressor stops, the high and low pressure difference of the system is balanced as soon as possible through the gas balance pipeline to minimize the amount of refrigerant liquid in the high-pressure liquid receiver tank entering the evaporator.

[0073] In some implementations...

[0074] The third pipe 103 is connected to the first pipe 101 at the junction point 2P. A U-shaped bend 13 is also provided on the first pipe 101 between the junction point 2P and the injector 10. The U-shaped bend 13 has a first highest point 131 and a second highest point 132. The first highest point 131 is connected to the injector 10, and the second highest point 132 is connected to the junction point 2P. The height of the first highest point 131 is lower than the height of the second highest point 132.

[0075] This invention, through the design of a U-shaped bend, allows only the gas in the storage tank to enter the injector and reach the suction line through the U-shaped bend, preventing the gas in the evaporator from passing through the U-shaped bend in the fluorine pump mode. The U-shaped bend can store part of the liquid flowing in from the oil separator at the bottom, thus forming a liquid seal for the gas flowing from the suction line to the storage tank.

[0076] Figure 1 In the refrigerant pump refrigeration mode, when there is refrigerant liquid at the evaporator outlet, the mixed refrigerant achieves gas-liquid separation inside the oil separator. The gaseous refrigerant enters the condenser after exiting the oil separator, while the separated refrigerant liquid or lubricating oil is stored at the bottom of the oil separator. The liquid inside the oil separator flows through the throttling device A under the suction of the refrigerant pump and returns directly to the top of the liquid receiver, thus achieving liquid balance in the refrigerant pump refrigeration mode and preventing excessive liquid retention inside the oil separator. The liquid from the oil separator outlet pipe reaches the high outlet of the U-shaped bend after passing through the throttling device A. After filling the U-shaped bend, a liquid seal is formed. The refrigerant gas at the evaporator outlet cannot flow backwards from the ejector, thus overcoming the liquid seal and preventing the refrigerant gas from flowing backwards from the ejector. Therefore, the liquid flowing out of the oil separator outlet pipe can only flow to the top of the liquid receiver under the sealing effect of the liquid seal in the U-shaped bend, thus achieving liquid balance circulation.

[0077] 1) Refrigerant flow cycle in compression refrigeration mode: compressor → oil separator → condenser → liquid receiver → check valve A → expansion valve → evaporator → compressor;

[0078] The oil return cycle at this time is: oil separator → throttling device A → throttling device B and / or U-bend → ejector → compressor suction port;

[0079] The gas balance cycle at this time is: top of the liquid storage tank → U-shaped bend → ejector → compressor suction port.

[0080] 2) Refrigeration flow cycle in refrigerant pump refrigeration mode: Refrigerant pump → expansion valve → evaporator → check valve B → oil separator → condenser → liquid receiver → refrigerant pump;

[0081] The liquid balance cycle at this time is: oil separator → throttling device A → top of the storage tank.

[0082] In some implementations...

[0083] The third pipeline 103 is connected to the return oil pipeline 100 at the junction point O. The return oil pipeline 100 is equipped with a throttling device A8 and a throttling device B9. The throttling device A8 is located between the junction point O and the oil separator 2, and the throttling device B9 is located between the junction point O and the suction end 10b of the injector 10.

[0084] This invention utilizes throttling device A to reduce the pressure of the liquid, including oil, flowing down from the oil separator, providing a suitable pressure for its return to the compressor suction line or, in refrigerant pump mode, its return to the receiver tank via a third line. Throttling device B further reduces the pressure of the fluid after reduction by throttling device A, meeting the low-pressure conditions of the compressor suction line. Alternatively, throttling device B can reduce the pressure of gas introduced from the receiver tank via the third line, providing favorable conditions for the ejector to draw more gas back to the suction line, further improving the gas balance effect. In some embodiments,

[0085] The throttling device A8 and the throttling device B9 are both capillary tubes. Both throttling devices A and B of the present invention are preferably capillary tubes, and both can automatically throttle and reduce the pressure of the flowing high-pressure fluid, automatically achieving gas balance in the compressor-off state and liquid balance in refrigerant pump mode of the refrigeration system.

[0086] In some implementations...

[0087] The system also includes an evaporator 5 and a throttling valve 6. The refrigerant pump 7 is connected between the liquid receiver 4 and the throttling valve 6. The throttling valve 6 is connected between the evaporator 5 and the refrigerant pump 7. One end of the evaporator 5 is connected to the throttling valve 6, and the other end is connected to the suction port of the compressor 1 through the suction pipe 200. This invention, through the arrangement of the evaporator and the throttling valve, enables the evaporator to evaporate the refrigerant, ensuring a cooling effect for the room or desired environment.

[0088] In some implementations...

[0089] It also includes a fourth pipeline 104, which is connected in parallel at both ends of the fluorine pump 7. A one-way valve A11 is provided on the fourth pipeline 104, which is configured to allow fluid to flow only between the throttle valve 6 and the fluorine pump 7.

[0090] The one-way valve A installed on the fourth pipeline of the present invention can effectively ensure that the fluid at the outlet of the fluorine pump will not flow back to the inlet of the fluorine pump in the fluorine pump mode.

[0091] In some implementations...

[0092] It also includes a fifth pipeline 105 and a one-way valve B12. One end of the fifth pipeline 105 is connected to the suction pipeline 200 and located between the suction port of the compressor 1 and the evaporator 5. The other end of the fifth pipeline 105 is connected to the discharge port of the compressor 1. The one-way valve B12 is installed on the fifth pipeline 105 and only allows fluid to flow from the evaporator 5 to the oil separator 2. This invention also allows bypassing of the compressor in refrigerant pump mode via the fifth pipeline and the one-way valve B, but it ensures that the fluid from the evaporator flows to the oil separator, preventing the gas discharged from the compressor in compression mode from flowing back to the compressor suction port, thus ensuring normal operation in compression mode.

[0093] The refrigerant flow cycle of the two different operating modes of the present invention is as follows:

[0094] 1) Refrigerant flow cycle in compression refrigeration mode: compressor → oil separator → condenser → liquid receiver → check valve A → expansion valve → evaporator → compressor;

[0095] The oil return cycle at this time is: oil separator → throttling device A → throttling device B and / or U-bend → ejector → compressor suction port;

[0096] The gas balance cycle at this time is: top of the liquid storage tank → U-shaped bend → ejector → compressor suction port.

[0097] 2) Refrigeration flow cycle in refrigerant pump refrigeration mode: Refrigerant pump → expansion valve → evaporator → check valve B → oil separator → condenser → liquid receiver → refrigerant pump;

[0098] The liquid balance cycle at this time is: oil separator → throttling device A → top of the storage tank.

[0099] In some implementations...

[0100] The oil separator 2 is internally equipped with a liquid-passing and gas-blocking structure 15, which includes a floating structure 16. The density of the floating structure 16 is lower than that of the liquid in the oil separator 2, so that it can float on the surface of the liquid. The bottom of the oil separator 2 is connected to the return oil pipeline 100. The height of the floating structure 16 can move up and down with the liquid level. When the liquid level is higher than the bottom of the oil separator 2, the liquid in the oil separator 2 can support the floating structure 16 and float on the liquid surface, allowing the liquid in the oil separator 2 to enter the return oil pipeline 100 and flow down. At the same time, the floating structure 16 and the liquid prevent gas above the liquid surface from entering the return oil pipeline 100. When the liquid level drops to the same level as the bottom of the oil separator 2, the floating structure 16 descends to the bottom of the oil separator 2, preventing gas above the floating structure 16 from entering the return oil pipeline 100.

[0101] This invention also incorporates a liquid-flow-and-gas-blocking structure within the oil separator. This structure, with a density less than that of liquid, floats on the liquid level and rises and falls with the liquid level. This allows only liquid to enter the return oil line while preventing gas from entering, thus achieving automatic flow and closure of the liquid balance line. It prevents high-pressure refrigerant gas from bypassing the return oil line and returning to the compressor suction port in an oil-free state, avoiding compressor performance degradation and fully utilizing the compressor's output capacity to improve the operating efficiency of the refrigeration system. The oil separator in the liquid balance line of this invention features a floating structure with liquid-flow-and-gas-blocking capability, thereby achieving automatic flow and closure of the liquid balance line.

[0102] The oil separator of this invention is preferably designed with a liquid-passing, gas-blocking structure (allowing liquid to pass through but preventing gas flow), as detailed in the following figure. Figure 2 As shown in the enlarged diagram M, its basic design principle is to use a low-density material in a high-density oil where the buoyancy is greater than the gravity, causing the low-density material to float to the surface and thus open the inlet of the return oil pipe at the bottom of the oil separator. When the amount of oil separated and retained inside the oil separator is insufficient, the buoyancy of the low-density material is not enough to overcome the gravity. Therefore, the low-density material sinks under the action of gravity and blocks the inlet of the return oil pipe, thereby preventing the gaseous refrigerant from returning from the liquid balance pipeline to the inlet of the refrigerant pump. This ensures that most of the refrigerant gas enters the condenser for cooling and liquefaction, achieving a normal refrigerant pump refrigeration cycle.

[0103] Therefore, the oil separator with a floating structure of the present invention has the function of liquid flow blocking gas. When the oil separator is used in a conventional compression refrigeration system or compression refrigeration mode, when the lubricating oil in the oil separator is insufficient, it can prevent part of the high-pressure refrigerant gas from bypassing back to the compressor suction port from the oil return line of the oil separator, thereby making efficient use of the compressor's exhaust output and avoiding a decrease in the capacity of the compression refrigeration system; conventional oil separators cannot solve the problem of refrigerant bypass leakage to the compressor suction port in the oil-free state.

[0104] In some implementations...

[0105] A gap 18 is provided between the outer peripheral wall of the floating structure 16 and the inner peripheral wall of the oil separator 2, allowing liquid to pass through the gap 18 from above the floating structure 16 to the space below the floating structure 16; and / or,

[0106] The floating structure 16 is a floating disk, and the liquid-passing and gas-blocking structure 15 also includes a positioning rod 17. The positioning rod 17 is connected to the lower end of the floating disk and extends downward. The lower end of the positioning rod 17 can be inserted into the return oil pipeline 100, so that the positioning rod 17 can move up and down in the return oil pipeline 100 as the floating disk floats.

[0107] The floating structure of the present invention preferably has a gap between its outer peripheral wall and the inner peripheral wall of the oil separator, allowing liquid to enter the lower part of the floating structure through the gap, ensuring that the liquid can enter the return oil pipeline, and allowing the floating structure to float upward by the rise of the liquid level, thus realizing the liquid discharge passage; the floating structure of the present invention is preferably a floating plate structure, with a positioning rod structure connected to the lower end of the floating plate. The positioning rod can be inserted into the return oil pipeline, ensuring that the liquid-passing and gas-blocking structure is positioned by the positioning rod during the up-and-down floating process of the floating plate, preventing the floating plate from tilting, tipping or overturning, and ensuring that the floating plate always floats normally on the liquid level surface.

[0108] like Figure 2 As shown, the oil separator cylinder of the present invention is provided with a floating plate that matches the cross-section of the oil separator cylinder. A gap is left between the floating plate and the inner cavity of the oil separator cylinder, so that the oil separated by the oil separator flows into the lower part of the floating plate through the gap between the two.

[0109] The bottom of the floating roof of the present invention is preferably provided with a positioning rod, which is inserted into the return oil pipe and forms a large clearance fit with the return oil pipe, so that the oil can enter the return oil pipe through this large clearance.

[0110] Preferably, the density of the overall structure of the floating roof and positioning rod made of different material densities after they are fixed together is less than the density of the lubricating oil, liquid refrigerant and oil mixture at the highest operating temperature (that is, to ensure that the density of the three is greater than the density of the floating roof and positioning rod). Here, the oil mixture specifically refers to the liquid in which the lubricating oil and liquid refrigerant are miscible (the mixing ratio varies).

[0111] Preferably, the densities of the floating roof and the positioning rod are both less than the densities of the lubricating oil, liquid refrigerant, and oil mixture at the highest operating temperature;

[0112] Preferably, the floating roof and the positioning rod are integrally formed from the same low-density material, the density of which is less than the density of the lubricating oil, liquid refrigerant and oil mixture at the highest operating temperature;

[0113] Preferably, both the floating roof and the positioning rod can be made of metal to form a hollow, sealed structure, thereby reducing the overall density of the structure. This metal material does not react physically and / or chemically with the lubricating oil and refrigerant, for example, aluminum and / or aluminum alloys are used. The sealed structure means that without damaging the structure, the liquid and / or gas inside the oil separator cavity cannot enter the internal cavity of the hollow structure, thus giving the hollow metal floating roof structure a stable overall low density.

[0114] The oil separator of this invention, with its floating disc structure, has a liquid-flow-and-gas-blocking function. When used in a conventional compression refrigeration system or in compression refrigeration mode, this oil separator can prevent some high-pressure refrigerant gas from bypassing the oil return line of the oil separator and returning to the compressor suction port when the lubricating oil in the oil separator is insufficient. This allows for efficient utilization of the compressor's exhaust output and avoids a decrease in the capacity of the compression refrigeration system. Conventional oil separators cannot solve the problem of refrigerant bypass leakage to the compressor suction port in an oil-free state.

[0115] In some implementations...

[0116] The inner wall of the oil separator 2 is also provided with a blocking structure 19. One end of the blocking structure 19 is connected to the inner wall of the oil separator 2, and the other end extends toward the internal space of the oil separator 2. The blocking structure 19 is located above the floating structure 16 so as to limit the highest position of the upward movement of the floating structure 16.

[0117] The present invention also uses a blocking structure extending inward on the inner wall of the oil separator to limit the highest position of the floating structure's upward movement, preventing the floating structure from rising too high and affecting the normal operation of the fluid entering the inlet pipe and the gas exiting the outlet pipe above the oil separator, thus ensuring that there is enough space above to achieve normal gas-liquid separation.

[0118] In some implementations...

[0119] The blocking structure 19 is a block; there are multiple blocking structures 19, and the multiple blocking structures 19 are distributed at intervals on the inner wall of the oil separator 2; or the blocking structure 19 is an annular structure extending on the inner wall of the oil separator 2.

[0120] This is a preferred structural form of the blocking structure of the present invention. The blocking structure can be a plurality of spaced blocks that can limit the upward movement of the floating structure, or it can be a complete ring structure that can also limit the upward movement of the floating structure.

[0121] In this invention, at least one baffle is preferably provided on the upper part of the floating roof and the inner wall of the oil separator cylinder. The baffle can prevent the floating roof from rising further, thereby ensuring that the upper part of the oil separator has a sufficient gas-liquid separation area. The baffle can be a component fixed to the cylinder wall by welding or other means, or it can be an inwardly protruding bulge formed on the cylinder wall by machining or other means.

[0122] In some implementations...

[0123] When the floating structure 16 is a floating disk, and the liquid-passing and gas-blocking structure 15 further includes a positioning rod 17: the height of the bottom of the stop block from the upper end of the return oil pipeline 100 is H, the height of the floating disk is D, the length of the positioning rod 17 is L, and HD is present. <L。

[0124] This is the preferred dimensional relationship between the height H of the blocking structure, the length L of the positioning rod, and the height (or thickness) D of the floating roof in this invention. This ensures that even when the floating roof reaches its highest position, i.e., when it contacts the stop block, at least a portion of the positioning rod remains inserted into the return oil pipe, guaranteeing effective positioning and guidance for the floating roof's vertical movement. When the floating roof rises and abuts against the lower part of the stop block, preventing further upward movement, at least a portion of the positioning rod at the bottom of the floating roof remains inserted into the return oil pipe. This ensures that when the floating roof sinks again, the positioning rod can re-insert into the return oil pipe, guaranteeing that the floating roof and positioning rod can function normally again. Figure 2 The dimensional relationships in HD satisfy: <L。

[0125] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention. The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the protection scope of the present invention.

Claims

1. A fluorine pump compression refrigeration system with balancing function, characterized in that: include: The compressor (1), oil separator (2), condenser (3), liquid receiver (4), refrigerant pump (7), injector (10), return oil line (100), suction line (200), first line (101) and second line (102) are connected. The oil separator (2) is connected between the exhaust port of the compressor (1) and the condenser (3). The liquid receiver (4) is connected between the condenser (3) and the refrigerant pump (7). The suction port of the compressor (1) is connected to the suction line (200). The injector (10) includes an inlet end (10a), a suction end (10b) and an outlet end (10c). The first line (101) One end of the first pipeline (101) can be connected to the top interior of the liquid storage tank (4) and the other end can be connected to the inlet end (10a). One end of the return oil pipeline (100) is connected to the inner bottom of the oil separator (2) and the other end can be connected to the suction end (10b). One end of the second pipeline (102) is connected to the suction pipeline (200) and the other end is connected to the outlet end (10c), so that at least part of the gas in the liquid storage tank (4) can be guided back to the suction pipeline (200) through the first pipeline (101), the ejector (10) and the second pipeline (102) after the compressor (1) stops.

2. The fluorine pump compression refrigeration system with balancing function according to claim 1, characterized in that: It also includes a third pipeline (103), one end of which is connected to the first pipeline (101) and the other end is connected to the return oil pipeline (100). The return oil pipeline (100), the third pipeline (103) and the first pipeline (101) can also guide the liquid in the oil separator (2) to the storage tank (4) in the fluorine pump mode.

3. The fluorine pump compression refrigeration system with balancing function according to claim 2, characterized in that: In compressor operation mode, at least a portion of the gas in the storage tank (4) is guided back to the suction line (200) through the first line (101), the ejector (10) and the second line (102), and the fluid in the third line (103) can also be injected into the first line (101), and the fluid in the oil separator (2) can also be drawn through the return oil line (100).

4. The fluorine pump compression refrigeration system with balancing function according to claim 2, characterized in that: The third pipeline (103) is connected to the return oil pipeline (100) at the junction (O). The return oil pipeline (100) is provided with a throttling device A (8) and a throttling device B (9). The throttling device A (8) is located between the junction (O) and the oil separator (2). The throttling device B (9) is located between the junction (O) and the suction end (10b) of the injector (10).

5. The fluorine pump compression refrigeration system with balancing function according to claim 2, characterized in that: The third pipe (103) is connected to the first pipe (101) at the second junction (P). A U-shaped bend (13) is also provided on the first pipe (101) between the second junction (P) and the injector (10). The U-shaped bend (13) has a first highest point (131) and a second highest point (132). The first highest point (131) is connected to the inlet end (10a) of the injector (10), and the second highest point (132) is connected to the second junction (P). The height of the first highest point (131) is lower than the height of the second highest point (132).

6. The fluorine pump compression refrigeration system with balancing function according to claim 4, characterized in that: The throttling device A (8) has a capillary structure, and the throttling device B (9) has a capillary structure.

7. The fluorine pump compression refrigeration system with balancing function according to claim 1, characterized in that: It also includes an evaporator (5) and a throttle valve (6). The fluorine pump (7) is connected between the liquid storage tank (4) and the throttle valve (6). The throttle valve (6) is connected between the evaporator (5) and the fluorine pump (7). One end of the evaporator (5) is connected to the throttle valve (6), and the other end is connected to the suction port of the compressor (1) through the suction pipe (200).

8. The fluorine pump compression refrigeration system with balancing function according to claim 7, characterized in that: It also includes a fourth pipeline (104), which is connected in parallel at both ends of the fluorine pump (7). A one-way valve A (11) is provided on the fourth pipeline (104), which is configured to allow fluid to flow only between the throttle valve (6) and the fluorine pump (7).

9. The fluorine pump compression refrigeration system with balancing function according to claim 7, characterized in that: It also includes a fifth pipe (105) and a one-way valve B (12). One end of the fifth pipe (105) is connected to the suction pipe (200) and located between the suction port of the compressor (1) and the evaporator (5). The other end of the fifth pipe (105) is connected to the discharge port of the compressor (1). The one-way valve B (12) is provided on the fifth pipe (105) and can only allow fluid to flow from the evaporator (5) to the oil separator (2).

10. The fluorine pump compression refrigeration system with balancing function according to any one of claims 1-9, characterized in that: The oil separator (2) is internally equipped with a liquid-passing and gas-blocking structure (15), which includes a floating structure (16). The density of the floating structure (16) is lower than that of the liquid in the oil separator (2), so that it can float on the surface of the liquid. The bottom of the oil separator (2) is connected to the return oil pipeline (100). The height of the floating structure (16) can move up and down with the liquid level. When the liquid level is higher than the bottom of the oil separator (2), the liquid in the oil separator (2) can support the flow of the liquid. The floating structure (16) floats on the liquid surface, allowing the liquid in the oil separator (2) to enter the return oil line (100) and flow down. At the same time, the floating structure (16) and the liquid prevent gas above the liquid surface from entering the return oil line (100). When the liquid level drops to the bottom of the oil separator (2), the floating structure (16) descends to the bottom of the oil separator (2), preventing gas above the floating structure (16) from entering the return oil line (100).

11. The fluorine pump compression refrigeration system with balancing function according to claim 10, characterized in that: A gap (18) exists between the outer peripheral wall of the floating structure (16) and the inner peripheral wall of the oil separator (2) to allow liquid to pass through the gap (18) from above the floating structure (16) into the space below the floating structure (16); and / or, The floating structure (16) is a floating disk, and the liquid-passing and gas-blocking structure (15) also includes a positioning rod (17). The positioning rod (17) is connected to the lower end of the floating disk and extends downward. The lower end of the positioning rod (17) can be inserted into the return oil pipeline (100), so that the positioning rod (17) can move up and down in the return oil pipeline (100) as the floating disk floats.

12. The fluorine pump compression refrigeration system with balancing function according to claim 10, characterized in that: The inner wall of the oil separator (2) is also provided with a blocking structure (19). One end of the blocking structure (19) is connected to the inner wall of the oil separator (2), and the other end extends toward the internal space of the oil separator (2). The blocking structure (19) is located above the floating structure (16) so as to limit the highest position of the upward movement of the floating structure (16).

13. The fluorine pump compression refrigeration system with balancing function according to claim 12, characterized in that: The blocking structure (19) is a block; there are multiple blocking structures (19), and multiple blocking structures (19) are distributed at intervals on the inner wall of the oil separator (2); or the blocking structure (19) is an annular structure extending on the inner wall of the oil separator (2).

14. The fluorine pump compression refrigeration system with balancing function according to claim 12, characterized in that: When the floating structure (16) is a floating disk, and the liquid-passing and gas-blocking structure (15) further includes a positioning rod (17): the height of the bottom of the blocking structure from the upper end of the return oil pipeline (100) is H, the height of the floating disk is D, the length of the positioning rod (17) is L, and HD <L。

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