A dual-temperature-zone refrigeration system and air conditioner
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- GREE ELECTRIC APPLIANCE INC OF ZHUHAI
- Filing Date
- 2025-06-25
- Publication Date
- 2026-06-12
AI Technical Summary
Traditional dual-zone refrigeration systems suffer from problems such as large throttling losses, high compressor compression ratios, high compressor strength requirements, and unstable system operation.
A dual-ejector structure is formed by using a first ejector and a second ejector to recover the high-pressure fluid energy at the condenser outlet. Combined with a gas-liquid separator and a check valve, the control valve mechanism enables independent operation of the two temperature zones.
Reduce throttling losses, improve system energy efficiency, lower compressor compression ratio, extend compressor life, and improve low-temperature refrigeration effect.
Smart Images
Figure CN224353330U_ABST
Abstract
Description
Technical Field
[0001] This utility model belongs to the field of refrigeration and air conditioning technology, specifically relating to a dual-temperature zone refrigeration system and an air conditioner. Background Technology
[0002] Traditional dual-zone refrigeration systems use a vapor compression refrigeration cycle, which suffers from significant throttling losses on the low-temperature side. Furthermore, the compressor typically has a high compression ratio, placing high demands on the compressor's strength and hindering stable system operation. Utility Model Content
[0003] Therefore, this utility model provides a dual-temperature zone refrigeration system and an air conditioner. The main technical problem to be solved is: how to reduce the throttling loss of the dual-temperature zone refrigeration system and improve the system energy efficiency.
[0004] To address the aforementioned problems, this utility model provides a dual-temperature zone refrigeration system, comprising a compressor, a condenser, a first ejector, a second ejector, a high-temperature evaporator, a low-temperature evaporator, and a first gas-liquid separator. The compressor has an exhaust port and an intake port. The first gas-liquid separator has a first inlet, a first liquid outlet, and a first gas outlet. The exhaust port is connected to one end of the condenser, and the other end of the condenser is connected to the working fluid inlets of both the first and second ejectors. The outlet of the first ejector is connected to the first inlet. The first liquid outlet is connected to one end of the high-temperature evaporator and one end of the low-temperature evaporator respectively through a first throttling device. The other end of the high-temperature evaporator and the outlet of the second ejector are both connected to the ejector fluid inlet of the first ejector, and the other end of the low-temperature evaporator is connected to the ejector fluid inlet of the second ejector.
[0005] In some embodiments, the outlet of the second injector is connected to the ejector fluid inlet of the first injector via a second gas-liquid separator;
[0006] The second gas-liquid separator has a second inlet and a second gas outlet. The second gas-liquid separator is connected to the outlet of the second ejector through the second inlet, and the second gas-liquid separator is connected to the ejector fluid inlet of the first ejector through the second gas outlet.
[0007] In some embodiments, the second gas-liquid separator further has a second liquid outlet, which is connected to one end of the low-temperature evaporator via a second throttling device.
[0008] In some embodiments, the first throttling device is connected to one end of the low-temperature evaporator via the second throttling device;
[0009] The second liquid outlet is connected to the flow path between the first throttling device and the second throttling device, and a one-way valve is provided in the flow path of the second liquid outlet to prevent fluid backflow in the flow path of the second liquid outlet.
[0010] In some embodiments, the dual-temperature zone refrigeration system further includes a valve mechanism for controlling whether the high-temperature evaporator and the low-temperature evaporator operate independently.
[0011] In some embodiments, the valve mechanism includes a first switching valve, which is disposed in the flow path at one end of the high-temperature evaporator or in the flow path at the other end of the high-temperature evaporator. The valve mechanism controls the operation or non-operation of the high-temperature evaporator through the first switching valve.
[0012] In some embodiments, the valve mechanism includes a second switching valve disposed in the flow path of the working fluid inlet of the second injector, and the valve mechanism controls the operation or non-operation of the cryogenic evaporator through the second switching valve.
[0013] This utility model also provides an air conditioner, which includes the dual-temperature zone refrigeration system described in any one of the above descriptions.
[0014] The dual-temperature zone refrigeration system and air conditioner provided by this utility model have the following beneficial effects:
[0015] 1. This utility model uses a first ejector and a second ejector to form a dual ejector, so as to recover the energy of the high-pressure fluid at the condenser outlet, reduce throttling losses, and the two-stage injection can increase the suction pressure of the compressor during low-temperature refrigeration, reduce the compression ratio of the compressor, and reduce the operating load of the compressor.
[0016] 2. This utility model arranges gas-liquid separators at the outlets of both injectors. The first gas-liquid separator is used to separate the refrigerant into a gas flow path and a liquid flow path, enabling the system to perform a refrigeration cycle. The second gas-liquid separator is used to ensure that the jet stream of the first injector is gas, avoiding liquid in the jet stream from affecting the ejection effect of the injector. At the same time, a one-way valve is introduced at the liquid outlet of the second gas-liquid separator to prevent refrigerant backflow.
[0017] 3. This utility model enables independent operation of refrigeration in two temperature zones by arranging and controlling the flow path and the first and second switching valves, and the low-temperature refrigeration side always performs two-stage injection, thereby improving the low-temperature refrigeration effect. Attached Figure Description
[0018] To more clearly illustrate the embodiments of this utility model or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. The drawings in the following description are merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.
[0019] Figure 1 This is a structural diagram of the first mode of the dual-temperature zone refrigeration system of this utility model;
[0020] Figure 2 This is the pressure-enthalpy diagram of Mode 1 of the dual-temperature zone refrigeration system of this utility model;
[0021] Figure 3 This is a structural diagram of Mode 2 of the dual-temperature zone refrigeration system of this utility model;
[0022] Figure 4 This is the pressure-enthalpy diagram of Mode 2 of the dual-temperature zone refrigeration system of this utility model;
[0023] Figure 5 This is a structural diagram of Mode 3 of the dual-temperature zone refrigeration system of this utility model;
[0024] Figure 6 This is the pressure-enthalpy diagram of Mode 3 of the dual-temperature zone refrigeration system of this utility model;
[0025] Figure 7 This is a structural diagram of the first injector of this utility model;
[0026] Figure 8 This is a structural diagram of the second injector of this utility model.
[0027] The attached figures are labeled as follows:
[0028] 001. Compressor; 002. Condenser; 003. First ejector; 004. First gas-liquid separator; 005. First throttling device; 006. First switching valve; 007. High-temperature evaporator; 008. Second switching valve; 009. Second ejector; 010. Second gas-liquid separator; 011. Second throttling device; 012. Low-temperature evaporator; 013. One-way valve; 1a. Exhaust port; 1b. Suction port; 2a. One end of the condenser; 2b. The other end of the condenser; 31. Working fluid inlet of the first ejector; 32. Ejector fluid inlet of the first ejector; 33. Outlet of the first ejector; 4a. First inlet; 4b. First liquid outlet; 4c. First gas outlet; 7a. One end of the high-temperature evaporator; 7b. The other end of the high-temperature evaporator; 91. Working fluid inlet of the second ejector; 92. Second ejector 93. The outlet of the second ejector; 10a. The second inlet; 10b. The second liquid outlet; 10c. The second gas outlet; 12a. One end of the cryogenic evaporator; 12b. The other end of the cryogenic evaporator; 1. The first flow channel; 2. The second flow channel; 3. The third flow channel; 4. The fourth flow channel; 5. The fifth flow channel; 6. The sixth flow channel; 7. The seventh flow channel; 8. The eighth flow channel; 9. The ninth flow channel; 10. The tenth flow channel; 11. The eleventh flow channel; 12. The twelfth flow channel; 13. The thirteenth flow channel; 14. The fourteenth flow channel; 3a. The nozzle of the first ejector; 3b. The ejector chamber of the first ejector; 3m. The mixing chamber of the first ejector; 3n. The diffuser chamber of the first ejector; 9a. The nozzle of the second ejector; 9b. The ejector chamber of the second ejector; 9m. The mixing chamber of the second ejector; 9n. The diffuser chamber of the second ejector. Detailed Implementation
[0029] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, 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 utility model or its application or use. All other embodiments obtained by those skilled in the art based on the embodiments of the present utility model without creative effort are within the scope of protection of the present utility model.
[0030] In the description of this utility model, it should be understood that the directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model 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 utility model. The directional terms "inner" and "outer" refer to the inner and outer contours of each component itself.
[0031] 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.
[0032] 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 cannot be construed as limiting the scope of protection of this utility model.
[0033] See also Figure 1-8As shown, according to an embodiment of the present invention, a dual-temperature zone refrigeration system is provided, comprising a compressor 001, a condenser 002, a first ejector 003, a second ejector 009, a high-temperature evaporator 007, a low-temperature evaporator 012, and a first gas-liquid separator 004. The compressor 001 has an exhaust port 1a and an intake port 1b. The first gas-liquid separator 004 has a first inlet 4a, a first liquid outlet 4b, and a first gas outlet 4c. The exhaust port 1a of the compressor 001 is connected to one end 2a of the condenser. The other end 2b of the condenser is connected to both the working fluid inlet 31 of the first ejector and the working fluid inlet 91 of the second ejector. The outlet 33 of the first ejector is connected to the first inlet 4a of the first gas-liquid separator. The first liquid outlet 4b of the first gas-liquid separator is connected to one end 7a of the high-temperature evaporator and one end 12a of the low-temperature evaporator via a first throttling device 005. The other end 7b of the high-temperature evaporator and the outlet 93 of the second ejector are both connected to the ejector fluid inlet 32 of the first ejector. The other end 12b of the low-temperature evaporator is connected to the ejector fluid inlet 92 of the second ejector.
[0034] Among them, the high-temperature evaporator 007 and the low-temperature evaporator 012 have different operating temperatures, with the high-temperature evaporator 007 operating at a higher temperature than the low-temperature evaporator 012.
[0035] In the example above, the high-pressure fluid exiting condenser 002, acting as the working fluid, expands and depressurizes within the first ejector 003 and the second ejector 009, attracting the entrained fluid. This increases the refrigerant flow rate on the entrained fluid side, i.e., the refrigerant flow rate of both the high-temperature evaporator 007 and the low-temperature evaporator 012, while simultaneously increasing the suction pressure of compressor 001 to reduce the compression ratio. In a system without ejectors, the high-pressure fluid exiting condenser 002 directly throttles before entering the evaporator for heat exchange, resulting in significant throttling losses. Therefore, the system with ejectors can recover some of the expansion work of the high-pressure fluid exiting condenser 002, reducing throttling losses and decreasing the compression ratio. During low-temperature refrigeration, the evaporation pressure is low. Direct compression would not only result in a high compression ratio for compressor 001 but also lead to a smaller actual flow rate for compressor 001 due to the lower refrigerant density at low pressure, affecting the refrigeration effect and increasing the load on compressor 001. Therefore, the dual-ejector structure formed by the first ejector 003 and the second ejector 009 can further increase the suction pressure of compressor 001.
[0036] In summary, the combination of the first ejector 003 and the second ejector 009 can recover the energy of the high-temperature and high-pressure fluid at the outlet of the condenser 002, reduce the throttling loss of the dual-temperature zone refrigeration system of this utility model, and improve the system energy efficiency. Furthermore, the dual-stage injection formed by the combination of the first ejector 003 and the second ejector 009 can also increase the suction pressure of the compressor 001, reduce the compression ratio of the compressor 001 during low-temperature refrigeration, reduce energy consumption, and extend the service life of the compressor 001.
[0037] The first gas-liquid separator 004 can divide the refrigerant at the outlet 33 of the first injector into a gas flow path and a liquid flow path, enabling the system to perform a high-efficiency refrigeration cycle.
[0038] In some implementations, such as Figure 1 As shown, the outlet 93 of the aforementioned second injector can be connected to the ejector fluid inlet 32 of the first injector via the second gas-liquid separator 010. The second gas-liquid separator 010 has a second inlet 10a and a second gas outlet 10c. The second gas-liquid separator 010 is connected to the outlet 93 of the second injector via the second inlet 10a, and the second gas-liquid separator 010 is connected to the ejector fluid inlet 32 of the first injector via the second gas outlet 10c.
[0039] In the above example, the second gas-liquid separator 010 can ensure that the ejector flow of the first ejector 003 is a gas without liquid, because the density of liquid is relatively high, and liquid in the ejector fluid will affect the ejection effect of the first ejector 003.
[0040] In some implementations, such as Figure 1 As shown, the aforementioned second gas-liquid separator 010 also has a second liquid outlet 10b, which is connected to one end 12a of the low-temperature evaporator through a second throttling device 011 to divert the separated liquid to the low-temperature evaporator 012 for heat exchange, thereby improving the heat exchange effect of the low-temperature evaporator 012.
[0041] In some implementations, such as Figure 1 As shown, the aforementioned first throttling device 005 is connected to one end 12a of the low-temperature evaporator via the aforementioned second throttling device 011. The second liquid outlet 10b of the second gas-liquid separator 010 is connected to the flow path between the first throttling device 005 and the second throttling device 011. A one-way valve 013 is provided in the flow path of the second liquid outlet 10b to prevent backflow of fluid within the flow path of the second liquid outlet 10b.
[0042] In the above example, the one-way valve 013 can prevent the refrigerant at the outlet of the first throttling device 005 from flowing back into the second gas-liquid separator 010.
[0043] The aforementioned structures of the first ejector 003 and the second ejector 009 are both prior art. In the ejector, the "working fluid" refers to the high-pressure fluid that expands and depressurizes in the working nozzle of the ejector, reducing the pressure to below that of the ejector fluid, to attract the "ejector fluid." The "ejector fluid" refers to the fluid that is drawn into the ejector due to the pressure difference. The first ejector 003 and the second ejector 009 have the same structure, as shown below. Figure 7 As shown, the first injector 003 has a nozzle 3a, an ejector chamber 3b, a mixing chamber 3m, and a diffuser chamber 3n. (As shown...) Figure 8 As shown, the second injector 009 has a nozzle 9a, an ejector chamber 9b, a mixing chamber 9m, and a diffuser chamber 9n.
[0044] In some embodiments, the aforementioned dual-temperature zone refrigeration system may further include a valve mechanism for controlling whether the high-temperature evaporator 007 and the low-temperature evaporator 012 operate or not.
[0045] In the example above, since the valve mechanism can control the high-temperature evaporator 007 and the low-temperature evaporator 012 to work or not work, the refrigeration of both temperature zones can be operated independently to adapt to different working conditions.
[0046] To achieve the aforementioned function of controlling the operation or non-operation of the high-temperature evaporator 007 via the valve mechanism, in some embodiments, such as... Figure 1 As shown, the valve mechanism may include a first switching valve 006, which is disposed on the flow path at one end 7a of the high-temperature evaporator or on the flow path at the other end 7b of the high-temperature evaporator. The valve mechanism controls the high-temperature evaporator 007 to work or not work through the first switching valve 006.
[0047] In the above example, the first switching valve 006 can be a solenoid valve, etc. The first switching valve 006 can open the flow path of the high-temperature evaporator 007, so that the high-temperature evaporator 007 can work; the first switching valve 006 can also close the flow path of the high-temperature evaporator 007, so that the high-temperature evaporator 007 cannot work.
[0048] To achieve the aforementioned function of controlling the operation or non-operation of the low-temperature evaporator 012 via the valve mechanism, in some embodiments, such as... Figure 1 As shown, the aforementioned valve mechanism may include a second switching valve 008, which is disposed in the flow path of the working fluid inlet 91 of the second injector. The valve mechanism controls the operation or non-operation of the low-temperature evaporator 012 through the second switching valve 008.
[0049] In the above example, the second switching valve 008 can be a solenoid valve, etc. The second switching valve 008 can open the flow path of the working fluid inlet 91 of the second injector, so that the low-temperature evaporator 012 can work; the second switching valve 008 can also close the flow path of the working fluid inlet 91 of the second injector, so that the low-temperature evaporator 012 cannot work.
[0050] In some embodiments, the aforementioned first throttling device 005 and second throttling device 011 can both be throttling valves, such as electronic expansion valves.
[0051] The first switching valve 006 and the second switching valve 008, as described above, cooperate to enable the dual-temperature zone refrigeration system of this utility model to have at least three operating modes, namely, Mode 1: the high-temperature evaporator 007 and the low-temperature evaporator 012 operate simultaneously (e.g., Figure 1 (As shown); Mode 2: Only high-temperature evaporator 007 operates (as shown) Figure 3 (As shown); Mode 3: Only the low-temperature evaporator 012 operates (as shown) Figure 5 (As shown).
[0052] In mode one, such as Figure 1 and 2As shown, both the first switching valve 006 and the second switching valve 008 are open, and the refrigerant circulation is as follows: the gaseous refrigerant coming out of the compressor 001 exhaust port is condensed into a high-temperature liquid in the condenser 002 (the refrigerant flow direction is: first flow channel 1 → second flow channel 2), and then part of the refrigerant enters the first branch and the other part enters the second branch.The refrigerant entering the first branch circuit as the working fluid enters the first ejector and expands and depressurizes in the working nozzle (refrigerant flow direction: second channel 2 → nozzle 3a of the first ejector). Meanwhile, the refrigerant exiting the high-temperature evaporator 007 mixes with the refrigerant exiting the gas outlet of the second gas-liquid separator 010 (refrigerant flow direction: third channel 3 → tenth channel 10) (refrigerant flow direction: seventh channel 7, tenth channel 10 → eighth channel 8) and then enters the first ejector 003 as the entrainer fluid (refrigerant flow direction: eighth channel 8 → ejector chamber 3b of the first ejector). In the first ejector 003, the working fluid and the entrainer fluid mix in the mixing chamber (refrigerant flow direction: nozzle 3a of the first ejector, first ejector...). After passing through the ejector chamber 3b → the ejector chamber mixing chamber 3m of the first ejector, the refrigerant is pressurized in the diffuser chamber (the refrigerant flow direction is: the ejector chamber mixing chamber 3m of the first ejector → the third flow channel 3), and then enters the first gas-liquid separator 004. The gaseous refrigerant from the gas outlet of the first gas-liquid separator 004 enters the suction port of the compressor 001 (the refrigerant flow direction is: the third flow channel 3 → the fourth flow channel 4), and is then compressed and pressurized in the compressor 001 (the refrigerant flow direction is: the fourth flow channel 4 → the first flow channel 1). The refrigerant entering the second branch passes through the second switch valve 008 and then enters the second ejector 009 as the working fluid (the refrigerant flow direction is: the second flow channel 2 → the nozzle 9a of the second ejector). The refrigerant from the low-temperature evaporator 012... The refrigerant, acting as the ejector fluid, enters the second ejector 009 (refrigerant flow direction: fourteenth channel 14 → ejector chamber 9b of the second ejector). The working fluid and the ejector fluid mix in the mixing chamber (refrigerant flow direction: nozzle 9a of the second ejector, ejector chamber 9b of the second ejector → mixing chamber 9m of the second ejector), and are then pressurized in the diffuser chamber (refrigerant flow direction: mixing chamber 9m of the second ejector → ninth channel 9), subsequently entering the second gas-liquid separator 010. The refrigerant exiting from the liquid outlet of the first gas-liquid separator 004 (refrigerant flow direction: third channel 3 → fifth channel 5) undergoes throttling and pressure reduction via the first throttling device 005 (refrigerant flow direction: fifth channel 5 → sixth channel 6), and mixes with the refrigerant from the second gas-liquid separator... After the refrigerant from the liquid outlet 010 (refrigerant flow direction: 9th channel 9 → 11th channel 11) is mixed (refrigerant flow direction: 6th channel 6, 11th channel 11 → 12th channel 12), part of the refrigerant enters the third branch, and the other part enters the fourth branch. The refrigerant entering the third branch passes through the first switch valve 006 and then enters the high-temperature evaporator 007 to evaporate and absorb heat (refrigerant flow direction: 12th channel 12 → 7th channel 7). The refrigerant entering the fourth branch first passes through the second throttling device 011 for throttling and pressure reduction (refrigerant flow direction: 12th channel 12 → 13th channel 13) and then enters the low-temperature evaporator 012 to evaporate and absorb heat (refrigerant flow direction: 13th channel 13 → 14th channel 14).
[0053] In mode two, such as Figure 3 and 4 As shown, the first switch valve 006 is open and the second switch valve 008 is closed. The refrigerant circulation is as follows: the gaseous refrigerant from the discharge port of the compressor 001 is condensed into a high-temperature liquid in the condenser 002 (refrigerant flow direction: first flow channel 1 → second flow channel 2), and then enters the first ejector 003 as the working fluid (refrigerant flow direction: second flow channel 2 → nozzle 3a of the first ejector). The refrigerant from the high-temperature evaporator 007 enters the first ejector as the ejector fluid (refrigerant flow direction: seventh flow channel 7 → ejector chamber 3b of the first ejector). In the first ejector 003, the working fluid and the ejector fluid are mixed in the mixing chamber (refrigerant flow direction: nozzle 3a of the first ejector, ejector chamber 3b of the first ejector → mixing chamber of the first ejector). After the refrigerant is mixed in the first gas-liquid separator (3m), it is pressurized in the diffuser (the refrigerant flow direction is: mixing chamber 3m of the first injector → third flow channel 3), and then enters the first gas-liquid separator 004; the refrigerant from the gas outlet of the first gas-liquid separator 004 enters the suction port of the compressor 001 (the refrigerant flow direction is: third flow channel 3 → fourth flow channel 4), and then is compressed and pressurized in the compressor 001 (the refrigerant flow direction is: fourth flow channel 4 → first flow channel 1); the liquid refrigerant from the outlet of the first gas-liquid separator 004 first passes through the first throttling device 005 for throttling and pressure reduction (the refrigerant flow direction is: fifth flow channel 5 → sixth flow channel 6), and then passes through the first switching valve 006 before entering the high-temperature evaporator 009 for evaporation and heat absorption (the refrigerant flow direction is: sixth flow channel 6 → seventh flow channel 7).
[0054] In mode three, such as Figure 5 and 6As shown, the first switch valve 006 is closed and the second switch valve 008 is open. The refrigerant circulation is as follows: the gaseous refrigerant from the discharge port of the compressor 001 is condensed into a high-temperature liquid in the condenser 002 (refrigerant flow direction: first flow channel 1 → second flow channel 2). Subsequently, part of the refrigerant enters the first branch and the other part enters the second branch. The refrigerant entering the first branch enters the ejector as the working fluid and expands and depressurizes in the working nozzle (refrigerant flow direction: second flow channel 2 → nozzle 3a of the first ejector). The refrigerant coming out of the gas outlet of the second gas-liquid separator 010 (refrigerant flow direction: third flow channel 3 → tenth flow channel 10) enters the first ejector 003 as the ejector fluid (refrigerant flow direction: tenth flow channel 10 → ejector chamber 3b of the first ejector); in the first ejector 003, the working fluid and the ejector fluid are mixed in the mixing chamber (refrigerant flow direction: nozzle 3a of the first ejector, ejector chamber 3b of the first ejector → first...). After passing through the mixing chamber 3m of the first injector, the refrigerant is pressurized in the diffuser chamber (refrigerant flow direction: mixing chamber 3m of the first injector → third flow channel 3), and then enters the first gas-liquid separator 004. The gaseous refrigerant from the gas outlet of the first gas-liquid separator 004 enters the suction port of the compressor 001 (refrigerant flow direction: third flow channel 3 → fourth flow channel 4), and then undergoes compression and pressurization (refrigerant flow direction: fourth flow channel 4 → first flow channel 1). The refrigerant entering the second branch passes through the second switching valve 008 and then enters the second injector 009 as working fluid (refrigerant flow direction: second flow channel 2 → nozzle of the second injector). 9a) The refrigerant from the low-temperature evaporator 012 is then used as an ejector fluid to enter the second ejector 009 (refrigerant flow direction: fourteenth channel 14 → ejector chamber 9b of the second ejector). The working fluid and the ejector fluid are mixed in the mixing chamber (refrigerant flow direction: nozzle 9a of the second ejector, ejector chamber 9b of the second ejector → mixing chamber 9m of the second ejector), and then pressurized in the diffuser chamber (refrigerant flow direction: mixing chamber 9m of the second ejector → ninth channel 9), and then enter the second gas-liquid separator 010; it exits from the liquid outlet of the first gas-liquid separator 004 (refrigerant flow direction: third channel 3 → The refrigerant in the fifth flow channel 5) is throttled and depressurized by the first throttling device 005 (refrigerant flow direction: fifth flow channel 5 → sixth flow channel 6), and mixed with the refrigerant coming out of the liquid outlet of the second gas-liquid separator 010 (refrigerant flow direction: ninth flow channel 9 → eleventh flow channel 11) (refrigerant flow direction: sixth flow channel 6, eleventh flow channel 11 → twelfth flow channel 12). After being throttled and depressurized by the second throttling device 011 (refrigerant flow direction: twelfth flow channel 12 → thirteenth flow channel 13), it enters the low-temperature evaporator 012 to evaporate and absorb heat (refrigerant flow direction: thirteenth flow channel 13 → fourteenth flow channel 14).
[0055] In the pressure-enthalpy diagrams of Mode 1 and Mode 3, the red part represents the process in the first injector 003 and the first gas-liquid separator 004, and the cyan part represents the process in the second injector 009 and the second gas-liquid separator 010.
[0056] The dual-stage injection mentioned in this utility model is embodied in Mode 1 and Mode 3. Part of the refrigerant passes through the second injector 009 and the first injector 003, and is pressurized twice before entering the suction port of the compressor 001. The process can be seen from the pressure-enthalpy diagram: Fourteenth channel 14 → ejector chamber 9b of the second injector → mixing chamber 9m of the second injector → ninth channel 9 → tenth channel 10 → ejector chamber 3b of the first injector → mixing chamber 3m of the first injector → third channel 3.
[0057] This invention utilizes dual ejectors (i.e., the aforementioned first ejector 003 and second ejector) to recover the energy of the high-pressure fluid at the condenser 002 outlet, reducing throttling losses. The two-stage injection also increases the suction pressure of the compressor 001 during low-temperature refrigeration, reduces the compression ratio of the compressor 001, lessens the operating load of the compressor 001, and extends the service life of the compressor 001. Furthermore, this invention employs gas-liquid separators (i.e., the aforementioned first gas-liquid separator 004 and second gas-liquid separator) at the outlets of both ejectors. The first gas-liquid separator 004 separates the refrigerant into gas and liquid paths, enabling the system to perform a refrigeration cycle. The second gas-liquid separator ensures that the ejector stream from the first ejector 003 is gaseous, preventing liquid from carrying into the ejector and affecting its ejection effect. Simultaneously, a one-way valve 013 is introduced at the liquid outlet of the second gas-liquid separator to prevent refrigerant backflow. In addition, this utility model enables the independent operation of refrigeration in two temperature zones by arranging and controlling the flow path and the first switching valve 006 and the second switching valve 008, and the low-temperature refrigeration side always performs two-stage injection, thereby improving the low-temperature refrigeration effect.
[0058] This utility model also provides an air conditioner that may include any of the above-mentioned dual-temperature zone refrigeration systems. Because the air conditioner uses the aforementioned dual-temperature zone refrigeration system, it recovers the energy of the high-temperature, high-pressure fluid at the outlet of the condenser 002, reduces throttling losses in the refrigeration system, and improves the overall energy efficiency of the system. Furthermore, the two-stage injection can increase the suction pressure of the compressor 001, reduce the compression ratio of the compressor 001 during low-temperature refrigeration, reduce energy consumption, and extend the service life of the compressor 001.
[0059] It will be readily understood by those skilled in the art that, without conflict, the advantageous technical features of the above-mentioned methods can be freely combined and superimposed.
[0060] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this utility model should be included within the protection scope of this utility model. The above description is only a preferred embodiment of this utility model. 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 this utility model, and these improvements and modifications should also be considered within the protection scope of this utility model.
Claims
1. A dual-temperature zone refrigeration system, characterized in that: The system includes a compressor (001), a condenser (002), a first ejector (003), a second ejector (009), a high-temperature evaporator (007), a low-temperature evaporator (012), and a first gas-liquid separator (004). The compressor (001) has an exhaust port (1a) and an intake port (1b). The first gas-liquid separator (004) has a first inlet (4a), a first liquid outlet (4b), and a first gas outlet (4c). The exhaust port (1a) is connected to one end (2a) of the condenser, and the other end (2b) of the condenser is connected to the first ejector (003) and the second ejector (009). The working fluid inlets of the second ejector (009) are connected. The outlet (33) of the first ejector is connected to the first inlet (4a). The first liquid outlet (4b) is connected to one end (7a) of the high-temperature evaporator and one end (12a) of the low-temperature evaporator through the first throttling device (005). The other end (7b) of the high-temperature evaporator and the outlet (93) of the second ejector are both connected to the ejector fluid inlet (32) of the first ejector. The other end (12b) of the low-temperature evaporator is connected to the ejector fluid inlet (92) of the second ejector.
2. The dual-temperature zone refrigeration system according to claim 1, characterized in that: The outlet (93) of the second injector is connected to the ejector fluid inlet (32) of the first injector through the second gas-liquid separator (010); The second gas-liquid separator (010) has a second inlet (10a) and a second gas outlet (10c). The second gas-liquid separator (010) is connected to the outlet (93) of the second injector through the second inlet (10a), and the second gas-liquid separator (010) is connected to the ejector fluid inlet (32) of the first injector through the second gas outlet (10c).
3. The dual-temperature zone refrigeration system according to claim 2, characterized in that: The second gas-liquid separator (010) also has a second liquid outlet (10b), which is connected to one end (12a) of the low-temperature evaporator via a second throttling device (011).
4. The dual-temperature zone refrigeration system according to claim 3, characterized in that: The first throttling device (005) is connected to one end (12a) of the low-temperature evaporator through the second throttling device (011); The second liquid outlet (10b) is connected to the flow path between the first throttling device (005) and the second throttling device (011), and a one-way valve (013) is provided on the flow path of the second liquid outlet (10b) to prevent the fluid in the flow path of the second liquid outlet (10b) from flowing back.
5. The dual-temperature zone refrigeration system according to any one of claims 1 to 4, characterized in that: It also includes a valve mechanism for controlling whether the high-temperature evaporator (007) and the low-temperature evaporator (012) work or not.
6. The dual-temperature zone refrigeration system according to claim 5, characterized in that: The valve mechanism includes a first switching valve (006), which is disposed on the flow path at one end (7a) of the high-temperature evaporator or on the flow path at the other end (7b) of the high-temperature evaporator. The valve mechanism controls the high-temperature evaporator (007) to work or not work through the first switching valve (006).
7. The dual-temperature zone refrigeration system according to claim 5, characterized in that: The valve mechanism includes a second switching valve (008), which is disposed in the flow path of the working fluid inlet (91) of the second injector. The valve mechanism controls the operation or non-operation of the low-temperature evaporator (012) through the second switching valve (008).
8. An air conditioner, characterized in that: The dual-temperature zone refrigeration system includes any one of claims 1-7.