Refrigerating system and variable frequency air conditioner

Abstract

The utility model discloses a refrigerating system and a variable frequency air conditioner, the refrigerating system is used for the variable frequency air conditioner and has a refrigerating mode, the refrigerating system comprises a first heat exchanger, a second heat exchanger, a third heat exchanger, a first throttling element and a second throttling element, in the refrigerating mode, the first heat exchanger is a condenser, the second heat exchanger is an evaporator, and the third heat exchanger is a condenser; the third heat exchanger is used for exchanging heat with a variable frequency controller of the variable frequency air conditioner, the first end of the third heat exchanger communicates with the first heat exchanger through a first throttling element, the second end of the third heat exchanger communicates with the second heat exchanger through a second throttling element, and the first throttling element has a first state and a second state which can be switched; the flow area of the first throttling element in the second state is smaller than that in the first state. Therefore, the refrigerant temperature of the first throttling element in the second state can be further reduced, so that the heat exchange amount of the third heat exchanger and the variable frequency controller is larger, and the operation stability of the variable frequency controller is improved.

Description

TECHNICAL FIELD

[0001] The utility model relates to refrigeration technical field especially is related to a refrigeration system and variable frequency air conditioner. BACKGROUND

[0002] At present, the country strengthens energy conservation and emission reduction constantly, and "low carbon" is popular, and the air conditioning industry has converted into variable frequency technology from fixed frequency technology, but with the climate temperature more and more hot, the refrigeration performance of variable frequency air conditioner under high temperature environment faces challenge.

[0003] When the outside temperature is too high, the temperature of the variable frequency controller installed outdoors also rises accordingly, and the variable frequency controller faces the risk of accelerated aging and damage under high temperature, in order to ensure the stable operation of the variable frequency controller, the refrigeration system will take the measure of limiting the maximum operating frequency of the compressor under high temperature conditions to reduce the temperature of the variable frequency controller. This measure helps to protect the variable frequency controller, but will affect the refrigeration performance of the variable frequency air conditioner to a certain extent, and then may reduce the refrigeration comfort of the user in high temperature weather, so that the user complains because of not feeling cool enough, which has a certain influence on the market competitiveness of the variable frequency air conditioner. Therefore, the variable frequency controller cooling technology needs to be improved. SUMMARY

[0004] The utility model aims at at least solving one of the technical problems existing in the prior art. For this purpose, the utility model provides a refrigeration system and variable frequency air conditioner, the refrigeration system further reduces the refrigerant temperature in the second state of the first throttling element, so that the heat exchange amount of the third heat exchanger and the variable frequency controller is more, thereby improving the stability of the operation of the variable frequency controller.

[0005] According to the refrigeration system of the first aspect embodiment of the utility model, the refrigeration system comprises: a first heat exchanger, a second heat exchanger, a third heat exchanger, a first throttling element and a second throttling element, in the refrigeration mode, the first heat exchanger is a condenser, the second heat exchanger is an evaporator, the third heat exchanger is used for heat exchange with the variable frequency controller of the variable frequency air conditioner, the first end of the third heat exchanger is communicated with the first heat exchanger through the first throttling element, the second end of the third heat exchanger is communicated with the second heat exchanger through the second throttling element, wherein the first throttling element has switchable first state and second state, and the flow area of the first throttling element in the second state is less than that in the first state.

[0006] According to the refrigeration system provided in the embodiment of the present application, the first throttling element has switchable first and second states, the flow area of the second state is smaller than that of the first state, the throttling capacity of the first throttling element in the second state is superior to that in the first state, the temperature of the refrigerant passing through the first throttling element in the second state can be further reduced, the heat exchange amount of the third heat exchanger and the frequency conversion controller is increased, the reliability of the frequency conversion controller in high-temperature operation is improved, and the stability of the refrigeration system in operation is improved.

[0007] In some embodiments, the first throttling element comprises a valve shell, a valve seat and a valve core, the valve shell is formed with a first medium opening communicated with the first heat exchanger and a second medium opening communicated with the third heat exchanger, the valve seat is fixedly arranged in the valve shell and located between the first medium opening and the second medium opening, the valve seat is formed with a first throttling channel communicated with the second medium opening, the valve core is arranged in the valve shell and located between the first medium opening and the valve seat, the valve core is formed with a communication channel communicated with the first medium opening and a second throttling channel, the communication channel is arranged at the outer circumferential side of the second throttling channel, the flow area of the communication channel is greater than that of the second throttling channel, the flow area of the first throttling channel is greater than that of the second throttling channel, in the first state, the communication channel is communicated with the first throttling channel, and in the second state, the communication channel is disconnected from the first throttling channel and the second throttling channel is communicated with the first throttling channel.

[0008] In some embodiments, the flow area of the communication channel is greater than or equal to that of the first throttling channel, the communication channel comprises a plurality of sub-channels arranged at intervals along the circumference of the second throttling channel, and the flow area of the second throttling channel is constant along the axial direction thereof.

[0009] In some embodiments, the flow area of the first throttling channel is S1, the flow area of the second throttling channel is S2, 0.1764≤S2 / S1≤0.8464, and / or the valve shell is a tubular structure, the flow area of the first throttling channel is S1, the flow area of the valve shell is S, and 0.04≤S1 / S≤0.2025.

[0010] In some embodiments, the valve core is movable relative to the valve shell, in the first state, the valve core is arranged at intervals from the valve seat, and in the second state, the valve core is abuttingly arranged with the valve seat.

[0011] In some embodiments, the valve shell is integrally provided with a stop portion, the stop portion is located between the valve core and the first medium opening, the valve core is movable along the axial direction of the first throttling channel and is adapted to abut against the side of the stop portion away from the first medium opening, the first throttling element further comprises an elastic member arranged between the valve seat and the valve core and used for applying an elastic force to the valve core to move towards the first medium opening.

[0012] In some embodiments, the valve seat includes a first seat body portion and a first flow passage portion, the first seat body portion is arranged around an outer circumferential side of the first flow passage portion and is fixed with the valve housing, the first flow passage portion is arranged protruding from the first seat body portion toward the valve core, a first throttling passage is formed on the first flow passage portion, the valve core includes a second seat body portion and a second flow passage portion, the second seat body portion is multiple and is arranged spaced apart along an outer circumferential side of the second flow passage portion, at least part of a communication passage is arranged between two adjacent second seat body portions, the second flow passage portion is arranged protruding from the second seat body portion toward the valve seat, a second throttling passage is formed on the second flow passage portion, and the elastic member is sleeved on the first flow passage portion and the second flow passage portion and abuts between the first seat body portion and the second seat body portion.

[0013] In some embodiments, the length of the first throttling passage is L1, the length of the second throttling passage is L2, 2≤L2 / L1≤3; and / or, 1.5mm≤L1≤5mm.

[0014] The variable frequency air conditioner according to the second aspect of the present application comprises a variable frequency controller and a refrigerating system according to the first aspect of the present application, the variable frequency controller is located outdoors and is used for adjusting the operating frequency of the compressor of the refrigerating system, and the third heat exchanger is used for heat exchange with the variable frequency controller.

[0015] The variable frequency air conditioner according to the present application has the above-mentioned refrigerating system, so that the refrigerating performance of the variable frequency air conditioner under high-temperature outdoor environment is improved.

[0016] In some embodiments, the third heat exchanger is in a tubular structure, the third heat exchanger is arranged around the outer circumferential side of the variable frequency controller, or the third heat exchanger is arranged through the variable frequency controller.

[0017] Additional aspects and advantages of the present application will be described in part in the description that follows, and will become apparent in the description that follows, or will be learned by practice of the present application. BRIEF DESCRIPTION OF DRAWINGS

[0018] The above and / or additional aspects and advantages of the present application will become apparent and more readily appreciated from the following description of embodiments, taken in conjunction with the accompanying drawings in which:

[0019] Figure 1 is an assembly schematic view of a first throttling element according to some embodiments of the present application in a first state;

[0020] Figure 2 is an assembly schematic view of a first throttling element according to some embodiments of the present application in a second state;

[0021] Figure 3 is Figure 1 a schematic view of a valve core shown in FIG.

[0022] Figure 4 is Figure 3 another schematic view of the valve core shown in

[0023] Figure 5 is Figure 1 a schematic view of the valve seat shown in

[0024] Figure 6 is Figure 5 another schematic view of the valve seat shown in

[0025] Figure 7 is a schematic view of a variable frequency air conditioner according to some embodiments of the present application, in which arrows represent the flow direction of refrigerant in cooling mode.

[0026] Reference Signs:

[0027] Variable frequency air conditioner 2, first heat exchanger 10, second heat exchanger 20, third heat exchanger 30, first throttling element 40, valve housing 42, first medium through port 420, second medium through port 422, stop portion 424, valve seat 44, first throttling passage 440, first seat body portion 442, first flow passage portion 444, valve core 46, communication passage 460, sub passage 460a, second throttling passage 462, second seat body portion 464, second flow passage portion 466, elastic member 48, second throttling element 50, compressor 60, reversing element 70. DETAILED DESCRIPTION

[0028] Embodiments of the present application are described below in detail with reference to the accompanying drawings. Examples of the embodiments are shown in the drawings, in which the same or similar components or components having the same or similar functions are denoted by the same reference numerals throughout. The embodiments described below by reference to the drawings are exemplary and are intended to explain the present application, and are not to be understood as limiting the present application.

[0029] The following disclosure provides many different embodiments, or examples, for implementing different structures of the present application. For the purpose of simplification, the components and arrangements of the specific examples are described in the following. Of course, they are merely examples and are not intended to limit the present application. In addition, the present application can repeatedly refer to the numbers and / or letters in different examples. Such repetition is for the purpose of simplification and clarity, and does not indicate the relationship between the various embodiments and / or arrangements discussed. In addition, the present application provides examples of various specific processes and materials, but those skilled in the art can realize the applicability of other processes and / or the use of other materials.

[0030] Below, with reference to the drawings, a refrigeration system according to a first aspect embodiment of the present application is described.

[0031] As Figure 1 ,Figure 2 and Figure 7 As shown in the figure, according to the refrigeration system of the first aspect of the present application, the refrigeration system comprises: a first heat exchanger 10, a second heat exchanger 20, a third heat exchanger 30, a first throttling element 40 and a second throttling element 50. In the refrigeration mode, the first heat exchanger 10 is a condenser, the second heat exchanger 20 is an evaporator, and the third heat exchanger 30 is used for heat exchange with the frequency conversion controller of the variable frequency air conditioner 2. The first end of the third heat exchanger 30 is communicated with the first heat exchanger 10 through the first throttling element 40, and the second end of the third heat exchanger 30 is communicated with the second heat exchanger 20 through the second throttling element 50. The first throttling element 40 has a switchable first state and a second state, and the flow area of the first throttling element 40 in the second state is smaller than that in the first state.

[0032] For example, when the refrigeration system is in the refrigeration mode, the refrigeration system releases the heat in the refrigerant to the environment through the first heat exchanger 10, so that at least part of the refrigerant is condensed from the gaseous state to the liquid state. Subsequently, the liquid refrigerant flows through the first throttling element 40 with switchable flow area, and the refrigerant after the first throttling element 40 enters the third heat exchanger 30, and the refrigerant exchanges heat with the frequency conversion controller of the variable frequency air conditioner 2, and the refrigerant after throttling and cooling adjusts the temperature of the controller; then, the refrigerant further reduces the pressure and temperature through the second throttling element 50, and then enters the second heat exchanger 20, and then absorbs the indoor heat, so as to realize the refrigeration effect of the variable frequency air conditioner 2; the first heat exchanger 10 is a condenser, which receives high-temperature and high-pressure gaseous refrigerant, and at least part of the refrigerant is converted into liquid state through heat exchange process, and the condenser releases the heat in the refrigerant to the external environment; the second heat exchanger 20 is an evaporator, which receives the liquid refrigerant or gas-liquid mixed refrigerant throttled by the second throttling element 50, and the refrigerant absorbs heat from the environment around the evaporator to convert into gaseous state, thereby reducing the temperature of the environment.

[0033] It can be understood that in the embodiment of the present application, the refrigeration system comprises a compressor 60, and in the refrigeration mode, the compressed refrigerant can flow to the first heat exchanger 10, and the refrigerant after heat exchange in the second heat exchanger 20 can flow to the compressor 60 for compression to enter the next cycle.

[0034] The third heat exchanger 30 exchanges heat with the frequency conversion controller of the variable frequency air conditioner 2, and the heat generated by the frequency conversion controller can be effectively transferred away through the heat exchange between the third heat exchanger 30 and the frequency conversion controller, so as to provide a more suitable working environment for the frequency conversion controller, so as to make the temperature of the frequency conversion controller within a suitable range, reduce the risk of accelerated aging or damage of the frequency conversion controller due to high temperature, and improve the stability of the refrigeration system.

[0035] It can be understood that the first throttling element 40 realizes throttling function at least in the second state. For example, the first throttling element 40 realizes throttling in the second state, and cannot realize throttling in the first state (for example, the flow area of the first throttling element 40 in the first state is substantially the same as the flow area of the pipeline between the first throttling element 40 and the first heat exchanger 10, and the flow area of the second throttling element 40 in the second state is smaller than the flow area of the pipeline between the first throttling element 40 and the first heat exchanger 10); or, the first throttling element 40 can realize throttling in the first state and the second state (for example, the flow area of the first throttling element 40 in the first state and the flow area of the first throttling element 40 in the second state are all smaller than the flow area of the pipeline between the first throttling element 40 and the first heat exchanger 10), and the throttling capacity of the first throttling element 40 in the second state is superior to the throttling capacity of the first throttling element 40 in the first state. Then, the first throttling element 40 is communicated with the third heat exchanger 30 at one end, so that the refrigerant with reduced temperature after passing through the first throttling element 40 in the second state can flow to the third heat exchanger 30 in the refrigeration mode, thereby improving the heat exchange efficiency of the third heat exchanger 30 and the frequency controller. Alternatively, in the embodiment of the present application, the flow area of the first throttling element 40 can refer to the minimum flow area of the first throttling element 40 in the corresponding state.

[0036] Taking the example that the first throttling element 40 can realize throttling in the first state and the second state: the flow area of the first throttling element 40 in the second state is smaller than the flow area in the first state, the refrigerant passing through the first throttling element 40 in the first state can take away the heat of the frequency controller when flowing through the third heat exchanger 30 after throttling by the first throttling element 40, and similarly, the refrigerant passing through the second throttling element 40 in the second state can also take away the heat of the frequency controller when flowing through the third heat exchanger 30 after throttling by the first throttling element 40; wherein, since the throttling capacity of the first throttling element 40 in the second state is superior to the throttling capacity in the first state, the temperature of the refrigerant after the first throttling element 40 in the second state can be further reduced relative to the first state, thereby further increasing the heat exchange amount of the third heat exchanger 30 and the frequency controller, and improving the reliability of the frequency controller working in a high-temperature environment; it can be seen that when the temperature of the frequency controller itself is relatively high or the temperature of the environment around the frequency controller is relatively high, the first throttling element 40 can be switched to the second state, so that the third heat exchanger 30 can take away more heat in time, and when the temperature of the frequency controller itself is relatively low or the temperature of the environment around the frequency controller is relatively low, the first throttling element 40 can be switched to the first state, so as to make the temperature of the refrigerant flowing through the third heat exchanger 30 and the cooling demand of the frequency controller well matched. Therefore, the first state and the second state of the first throttling element 40 which can be switched can make the temperature of the frequency controller be more flexible and effective, thereby improving the stability of the frequency controller working.

[0037] For example, in a normal state, the ambient temperature of the frequency conversion controller is less than 55℃, at this time, the heat dissipation required by the frequency conversion controller is small, the first throttling element 40 can be maintained in the first state, in which the flow area of the first throttling element 40 is relatively large, the refrigerant can pass through the first throttling element 40 in the first state to reduce the temperature, and the refrigerant with reduced temperature flows to the third heat exchanger 30 to exchange heat with the frequency conversion controller, so that the working temperature of the frequency conversion controller is maintained at a relatively stable level; in a high-temperature state, the ambient temperature of the frequency conversion controller is greater than or equal to 55℃, at this time, the heat dissipation required by the frequency conversion controller is large, the first throttling element 40 can be maintained in the second state, in which the flow area of the first throttling element 40 is relatively small, the refrigerant can pass through the first throttling element 40 in the second state to further reduce the temperature, and the refrigerant with lower temperature flows to the third heat exchanger 30 to increase the heat exchange amount between the third heat exchanger 30 and the frequency conversion controller, so that the working temperature of the frequency conversion controller is maintained at a relatively stable level. As an example, the frequency conversion controller can be arranged outdoors, and the ambient temperature of the frequency conversion controller can be the outdoor ambient temperature.

[0038] In other examples, the first throttling element 40 realizes throttling in the second state and cannot realize throttling in the first state, which is basically the same as the above case, and will not be described here.

[0039] Compared with some technologies, the frequency conversion controller is arranged outdoors, and in order to protect the frequency conversion controller, the maximum operating frequency of the compressor is limited to reduce the temperature of the frequency conversion controller in a high-temperature external environment, which protects the frequency conversion controller by limiting the operating frequency of the frequency conversion air conditioner compressor, and sacrifices the refrigeration capacity of the frequency conversion air conditioner in a high-temperature environment, so that the refrigeration effect of the frequency conversion air conditioner in a high-temperature environment is not good.

[0040] According to the refrigeration system, the first throttling element 40 is arranged between the first heat exchanger 10 and the third heat exchanger 30, so that the refrigerant flowing out of the first heat exchanger 10 in a refrigeration mode first flows through the first throttling element 40 and then flows to the third heat exchanger 30. Since the first throttling element 40 has the first state and the second state, and the throttling capacity of the first throttling element 40 in the second state is better than that in the first state, the temperature of the refrigerant flowing through the first throttling element 40 in the second state can be further reduced, the heat exchange amount between the third heat exchanger 30 and the frequency conversion controller can be improved, the temperature of the frequency conversion controller can be maintained at a relatively stable level, the adaptability of the frequency conversion controller to a high-temperature environment and the reliability of the frequency conversion controller in a high-temperature environment can be improved, and the operating frequency of the compressor 60 does not need to be limited, so that the frequency conversion controller can be protected, the problem that the frequency conversion controller is easily aged and damaged in a high-temperature environment can be improved, and the refrigeration performance of the refrigeration system in a high-temperature external environment can be improved, so that the use experience of the frequency conversion air conditioner 2 is improved.

[0041] Optionally, the second throttling element 50 is a capillary tube or an electronic expansion valve. The capillary tube has the characteristics of simple structure, stability and reliability, economy and practicality, and is suitable for small refrigeration equipment or refrigeration systems with stable load to ensure basic throttling effect. The electronic expansion valve has the advantages of precise control, strong adaptability, energy efficiency improvement and intelligence, and is more suitable for large refrigeration equipment or occasions requiring high-precision refrigeration control to realize on-demand adjustment of refrigerant flow. Users can comprehensively consider according to the specific needs, cost budget and operating conditions of the refrigeration system.

[0042] Optionally, the first throttling element 40 can be configured as a throttling valve with adjustable opening degree.

[0043] In the embodiments of the present application, the refrigeration system can be a single-cooling system or a cooling and heating system. When the refrigeration system is used in an air conditioner, the air conditioner can be a single-cooling air conditioner or a cooling and heating air conditioner.

[0044] Taking the refrigeration system as a cooling and heating system as an example: as shown in Figure 7 In some embodiments, the refrigeration system further includes a reversing element 70, which is a key part of the refrigeration system for realizing the conversion between refrigeration and heating. The reversing element 70 can control the flow direction of the refrigerant, so that the refrigeration system can be flexibly switched between the refrigeration and heating modes.

[0045] For example, the reversing element 70 has a first valve port, a second valve port, a third valve port and a fourth valve port, the first valve port is switched to communicate with one of the second valve port and the third valve port, and the fourth valve port is switched to communicate with the other one of the second valve port and the third valve port; in other words, when the first valve port communicates with the second valve port, the fourth valve port communicates with the third valve port, and when the first valve port communicates with the third valve port, the fourth valve port communicates with the second valve port. The compressor 60 has a discharge port and a return port, the first valve port is connected to the discharge port, the fourth valve port is connected to the return port, one end of the second heat exchanger 20 is connected to the third valve port, and one end of the first heat exchanger 10 is connected to the second valve port. In the cooling mode, the first valve port communicates with the second valve port, the third valve port communicates with the fourth valve port, and the reversing element 70 makes the refrigerant from the compressor 60 enter the first heat exchanger 10, the first heat exchanger 10 releases heat of the refrigerant to the outdoor as a condenser, and then the refrigerant flows through the first throttling element 40, the third heat exchanger 30 and the second throttling element 50 in sequence, and then flows to the second heat exchanger 20 to perform cooling, and the heat-exchanged refrigerant in the second heat exchanger 20 flows to the compressor 10 through the reversing element 70 to complete the cooling process; and in the heating mode, the first valve port communicates with the third valve port, and the second valve port communicates with the fourth valve port, and the reversing element 70 changes the flow direction of the refrigerant, so that the refrigerant from the compressor 60 enters the second heat exchanger 20 to perform heating, and then the refrigerant flows through the second throttling element 50, the third heat exchanger 30 and the first throttling element 40 in sequence, and then flows to the first heat exchanger 10 to absorb outdoor heat, and then flows to the compressor 60 through the reversing element 70 to complete the heating process.

[0046] Optionally, the reversing element 70 is a four-way valve, which can quickly and accurately change the flow direction of the refrigerant, so that the refrigeration system can be flexibly switched between the cooling mode and the heating mode to meet different needs of users.

[0047] For example, Figures 1-6As shown, in some embodiments, the first throttling element 40 includes a valve housing 42, a valve seat 44 and a valve core 46. The valve housing 42 has a first medium passage 420 and a second medium passage 422 formed therein, the first medium passage 420 being in communication with the first heat exchanger 10, and the second medium passage 422 being in communication with the third heat exchanger 30. The valve seat 44 is fixedly arranged in the valve housing 42 and located between the first medium passage 420 and the second medium passage 422. The valve seat 44 has a first throttling passage 440 formed therein, the first throttling passage 440 being in communication with the second medium passage 422. The valve core 46 is arranged in the valve housing 42 and located between the first medium passage 420 and the valve seat 44. The valve core 46 has a communication passage 460 and a second throttling passage 462 formed therein, the communication passage 460 being arranged at the outer circumferential side of the second throttling passage 462, and the flow area of the communication passage 460 being greater than that of the second throttling passage 462. The flow area of the first throttling passage 440 is greater than that of the second throttling passage 462. In the first state, the communication passage 460 is in communication with the first throttling passage 440. In the second state, the communication passage 460 is cut off from the first throttling passage 440, and the second throttling passage 462 is in communication with the first throttling passage 440.

[0048] It can be seen that, when the first throttling element 40 is in the first state, the first medium passage 420 is in communication with the second medium passage 422 through the communication passage 460 and the first throttling passage 440. When the first throttling element 40 is in the second state, the first medium passage 420 is in communication with the second medium passage 422 through the second throttling passage 462 and the first throttling passage 440. The switching between the first state and the second state can be realized by adjusting the communication mode of the flow passage in the first throttling element 40, for example, controlling the on-off between the communication passage 460 and the first throttling passage 440.

[0049] For example, in the first state, since the flow area of the communication passage 460 is larger than that of the second throttling passage 462, the refrigerant can flow more smoothly through the communication passage 460, and the refrigerant flow is relatively larger than that in the second state. The refrigerant mainly passes through the first throttling passage 440 for throttling, and the temperature of the refrigerant passing through the first throttling passage 440 is lowered. The refrigerant then flows to the third heat exchanger 30 through the second medium port 422, so that the third heat exchanger 30 and the frequency controller can realize rapid heat exchange, thereby achieving the effect of cooling. When the first throttling element 40 is in the second state, the refrigerant only flows to the first throttling passage 440 through the second throttling passage 462 and cannot flow to the first throttling passage 440 through the communication passage 460. Since the flow area of the first throttling passage 440 is larger than that of the second throttling passage 462, the refrigerant passing through the second throttling passage 462 will be subjected to significant throttling, that is, the temperature of the refrigerant passing through the second throttling passage 462 can be further lowered. The refrigerant then flows to the third heat exchanger 30 through the second medium port 422, so that the heat exchange amount of the third heat exchanger 30 and the frequency controller is larger, thereby improving the stability of the frequency controller in high-temperature operation.

[0050] It can be understood that in the first state, the second throttling passage 462 can be in communication with the first throttling passage 440 or can be disconnected. If the second throttling passage 462 is also in communication with the first throttling passage 440, the refrigerant can flow to the first throttling passage 440 through the communication passage 460 and the second throttling passage 462. However, the flow area of the communication passage 460 is larger than that of the second throttling passage 462, so that the refrigerant has smaller resistance when passing through the communication passage 460. The flow of the refrigerant in the communication passage 460 is larger, and then the refrigerant is throttled and cooled by the first throttling passage 440. The refrigerant passing through the second throttling passage 462 has smaller flow due to the smaller flow area of the second throttling passage 462. The throttling and cooling effect of the second throttling passage 462 can be relatively less significant. That is, in the first state, the first throttling element 40 mainly throttles and cools through the first throttling passage 440.

[0051] As Figures 1-4As shown, in some embodiments, the flow area of the communication passage 460 is greater than or equal to the flow area of the first throttling passage 440, so that the refrigerant encounters less resistance and has a greater flow rate when passing through the communication passage 460, and the refrigerant can flow more smoothly in the communication passage 460; the communication passage 460 includes a plurality of sub-passages 460a arranged along the circumference of the second throttling passage 462, that is, when the first throttling element 40 is in the first state, the refrigerant flows through the plurality of sub-passages 460a and the second throttling passage 462 to the first throttling passage 440, so that the refrigerant flow to the first throttling passage 440 is greater, which helps to improve the overall flow efficiency of the refrigeration system, thereby enhancing the refrigeration capacity of the refrigeration system. For example, when in a normal state, that is, when the external temperature is less than 55°C, the refrigerant has a greater flow rate through the communication passage 460, and then throttles and cools through the first throttling passage 440, which can meet the heat dissipation demand of the frequency controller while enhancing the refrigeration capacity of the system.

[0052] In some embodiments, the flow area of the second throttling passage 462 is constant along its axial direction, that is, the second throttling passage 462 is a straight-through hole, the hole diameter of the straight-through hole remains consistent along its axial direction, and the refrigerant does not encounter a sudden change in hole diameter during flow in the second throttling passage 462, so that the refrigerant can maintain a relatively stable flow rate and pressure distribution, reducing the pressure loss caused by the variable diameter and improving the working efficiency of the refrigeration system.

[0053] In some embodiments, the flow area of the first throttling passage 440 is S1, the flow area of the second throttling passage 462 is S2, and 0.1764≤S2 / S1≤0.8464; and / or, the valve housing 42 is a tubular structure, the flow area of the first throttling passage 440 is S1, the flow area of the valve housing 42 is S, and 0.04≤S1 / S≤0.2025. For example, S2 / S1 is 0.1764, 0.19, 0.24, 0.38, 0.42, 0.55, 0.67, 0.72, 0.8464, etc.; S1 / S is 0.04, 0.09, 0.12, 0.17, 0.19, 0.2, or 0.2025, etc.

[0054] When the ratio of S2 / S1 is too small, i.e., the flow area of the second throttling passage 462 is too small relative to the flow area of the first throttling passage 440, it will cause the refrigerant to be subjected to greater resistance when passing through the second throttling passage 462, the pressure of the refrigerant inside the refrigeration system increases, the flow of the refrigerant passing through the second throttling passage 462 to the first throttling passage 440 is smaller, which affects the refrigeration effect of the variable frequency air conditioner 2, and the increased pressure also requires more energy for the refrigeration system to overcome the resistance to push the refrigerant to flow, thereby increasing the energy consumption of the refrigeration system; when the ratio of S2 / S1 is too large, i.e., the flow area of the second throttling passage 462 is relatively small relative to the flow area of the first throttling passage 440, the throttling and cooling effect of the refrigerant passing through the second throttling passage 462 to the first throttling passage 440 will be weakened, which limits the pressure and temperature drop of the refrigerant after passing through the second throttling passage 462, and limits the heat exchange amount of the third heat exchanger 30; by setting the ratio of S2 / S1 to be between 0.1764 and 0.8464, it can ensure that the refrigerant passing through the second throttling passage 462 to the first throttling passage 440 is subjected to appropriate resistance to achieve throttling and pressure reduction, and will not increase energy consumption due to excessive resistance, which helps to optimize the flow state of the refrigerant in the refrigeration system, improve the refrigeration efficiency, and reduce unnecessary energy consumption.

[0055] It can be understood that by adjusting the flow area ratio of the first throttling passage 440 and the second throttling passage 462, the refrigeration demand under different working conditions can be adapted to a certain extent. For example, in the case of requiring higher refrigeration effect, the flow area of the second throttling passage 462 can be appropriately reduced to enhance the throttling effect; and in the case of requiring to reduce energy consumption, the flow area of the second throttling passage 462 can be appropriately increased to reduce the resistance.

[0056] Exemplarily, the first throttling passage 440 and the second throttling passage 462 are both circular through holes, and the diameter of the first throttling passage 440 is D1, and the diameter of the second throttling passage 462 is D2, 0.42≤D2 / D1≤0.92, such as D2 / D1 being 0.42, 0.5, 0.64, 0.75, 0.8 or 0.92, etc.; by setting the ratio of the diameters of the second throttling passage 462 and the first throttling passage 440 to be within the range of 0.42 to 0.92, the refrigerant passing through the second throttling passage 462 to the first throttling passage 440 is subjected to appropriate resistance to achieve throttling and pressure reduction, and will not increase energy consumption due to excessive resistance, which helps to optimize the flow state of the refrigerant in the refrigeration system.

[0057] When the S1 / S ratio is too small, the refrigerant encounters significant resistance when passing through the first throttling channel 440, increasing the refrigerant pressure inside the refrigeration system. This requires more energy to overcome the resistance and propel the refrigerant, thus increasing the system's energy consumption. Furthermore, the refrigerant flow rate through the first throttling channel 440 is relatively low, affecting the cooling effect of the inverter air conditioner. Conversely, when the S1 / S ratio is too large, the throttling and cooling effect of the refrigerant through the first throttling channel 440 is relatively small, failing to effectively achieve the throttling and cooling function, preventing the refrigeration system from reaching the expected cooling effect or energy efficiency level. By setting the S1 / S ratio between 0.04 and 0.2025, a reasonable design of the first throttling channel 440 helps optimize the overall performance of the refrigeration system. This ensures that the refrigerant encounters appropriate resistance when passing through the first throttling channel 440, achieving effective throttling and cooling, meeting the refrigeration and energy efficiency requirements of the system, and enhancing its stability and reliability.

[0058] For example, the first throttling channel 440 is a circular through hole, and the valve housing 42 is a circular straight pipe with the hole diameter of the valve housing 42 remaining consistent along its axial direction. The diameter of the first throttling channel 440 is D1, and the inner diameter of the valve housing 42 is D3, where 0.2 ≤ D1 / D3 ≤ 0.45. For example, D1 / D3 can be 0.2, 0.24, 0.37, 0.4, or 0.45. By setting the ratio of the diameter of the first throttling channel 440 to the diameter of the valve housing 42 within the range of 0.2 to 0.45, it helps to optimize the overall performance of the refrigeration system, so that the refrigerant experiences appropriate resistance when passing through the first throttling channel 440, thereby achieving an effective throttling and cooling effect.

[0059] like Figure 1 and Figure 2 As shown, in some embodiments, the valve core 46 can move relative to the valve housing 42. In a first state, the valve core 46 and the valve seat 44 are spaced apart, and in a second state, the valve core 46 and the valve seat 44 are abutted together. It is evident that the valve core 46 can move relative to the valve housing 42, allowing it to freely switch between the first and second states. In the first state, the valve core 46 and the valve seat 44 are spaced apart, allowing refrigerant to flow through the connecting channel 460 to the first throttling channel 440, thereby increasing the refrigerant flow rate in the first state to meet the refrigeration requirements of the refrigeration system and the heat dissipation requirements of the frequency converter. In the second state, the valve core 46 and the valve seat 44 are abutted together, disconnecting the connecting channel 460 from the first throttling channel 440. The refrigerant can only flow through the second throttling channel 462 to the first throttling channel 440, resulting in a lower temperature of the refrigerant passing through the first throttling element 40, thus meeting the heat dissipation requirements of the frequency converter.

[0060] For example, a second throttling channel 462 is provided in the middle of the valve core 46, and a connecting channel 460 is provided on the outer periphery of the second throttling channel 462. Therefore, in the radial direction of the valve core 46, the connecting channel 460 is located outside the second throttling channel 462, and also outside the first throttling channel 440. The second throttling channel 462 can be arranged opposite to the first throttling channel 440 along the axial direction of the valve core 46. The connecting channel 460 and the first throttling channel 440 are radially offset. Because the second throttling... The flow area of ​​channel 462 is smaller than that of the first throttling channel 440, and the connecting channel 460 is located on the outer periphery of the second throttling channel 462. Therefore, no matter how the valve core 46 moves, the second throttling channel 462 is always connected to the first throttling channel 440. The part of the valve seat 44 that is suitable for abutting with the valve core 46 can separate the connecting channel 460 and the second throttling channel 462 radially when the valve core 46 abuts with the valve seat 44, so as to cut off the connection between the connecting channel 460 and the first throttling channel 440.

[0061] like Figure 1 and Figure 2 As shown, in some embodiments, a stop portion 424 is integrally provided on the valve housing 42. The stop portion 424 is located between the valve core 46 and the first medium inlet 420. The valve core 46 can move along the axial direction of the first throttling channel 440 (e.g., Figure 1 The first throttling element 40 also includes an elastic element 48, which is disposed between the valve seat 44 and the valve core 46 and is used to apply an elastic force to the valve core 46 toward the first medium inlet 420. The first throttling element 40 moves in the direction of the extension of the central axis L3 of the first throttling channel 440 and the valve core 46 is adapted to abut against the side of the stop portion 424 opposite to the first medium inlet 420.

[0062] As can be seen, the stop part 424 is located between the valve core 46 and the first medium inlet 420, which can limit the movement range of the valve core 46, so that the valve core 46 will not move too far away from the valve seat 44 under the action of the elastic member 48. The refrigerant can flow smoothly through the connecting channel 460 to the first throttling channel 440 for throttling and cooling, thereby improving the stability of the refrigeration system operation.

[0063] When the ambient temperature is too high, the frequency converter has a large heat dissipation demand. At the same time, the temperature and saturation pressure of the refrigerant flowing through the outside will also increase, causing the exhaust pressure of the refrigeration system to rise. Under the action of the high pressure difference, the first throttling element 40 causes the valve core 46 to overcome the elastic force of the elastic element 48 and stop against the valve seat 44. That is, under the action of the high pressure difference, the first throttling element 40 switches from the first state to the second state. The refrigerant flows only through the second throttling channel 462 to the first throttling channel 440, so that the temperature of the refrigerant passing through the first throttling element 40 is lower, thereby meeting the heat dissipation demand of the frequency converter and improving the stability of the frequency converter operation.

[0064] When the ambient temperature is not high, the heat dissipation demand of the frequency conversion controller is small, at this time, the temperature and saturation pressure of the refrigerant flowing through the outside are not high, and the exhaust pressure of the refrigeration system is low. Therefore, the valve core 46 can be spaced apart from the valve seat 44 under the action of the elastic member 48, the refrigerant can flow to the first throttling channel 440 through the communication channel 460 and the second throttling channel 462, the refrigerant flow to the first throttling channel 440 is larger, which helps to improve the overall flow efficiency of the refrigeration system, thereby enhancing the refrigeration capacity of the refrigeration system.

[0065] As can be seen, according to the characteristics of the refrigerant, when the ambient temperature is too high, the temperature and saturation pressure of the refrigerant flowing through the outside will also rise, so that the exhaust pressure of the system rises, thereby overcoming the elastic force of the elastic member 48 to make the valve core 46 and the valve seat 44 stop. When the ambient temperature is not high, the temperature and saturation pressure of the refrigerant flowing through the outside are not high, and the valve core 46 can be spaced apart from the valve seat 44 under the elastic force of the elastic member 48. By utilizing the characteristics of the refrigerant, the switching of the first throttling element 40 between the first state and the second state can be automatically controlled according to the outside temperature, without manual adjustment or the need to set a special driving structure for adjustment, thereby simplifying the control logic.

[0066] Optionally, the elastic member 48 is a spring, which has simple structure, low cost, easy to manufacture and install, and helps to reduce the cost of the first throttling element 40.

[0067] In some embodiments, the stop portion 424 is an annular flange formed by the part of the valve shell 42 protruding radially inward, which enhances the structural strength of the valve shell 42 in this area and improves the durability of the stop portion 424 under the impact of the valve core 46 and the pressure of the refrigerant for a long time. At the same time, the design of the annular flange utilizes the material of the valve shell 42 itself, without the need to add additional parts as the stop portion 424, thereby simplifying the manufacturing process and reducing the cost.

[0068] As Figures 1-6As shown, in some embodiments, the valve seat 44 includes a first seat body portion 442 and a first flow passage portion 444, the first seat body portion 442 is arranged around the outer periphery of the first flow passage portion 444 and is fixed to the valve housing 42, the first flow passage portion 444 is arranged protruding from the first seat body portion 442 towards the valve core 46, the first throttling passage 440 is formed on the first flow passage portion 444, the valve core 46 includes a second seat body portion 464 and a second flow passage portion 466, the second seat body portion 464 is multiple and is arranged spaced apart along the outer periphery of the second flow passage portion 466, at least part of the communication passage 460 is arranged between two adjacent second seat body portions 464, the second flow passage portion 466 is arranged protruding from the second seat body portion 464 towards the valve seat 44, the second throttling passage 462 is formed on the second flow passage portion 466, the second throttling passage 462 can pass through both axial ends of the second flow passage portion 466, the elastic member 48 is sleeved on the first flow passage portion 444 and the second flow passage portion 466, and the elastic member 48 is abutted between the first seat body portion 442 and the second seat body portion 464.

[0069] In the first state, the second flow passage portion 466 is arranged spaced apart from the first flow passage portion 444, so that the communication passage 460 communicates with the first throttling passage 440 through the space between the second flow passage portion 466 and the first flow passage portion 444; in the second state, the second flow passage portion 466 is arranged abutting with the first flow passage portion 444, then the first flow passage portion 444 separates the communication passage 460 and the second throttling passage 462 in the radial direction, so that the communication passage 460 is cut off from the first throttling passage 440.

[0070] It can be seen that the first seat body 442 is arranged around the outer periphery of the first flow passage 444 and fixed with the valve housing 42, which enhances the structural stability of the valve seat 44, enables the valve seat 44 to withstand greater refrigeration system pressure and impact force, and thus prolongs the service life of the valve seat 44; the first flow passage 444 is arranged protruding from the first seat body 442 towards the valve core 46, and the first throttling passage 440 is formed on the first flow passage 444, so that the axial length of the first throttling passage 440 is longer, and the refrigerant needs to pass through a longer path when passing through the first throttling passage 440, thereby increasing the contact time of the refrigerant with the first throttling passage 440, which helps to more effectively reduce the pressure of the refrigerant and improve the throttling effect of the refrigerant flowing through the first throttling passage 440; the second seat body 464 is multiple and arranged in intervals along the outer periphery of the second flow passage 466, which can form a more stable support structure and help to enhance the overall structural strength of the valve core 46 and improve the stability and reliability of the valve core 46 under high pressure; the second flow passage 466 is arranged protruding from the second seat body 464 towards the valve seat 44, and the second throttling passage 462 is formed on the second flow passage 466, so that the axial length of the second throttling passage 462 is longer, and the refrigerant needs to pass through a longer path when passing through the second throttling passage 462, thereby increasing the contact time of the refrigerant with the second throttling passage 462, which helps to more effectively reduce the pressure of the refrigerant and improve the throttling effect of the refrigerant flowing through the second throttling passage 462.

[0071] In addition, the elastic member 48 is sleeved on the first flow passage 444 and the second flow passage 466 and abuts between the first seat body 442 and the second seat body 464, which can absorb the energy when the valve core 46 is subjected to the refrigeration system pressure or impact force and play a buffering and damping role, thereby helping to protect the valve core 46 and the valve seat 44 from damage and prolong the service life of the valve.

[0072] It can be understood that the plurality of second seat bodies 464 define the communication passage 460 with the valve housing 42, and the communication passage 460 is arranged between the adjacent two second seat bodies 464 or arranged between the adjacent two seat bodies, and the user can flexibly select the shape of the valve core 46 according to actual needs to meet the performance requirements in different application scenarios.

[0073] As Figure 1 and Figure 2As shown in the drawings, in some embodiments, the valve shell 42 is radially protruded to form an annular protrusion, and the first seat body portion 442 is connected with the annular protrusion through interference fit, which improves the connection strength of the first seat body portion 442 and the valve shell 42, so that the first seat body portion 442 can withstand greater pressure and impact force of the refrigeration system during use, and the interference fit connection improves the sealing of the first seat body portion 442 and the valve shell 42, effectively reduces the possibility of refrigerant leakage through the connection gap under high pressure, and improves the reliability of the refrigeration system operation.

[0074] As shown in the drawings, Figure 1 and Figure 2 As shown in the drawings, in some embodiments, the length of the first throttling channel 440 is L1, and the length of the second throttling channel 462 is L2, 2≤L2 / L1≤3, by adjusting the quantitative relationship between L1 and L2, the throttling effect in the second state can be optimized to a certain extent, the longer second throttling channel 462 can more effectively reduce the pressure of the refrigerant, so that the temperature of the refrigerant passing through the second throttling channel 462 is lower, and the throttling effect in the second state is improved; and / or, the length of the first throttling channel 440 is L1, 1.5mm≤L1≤5mm, if the length of the first throttling channel 440 is too large, it is easy to increase the material consumption of manufacturing the valve seat 44, resulting in rising product cost, if the length of the first throttling channel 440 is too small, the throttling effect of the refrigerant passing through the first throttling channel 440 is limited, the length of the first throttling channel 440 is set in the range of 1.5mm to 5mm, so that the valve seat 44 has sufficient structural strength, which helps to reduce the deformation or damage of the valve seat 44 caused by the pressure of the refrigeration system or external impact, and at the same time the refrigerant passing through the first throttling channel 440 can achieve good throttling effect, thereby improving the stability of the refrigeration system operation. For example, L2 / L1 can be 2, 2.3, 2.5, 2.8 or 3, etc.; L1 can be 1.5mm, 2.4mm, 3mm, 3.7mm, 4mm, 4.6mm or 5mm, etc.

[0075] The variable frequency air conditioner 2 according to the second aspect of the present application comprises a variable frequency controller and a refrigeration system according to the first aspect of the present application, the variable frequency controller is located outdoors and is used for adjusting the operating frequency of the compressor 60 of the refrigeration system, and the third heat exchanger 30 is used for heat exchange with the variable frequency controller.

[0076] The variable frequency air conditioner 2 according to the embodiment of the present application, by adopting the above refrigeration system, can improve the refrigeration performance of the variable frequency air conditioner 2 under high temperature outdoor environment.

[0077] Exemplarily, the temperature sensor is usually arranged on the variable frequency air conditioner 2, which can monitor the temperature of the variable frequency controller in real time. When the temperature of the variable frequency controller is too high, the variable frequency controller will limit the running power of the compressor 60 to reduce the temperature of the variable frequency controller. By adopting the above refrigeration system, under the high temperature outdoor environment, the first throttling element 40 can reduce the temperature of the refrigerant flowing to the third heat exchanger 30 by switching to the second state, which is beneficial to increase the heat exchange amount between the third heat exchanger 30 and the variable frequency controller, so that the temperature of the variable frequency controller will not be too high under the high temperature outdoor environment, thereby the running power of the compressor 60 will not be limited, which is convenient to improve the refrigeration performance of the variable frequency air conditioner 2 under the high temperature outdoor environment.

[0078] It can be understood that the type of the variable frequency air conditioner 2 in the embodiments of the present application is not limited, which can be a vehicle-mounted air conditioner, and can also be an all-in-one air conditioner or a split air conditioner. The all-in-one air conditioner can include a window air conditioner or a mobile air conditioner, etc. The split air conditioner can include an air conditioner hanging machine or an air conditioner cabinet machine, etc.

[0079] In some embodiments, the third heat exchanger 30 is a tubular structure, and the third heat exchanger 30 is arranged around the outer circumferential side of the variable frequency controller. The tubular structure of the third heat exchanger 30 can be flexibly arranged around the outer circumferential side of the variable frequency controller, so as to maximize the heat dissipation area and improve the heat exchange efficiency between the third heat exchanger 30 and the variable frequency controller. Moreover, the layout mode of surrounding arrangement makes full use of the space around the variable frequency controller, reduces the occupied space of the third heat exchanger 30, and improves the compactness of the variable frequency air conditioner 2.

[0080] In other embodiments of the present application, the third heat exchanger 30 is a tubular structure, and the third heat exchanger 30 can also be arranged in the variable frequency controller, which is convenient to reduce the distance between the third heat exchanger 30 and the heat source inside the variable frequency controller, so as to make the third heat exchanger 30 more effectively exchange heat with the heat source inside the variable frequency controller and improve the heat dissipation efficiency.

[0081] In addition, it should be noted that various specific technical features described in the above specific embodiments can be combined in any suitable manner without contradiction. In order to avoid unnecessary repetition, various possible combinations are not described again in the present application. In addition, various different embodiments of the present application can also be combined in any manner, as long as it does not violate the idea of the present application, it should also be considered as disclosed in the present application.

[0082] In the description of the utility model, need understanding is, the orientation or positional relation that the terms "center", "transverse", "length", "thickness", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential" indicate is based on the orientation or positional relation shown in the drawing, is only for the convenience of describing the utility model and simplifying the description, and is not the indication or implication that the indicated device or element must have a particular orientation, is constructed and operated in a particular orientation, therefore can not be understood as the limitation to the utility model. In addition, the features limited with "first", "second" can be explicitly or implicitly include one or more of the features. In the description of the utility model, unless otherwise specified, the meaning of "a plurality of" is two or more than two. In the description of the utility model, it needs to be explained that, unless otherwise specified and limited, the terms "mounting", "connecting", "connection" should be understood broadly, for example, can be fixedly connected, can be detachably connected, or integrally connected;Can be mechanically connected, can be electrically connected;Can be directly connected, can be indirectly connected through an intermediate medium, can be the communication inside two elements. For ordinary skilled in the art, the specific meaning of the above terms in the utility model can be understood according to the specific circumstances.

[0083] In the description of the specification, the description of the terms "one embodiment", "some embodiments", "illustrative embodiment", "example", "specific example" or "some examples" means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the utility model. In the specification, the illustrative description of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0084] Although the embodiments of the utility model have been shown and described, those skilled in the art can understand that various changes, modifications, replacements and variations can be made to these embodiments without departing from the principles and purposes of the utility model, and the scope of the utility model is defined by the claims and its equivalents.

Claims

1. A refrigeration system, characterized in that, The refrigeration system is used in a variable frequency air conditioner and has a cooling mode. The refrigeration system includes: In the refrigeration mode, the first heat exchanger is a condenser and the second heat exchanger is an evaporator. A third heat exchanger is used for heat exchange with the inverter controller of the inverter air conditioner; The first throttling element and the second throttling element are connected. The first end of the third heat exchanger is connected to the first heat exchanger through the first throttling element, and the second end of the third heat exchanger is connected to the second heat exchanger through the second throttling element. The first throttling element has a switchable first state and a second state, wherein the flow area of ​​the first throttling element in the second state is smaller than the flow area in the first state.

2. The refrigeration system according to claim 1, characterized in that, The first throttling element includes a valve housing, a valve seat, and a valve core. The valve housing has a first medium inlet communicating with the first heat exchanger and a second medium inlet communicating with the third heat exchanger. The valve seat is fixed within the valve housing and located between the first medium inlet and the second medium inlet. The valve seat has a first throttling channel communicating with the second medium inlet. The valve core is located within the valve housing and between the first medium inlet and the valve seat. The valve core has a connecting channel communicating with the first medium inlet and a second throttling channel. The connecting channel is located on the outer periphery of the second throttling channel, and the flow area of ​​the connecting channel is larger than the flow area of ​​the second throttling channel. The flow area of ​​the first throttling channel is larger than the flow area of ​​the second throttling channel. In the first state, the connecting channel is connected to the first throttling channel; in the second state, the connecting channel is disconnected from the first throttling channel, and the second throttling channel is connected to the first throttling channel.

3. The refrigeration system according to claim 2, characterized in that, The flow area of ​​the connecting channel is greater than or equal to the flow area of ​​the first throttling channel. The connecting channel includes a plurality of sub-channels spaced circumferentially along the second throttling channel. The flow area of ​​the second throttling channel remains constant along its axial direction.

4. The refrigeration system according to claim 2, characterized in that, The flow area of ​​the first throttling channel is S1, the flow area of ​​the second throttling channel is S2, and 0.1764≤S2 / S1≤0.8464; and / or, the valve body is a tubular structure, the flow area of ​​the first throttling channel is S1, the flow area of ​​the valve body is S, and 0.04≤S1 / S≤0.2025.

5. The refrigeration system according to claim 2, characterized in that, The valve core is movable relative to the valve body. In the first state, the valve core and the valve seat are spaced apart. In the second state, the valve core and the valve seat are abutted against each other.

6. The refrigeration system according to claim 5, characterized in that, The valve housing is integrally provided with a stop portion, which is located between the valve core and the first medium inlet. The valve core is axially movable along the first throttling channel and is adapted to abut against the side of the stop portion opposite to the first medium inlet. The first throttling element further includes an elastic element disposed between the valve seat and the valve core and used to apply an elastic force to the valve core to move toward the first medium inlet.

7. The refrigeration system according to claim 6, characterized in that, The valve seat includes a first seat portion and a first flow channel portion. The first seat portion is disposed around the outer periphery of the first flow channel portion and fixed to the valve housing. The first flow channel portion protrudes from the first seat portion toward the valve core. A first throttling channel is formed on the first flow channel portion. The valve core includes a second seat portion and a second flow channel portion. Multiple second seat portions are spaced apart along the outer periphery of the second flow channel portions. At least a portion of the communicating channel is provided between adjacent two second seat portions. The second flow channel portion protrudes from the second seat portion toward the valve seat. A second throttling channel is formed on the second flow channel portion. The elastic element is sleeved on the first flow channel portion and the second flow channel portion, and abuts against the first seat portion and the second seat portion.

8. The refrigeration system according to claim 6, characterized in that, The length of the first throttling channel is L1, the length of the second throttling channel is L2, 2≤L2 / L1≤3; and / or, 1.5mm≤L1≤5mm.

9. A variable frequency air conditioner, characterized in that, The system includes a variable frequency controller and a refrigeration system according to any one of claims 1-8, wherein the variable frequency controller is located outdoors and is used to adjust the operating frequency of the compressor of the refrigeration system, and the third heat exchanger is used to exchange heat with the variable frequency controller.

10. The variable frequency air conditioner according to claim 9, characterized in that, The third heat exchanger is a tubular structure, and is arranged around the outer periphery of the frequency converter, or the third heat exchanger is arranged through the frequency converter.

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