Two-way throttle valve, first air conditioning system and second air conditioning system

Abstract

The present invention relates to the field of valve technology, and in particular to a two-way throttle valve and an air conditioning system having the same. The two-way throttle valve includes a valve tube, a first valve core and an inner wall of a first valve port cooperate to form a first flow channel; a second valve core and an inner wall of the second valve port cooperate to form a second flow channel; when the first valve port and the second valve port are opened, the flow area of ​​the first flow channel is greater than the flow area of ​​the second flow channel, and the second valve core cooperates with the second valve port to achieve throttling. The present invention also provides an air conditioning system, which includes the above-mentioned two-way throttle valve. Compared with the prior art, the advantage of the present invention is that when the first valve port and the second valve port are opened, the flow area of ​​the first flow channel is greater than the flow area of ​​the second flow channel, thereby increasing the flow volume, so as to realize the two-way flow and one-way throttling function of the two-way throttle valve, and also to meet the requirements of low pressure and large flow under the defrosting condition.

Description

Technical Field

[0001] The present invention relates to the field of valve technology, and in particular to a two-way throttle valve, a first air-conditioning system and a second air-conditioning system. Background Art

[0002] Throttle valves are mainly used in air conditioning and refrigeration systems and are an important part of refrigeration systems. Bidirectional throttle valves are mainly used in cooling and heating air conditioning systems. Two throttle valve components are connected in parallel or in series to achieve a bidirectional flow function.

[0003] The existing one-way throttle valve and two-way throttle valve have limitations in function. The one-way throttle valve can only realize one-way circulation, while the two-way throttle valve has a small flow rate when realizing two-way circulation. It cannot meet the requirements of two-way circulation and one-way throttling of some models, as well as the requirements of low pressure and large flow on the defrosting side under defrosting conditions. Summary of the invention

[0004] In view of this, in order to solve the above technical problems, a two-way throttle valve is provided in one embodiment of the present invention.

[0005] In order to solve the above technical problems, the present invention provides the following technical solutions:

[0006] A two-way throttle valve comprises a valve tube, wherein a first valve core assembly and a second valve core assembly are respectively provided at two ends of the valve tube, wherein the first valve core assembly comprises a first valve core, wherein the first valve core assembly has a first valve port, the first valve core is movably disposed in the valve tube and is capable of opening / closing the first valve port, and the first valve core cooperates with an inner wall of the first valve port to form a first circulation channel; the second valve core assembly comprises a second valve core, wherein the second valve core assembly has a second valve port, the second valve core is movably disposed in the valve tube and is capable of opening / closing the second valve port, and the second valve core cooperates with an inner wall of the second valve port to form a second circulation channel; when the first valve port and the second valve port are opened, the circulation area of ​​the first circulation channel is greater than the circulation area of ​​the second circulation channel, and the second valve core cooperates with the second valve port to achieve throttling.

[0007] It can be understood that when the first valve port and the second valve port are opened, the present application increases the flow rate by making the flow area of ​​the first flow channel larger than the flow area of ​​the second flow channel, which not only can realize the two-way flow and one-way throttling functions of the two-way throttle valve, but also, when the two-way throttle valve is in a defrosting condition, can meet the requirements of low pressure and large flow under this condition.

[0008] In one embodiment, the valve pipe is connected to the air-conditioning system pipeline, and a connecting piece is also provided in the valve pipe, and the first valve core assembly is installed at one end of the connecting piece; the connecting piece is provided with a first channel, and the first channel is connected to the first valve port; the caliber at the first valve port is D1, the diameter of the first channel is D2, and the diameter of the air-conditioning system pipeline is D3, and D1, D2 and D3 satisfy the following relationship: D2≥D1≥D3.

[0009] It can be understood that by making the diameter D1 at the first valve port, the diameter D2 of the first channel and the diameter D3 of the air-conditioning system pipeline satisfy the relationship: D2≥D1≥D3, it is achieved that when the first valve port is opened, the first valve core assembly does not generate throttling and full circulation is achieved.

[0010] In one embodiment, the valve pipe is connected to the air-conditioning system pipeline, and a connecting piece is also provided in the valve pipe, and the first valve core assembly is installed at one end of the connecting piece; the diameter at the first valve port is D1, and the diameter of the air-conditioning system pipeline is D3, and D1 and D3 satisfy the following relationship: D1<D3.

[0011] It can be understood that by making the caliber D1 at the first valve port and the diameter D3 of the air conditioning system pipeline satisfy the relationship: D1<D3, it is achieved that when the first valve port is opened, the first valve core assembly partially throttles to achieve small hole throttling.

[0012] In one embodiment, the diameter of the second valve port is D4, and D1 and D4 satisfy the following relationship: D4>D1>(1 / 3)D4.

[0013] It can be understood that by making the diameter D1 at the first valve port and the diameter D4 at the second valve port satisfy the relationship: D4>D1>(1 / 3)D4, when the first valve port is opened, the first valve port further realizes small hole throttling.

[0014] In one embodiment, the first valve core assembly includes a first valve seat, the first valve core is movably disposed in the first valve seat, and the first valve port is opened in the first valve seat; a gap flow area S1 between a side wall of the first valve core and an inner wall of the first valve seat is greater than a flow area S2 at the first valve port.

[0015] It can be understood that by making the gap flow area S1 between the first valve core and the first valve seat larger than the flow area S2 at the first valve port, no throttling occurs at the first valve port, thereby increasing the flow rate at the first valve port.

[0016] In one embodiment, the second valve core assembly includes a second valve seat, the second valve core is movably disposed in the second valve seat, and the second valve port is opened in the second valve seat; the flow area of ​​the gap between the side wall of the second valve core and the inner wall of the second valve seat is smaller than the flow area at the second valve port.

[0017] It can be understood that by making the flow area of ​​the gap between the second valve core and the second valve seat smaller than the flow area at the second valve port, throttling is generated at the second valve port.

[0018] In one embodiment, the second valve core assembly includes a second valve seat, and the second valve core is movably arranged in the second valve seat; a second head and an elastic member are also provided in the second valve seat, and the second head is provided at an end of the second valve seat away from the first valve core assembly, and the two ends of the elastic member are respectively abutted against the second valve core and the second head, so that the second valve core has a tendency to reduce the flow area of ​​the second flow channel.

[0019] It is understandable that by arranging the elastic member in the second valve seat, the second valve core needs to overcome the elastic force of the elastic member while moving under the fluid pressure, thereby achieving throttling at the second valve port.

[0020] In one embodiment, the first channel is configured as a linear channel inclined relative to the axial direction of the connecting piece.

[0021] It can be understood that by configuring the first channel and the second channel as straight channels that are axially inclined relative to the connecting piece, the flow resistance of the fluid is smaller when flowing in the first channel and the second channel, thereby improving the stability of the two-way throttle valve.

[0022] In one embodiment of the present invention, the following technical solution is also provided:

[0023] A first air-conditioning system, the first air-conditioning system includes a compressor, a first heat exchanger, a second heat exchanger, a four-way valve and at least two two-way throttle valves, the two-way throttle valve includes a first two-way throttle valve and a second two-way throttle valve, the first heat exchanger is connected between the C port of the four-way valve and an end of the first two-way throttle valve close to its second valve core component, the second heat exchanger is connected between the E port of the four-way valve and an end of the second two-way throttle valve close to its second valve core component, the end of the first two-way throttle valve close to its first valve core component is connected to an end of the second two-way throttle valve close to its first valve core component, and the compressor is connected between the D port of the four-way valve and the S port of the four-way valve.

[0024] It can be understood that by connecting the first heat exchanger between the C port of the four-way valve and the end of the first two-way throttle valve close to the second valve core assembly, the second heat exchanger is connected between the E port of the four-way valve and the end of the second two-way throttle valve close to the second valve core assembly, the end of the first two-way throttle valve close to the first valve core assembly is connected to the end of the second two-way throttle valve close to the first valve core assembly, and the compressor is connected between the D port of the four-way valve and the S port of the four-way valve, thereby solving the problem of large cooling loss along the way when the system pipeline is long.

[0025] In one embodiment, there are at least two second heat exchangers and at least two second two-way throttle valves, each of the second heat exchangers is connected between the E port of the four-way valve and one end of each second two-way throttle valve close to its second valve core component, and one end of each second two-way throttle valve close to its first valve core component is connected to each other.

[0026] It can be understood that by connecting each of the second heat exchangers between the E port of the four-way valve and one end of each of the second two-way throttle valves close to its second valve core assembly, each of the second two-way throttle valves close to its first valve core assembly are connected to each other, thereby achieving the possibility of connecting multiple second two-way throttle valves in parallel in the air-conditioning system, which can be applied to one-to-many situations in the air-conditioning system.

[0027] In one embodiment of the present invention, the following technical solution is also provided:

[0028] A second air-conditioning system, the second air-conditioning system includes a compressor, a first heat exchanger, a second heat exchanger, a four-way valve and at least one two-way throttle valve, the first heat exchanger is connected between the E port of the four-way valve and the end of the two-way throttle valve close to the first valve core component, the second heat exchanger is connected between the C port of the four-way valve and the end of the two-way throttle valve close to the second valve core component, and the compressor is connected between the D port of the four-way valve and the S port of the four-way valve.

[0029] It can be understood that by connecting the first heat exchanger between the E port of the four-way valve and the end of the two-way throttle valve close to the first valve core assembly, connecting the second heat exchanger between the C port of the four-way valve and the end of the two-way throttle valve close to the second valve core assembly, and connecting the compressor between the D port of the four-way valve and the S port of the four-way valve, the problem of the need to significantly increase the refrigerant flow rate when defrosting the air conditioner under long-term cooling conditions is solved.

[0030] Compared with the prior art, the two-way throttle valve provided in one embodiment of the present invention, when the first valve port and the second valve port are opened, increases the flow volume by making the flow area of ​​the first flow channel larger than the flow area of ​​the second flow channel, thereby realizing the two-way flow and one-way throttling function of the two-way throttle valve, and also realizing that when the two-way throttle valve is in a defrosting condition, the requirements of low pressure and large flow under this condition are met. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] Figure 1 A schematic diagram of the structure of a two-way throttle valve provided by the present invention;

[0032] Figure 2 A schematic diagram of the bidirectional flow direction of the bidirectional throttle valve provided by the present invention;

[0033] Figure 3 A schematic diagram of the structure inside the valve tube of the two-way throttle valve provided by the present invention;

[0034] Figure 4 A schematic diagram of the structure of the connecting piece provided by the present invention;

[0035] Figure 5 A schematic structural diagram of a first valve seat provided by the present invention;

[0036] Figure 6 A schematic diagram of the structure of the second valve seat provided by the present invention;

[0037] Figure 7 for Figure 1 Schematic diagram of the cross-sectional structure at AA in the middle;

[0038] Figure 8 for Figure 1 Schematic diagram of the cross-sectional structure at BB in the middle;

[0039] Fig. 9 A schematic diagram of a first air conditioning system provided by the present invention;

[0040] Fig.10 for Fig. 9 A local enlarged schematic diagram of the X in the middle;

[0041] Fig.11 for Fig. 9 A partial enlarged schematic diagram of the Y in the middle;

[0042] Fig.12 A schematic diagram of a second air conditioning system provided by the present invention.

[0043] The symbols in the figure mean the following:

[0044] 100, two-way throttle valve; 10, valve tube; 11, first valve cavity; 12, second valve cavity; 20, first valve core assembly; 21, first valve seat; 211, first valve port; 212, first seat cavity; 22, first valve core; 23, first end cap; 30, second valve core assembly; 31, second valve seat; 311, second valve port; 312, second seat cavity; 32, second valve core; 33, second end cap; 34, elastic member; 40, connecting member; 41, first channel; 42, second channel; 43, first chamber; 44, second chamber; 200, air-conditioning system; 201, first air-conditioning system; 202, second air-conditioning system; 50, compressor; 60, first heat exchanger; 61, second heat exchanger; 70, four-way valve; 80, first two-way throttle valve; 81, second two-way throttle valve; 90, air-conditioning system pipeline. DETAILED DESCRIPTION

[0045] In order to make the purpose, technical solution and advantages of the present invention more clearly understood, the present invention is further described in detail below in conjunction with the accompanying drawings and specific implementation methods. It should be understood that the specific implementation methods described herein are only used to explain the present invention and do not limit the scope of protection of the present invention.

[0046] It should be noted that when a component is referred to as being "mounted on" another component, it may be directly on the other component or there may also be a centered component. When a component is considered to be "set on" another component, it may be directly set on the other component or there may also be a centered component. When a component is considered to be "fixed to" another component, it may be directly fixed on the other component or there may also be a centered component. The terms "vertical", "horizontal", "left", "right" and similar expressions used herein are for illustrative purposes only and do not represent the only implementation method.

[0047] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as those commonly understood by those skilled in the art of the present invention. The terms used herein in the specification of the present invention are only for the purpose of describing specific embodiments and are not intended to limit the present invention. The term "or / and" used herein includes any and all combinations of one or more related listed items.

[0048] See also Figures 1 to 12 In one embodiment of the present invention, a two-way throttle valve 100 is provided. The two-way throttle valve 100 is applied to an air-conditioning system 200. The two-way throttle valve 100 is mainly applied to a cooling and heating type air-conditioning system 200. Two throttle valve components are arranged in parallel or in series to realize a two-way flow function.

[0049] The existing one-way throttle valve and two-way throttle valve have limitations in function. The one-way throttle valve can only realize one-way circulation, while the two-way throttle valve has a small flow rate when realizing two-way circulation. It cannot meet the requirements of two-way circulation and one-way throttling of some models, as well as the requirements of low pressure and large flow on the defrosting side under defrosting conditions.

[0050] In order to solve the problems existing in the existing two-way throttle valve, a two-way throttle valve 100 is provided in one embodiment of the present invention, including a valve tube 10, wherein the first valve core assembly 20 and the second valve core assembly 30 are respectively provided at both ends of the valve tube 10, the first valve core assembly 20 includes a first valve core 22, and the first valve core assembly 20 has a first valve port 211, the first valve core 22 is movably arranged in the valve tube 10 and can open / close the first valve port 211, and the first valve core 22 cooperates with the inner wall of the first valve port 211 to form a first flow Through channel; the second valve core assembly 30 includes a second valve core 32, and the second valve core assembly 30 has a second valve port 311. The second valve core 32 is movably arranged in the valve tube 10 and can open / close the second valve port 311. The second valve core 32 and the inner wall of the second valve port 311 cooperate to form a second circulation channel; when the first valve port 211 and the second valve port 311 are opened, the circulation area of ​​the first circulation channel is greater than the circulation area of ​​the second circulation channel, and the second valve core 32 and the second valve port 311 cooperate to achieve throttling.

[0051] When the first valve port 211 and the second valve port 311 are opened, the present application increases the flow volume by making the flow area of ​​the first flow channel larger than the flow area of ​​the second flow channel, thereby not only realizing the two-way flow and one-way throttling function of the two-way throttle valve 100, but also, when the two-way throttle valve 100 is in a defrosting condition, it can also meet the requirements of low pressure and large flow under this condition.

[0052] like Figure 1 As shown, a connecting piece 40 is also provided in the valve tube 10. The connecting piece 40 is provided in the valve tube 10 and divides the interior of the valve tube 10 into a first valve cavity 11 and a second valve cavity 12. The connecting piece 40 is provided with a first chamber 43, a second chamber 44, a first channel 41 and a second channel 42. The first chamber 43 is located at one end of the connecting piece 40 close to the first valve cavity 11, and the second chamber 44 is located at one end of the connecting piece 40 close to the second valve cavity 12. The first channel 41 connects the first chamber 43 and the second valve cavity 12, and the second channel 42 connects the second chamber 44 and the first valve cavity 11. The first valve core assembly 20 is installed in the first chamber 43 to automatically adjust the flow rate between the first channel 41 and the first valve cavity 11. The second valve core assembly 30 is installed in the second chamber 44 to adjust the flow rate between the second channel 42 and the second valve cavity 12.

[0053] like Figure 2As shown, when the two-way throttle valve 100 is working, the fluid can enter the second channel 42 from the first valve cavity 11, then enter the second chamber 44, then enter the second valve core assembly 30, and finally enter the second valve cavity 12. The fluid can also enter the first channel 41 from the second valve cavity 12, then enter the first chamber 43, then enter the first valve core assembly 20, and finally enter the first valve cavity 11. In this way, the two-way throttle valve 100 can achieve a two-way flow function through the valve tube 10, the connecting piece 40, the first valve core assembly 20 and the second valve core assembly 30, with fewer parts and a very simple structure. During installation, it is only necessary to install the connecting piece 40 in the valve tube 10, and install the first valve core assembly 20 and the second valve core assembly 30 at both ends of the connecting piece 40 respectively, so as to complete the assembly of the two-way throttle valve 100. The installation process is also very simple, which reduces the probability of defects in the assembly process, is conducive to improving product consistency, and thus greatly reduces the production cost of the two-way throttle valve 100. "Product consistency" means that different products remain basically the same during batch production.

[0054] like Figure 3 and Figure 4 As shown, the first channel 41 is configured as a straight channel inclined relative to the axial direction of the connecting member 40. In this way, when the fluid flows in the first channel 41, the flow resistance is small, so that the stability of the two-way throttle valve 100 is better. Correspondingly, the second channel 42 is also configured as a straight channel inclined relative to the axial direction of the connecting member 40. Similarly, when the fluid flows in the second channel 42, the flow resistance is small, so that the stability of the two-way throttle valve 100 is better.

[0055] In this embodiment, the connecting piece 40, the first valve core assembly 20 and the second valve core assembly 30 are coaxially arranged. The coaxial arrangement makes the connecting piece 40, the first valve core assembly 20 and the second valve core assembly 30 occupy a smaller space as a whole, which is conducive to the miniaturization design of the valve tube 10 and greatly reduces the occupied space of the two-way throttle valve 100.

[0056] like Figure 5As shown, the first valve core assembly 20 includes a first valve seat 21. The first valve seat 21 has a first seat cavity 212, the first valve core 22 is movably arranged in the first seat cavity 212, and the first valve port 211 is opened in the first valve seat 21. The first valve seat 21 is provided with a first end cap 23 at one end away from the second valve core assembly 30, and a gap connecting the first seat cavity 212 and the first valve cavity 11 is left between the first end cap 23 and the first valve seat 21 for fluid to pass through. When the flow area of ​​the first valve port 211 is reduced to zero, the first valve port 211 is closed. When the fluid pressure in the first channel 41 is greater than the self-weight of the first valve core 22, the fluid pushes the first valve core 22 to move, thereby opening the first valve port 211 or increasing the flow area of ​​the first valve port 211, and the fluid flows from the first channel 41 through the first valve port 211 and the first seat cavity 212 in sequence, and finally enters the first valve cavity 11. When the fluid pressure in the first channel 41 is less than the self-weight of the first valve core 22 , the first valve core 22 moves in the reverse direction and reduces the flow area of ​​the first valve port 211 , or even closes the first valve port 211 .

[0057] like Figure 6 As shown, the second valve core assembly 30 includes a second valve seat 31. The second valve seat 31 has a second seat cavity 312, the second valve core 32 is movably arranged in the second seat cavity 312, and the second valve port 311 is opened in the second valve seat 31. The second valve seat 31 is provided with a second head 33 at one end cover away from the first valve core assembly 20, and a gap connecting the second seat cavity 312 and the second valve cavity 12 is left between the second head 33 and the second valve seat 31 for fluid to pass through.

[0058] Furthermore, an elastic member 34 is also provided in the second valve seat 31, and the two ends of the elastic member 34 are respectively in contact with the second valve core 32 and the second end cap 33, so that the second valve core 32 has a tendency to reduce the flow area of ​​the second flow channel. When the flow area of ​​the second valve port 311 is zero, the second valve port 311 is in a closed state, and when the flow area of ​​the second valve port 311 is greater than zero, the second valve port 311 is in an open state. Adjusting the size of the flow area of ​​the second valve port 311 includes both adjusting the size of the flow area in the open state of the second valve port 311 and switching the second valve port 311 between the open state and the closed state. When the flow area of ​​the second valve port 311 is reduced to zero, the second valve port 311 is closed. When the fluid pressure in the second channel 42 is greater than the elastic force of the elastic member 34, the fluid pushes the second valve core 32 to move, thereby compressing the elastic member 34 and opening the second valve port 311 or increasing the flow area of ​​the second valve port 311. The greater the fluid pressure in the second channel 42, the greater the flow area of ​​the second valve port 311, so that the fluid flows from the second channel 42 through the second valve port 311 and the second seat cavity 312 in sequence, and finally enters the second valve cavity 12. When the fluid pressure in the second channel 42 is less than the elastic force of the elastic member 34, under the elastic restoring force of the elastic member 34, the second valve core 32 moves in the opposite direction and reduces the flow area of ​​the second valve port 311, or even closes the third valve port.

[0059] Since the existing two-way throttle valve is usually a two-way flow and two-way throttling structure, the flow rate of the fluid is usually small. Under the defrosting condition in the air-conditioning system 200, a sufficient amount of fluid is usually required to defrost the condensed water in the air-conditioning system 200. If the two-way throttle valve 100 is in the case of two-way throttling, the large flow requirement under the defrosting condition cannot be met at all.

[0060] The specific implementation method is that, in the two valve core components in the two-way throttle valve 100, one valve core component is set to a full flow or small hole throttling structure, and the other valve core component is set to a throttling structure. It should be noted that the flow volume of the full flow or small hole throttling structure is greater than that of the throttling structure. In this way, the two-way throttle valve 100 can meet both throttling and large flow under defrosting conditions.

[0061] In this embodiment, the first valve core component 20 is set to a full flow or small hole throttling structure. Of course, in other embodiments, the second valve core component 30 can also be set to a full flow or small hole throttling structure, which is not limited here.

[0062] When the first valve core assembly 20 achieves full circulation, the diameter of the first valve port 211 is D1, the diameter of the first channel 41 is D2, the diameter of the air conditioning system pipeline 90 is D3, and D1, D2 and D3 satisfy the relationship: D2≥D1≥D3. When designing the diameters of the first valve port 211 and the first channel 41, D1, D2 and D3 satisfy the relationship: D2≥D1≥D3, so that when the first valve port 211 is opened, the first valve core assembly 20 does not generate throttling and achieves full circulation.

[0063] It should be noted that when the fluid flows from the air-conditioning system pipeline 90 into the second valve chamber 12, the fluid flows from the gap between the second valve seat 31 and the valve tube 10 into the first channel 41. Since the diameter of the first channel 41 is larger than the diameter of the air-conditioning system pipeline 90, the flow channel area becomes larger at this time, achieving full circulation.

[0064] When the first valve core assembly 20 realizes small hole throttling, the caliber at the first valve port 211 is D1, the diameter of the air conditioning system pipeline 90 is D3, and D1 and D3 satisfy the following relationship: D1<D3. When designing the caliber of the first valve port 211, D1 and D3 satisfy the relationship: D1<D3, so that when the first valve port 211 is opened, the first valve core assembly 20 partially throttles and realizes small hole throttling.

[0065] It should be noted that when the fluid flows from the air-conditioning system pipeline 90 into the second valve chamber 12, the fluid flows from the gap between the second valve seat 31 and the valve tube 10 into the first valve port 211. Since the diameter of the first valve port 211 is smaller than the diameter of the air-conditioning system pipeline 90, the flow channel area becomes smaller at this time, thereby achieving small-hole throttling.

[0066] Furthermore, in order to better realize the small hole throttling of the first valve core assembly 20, the caliber of the second valve port 311 is D4, and D1 and D4 satisfy the relationship: D4>D1>(1 / 3)D4. When designing the calibers of the first valve port 211 and the second valve port 311, D1 and D4 satisfy the relationship: D4>D1>(1 / 3)D4, so that when the first valve port 211 is opened, the small hole throttling is further realized at the first valve port 211.

[0067] It is worth noting that for the second valve core assembly 30 which is set as a throttling structure, when the fluid flows into the first valve cavity 11 from the air conditioning system pipeline 90, the fluid flows into the second valve port 311 from the gap between the first valve seat 21 and the valve tube 10. Since the diameter of the second valve port 311 is also smaller than the diameter of the air conditioning system pipeline 90, the flow channel area is also reduced at this time, thereby achieving throttling. So why is the flow volume of the second valve core assembly 30 still smaller than the flow volume of the first valve core assembly 20 when it is designed as a small hole throttling? It mainly lies in the following differences in the structure between the first valve core assembly 20 and the second valve core assembly 30.

[0068] like Figures 7 and 8 As shown, first of all, there is a difference in the flow area. The flow area S1 of the gap between the side wall of the first valve core 22 and the inner wall of the first valve seat 21 is larger than the flow area S2 at the first valve port 211. The flow area of ​​the gap between the side wall of the second valve core 32 and the inner wall of the second valve seat 31 is smaller than the flow area at the second valve port 311. Based on this, it can be seen that due to the pressure difference, the process of the fluid pushing open the first valve core 22 is obviously easier than the process of the fluid pushing open the second valve core 32. The opening channel area of ​​the first valve port 211 is larger than the opening channel area of ​​the second valve port 311. Therefore, the flow volume of the first valve core assembly 20 is greater than the flow volume of the second valve core assembly 30.

[0069] The second difference is about the elastic structure. That is, the first seat cavity 212 is only provided with the first valve core 22 that can move in the first seat cavity 212, that is, when the fluid pushes the first valve core 22 away from the first valve port 211, it only needs to overcome the gravity of the first valve core 22 itself, and because the first valve core 22 is not connected to other components, after the fluid pushes the first valve core 22 away, unless the impact force of the fluid gradually becomes smaller than the gravity of the first valve core 22, the first valve core 22 will not move toward the direction of the first valve port 211, and at this time, a large flow rate is achieved at the first valve port 211; the second seat cavity 3 In addition to the second valve core 32, 12 is also provided with an elastic member 34 whose two ends are respectively connected to the second head 33 and the second valve core 32. That is to say, when the fluid pushes the second valve core 32 away from the second valve port 311, in addition to overcoming the self-gravity of the second valve core 32, it is also necessary to overcome the elastic force of the elastic member 34. Moreover, after the fluid pushes the second valve core 32 away, the second valve core 32 will have a tendency to move toward the second valve port 311 due to the elastic restoring force of the elastic member 34, and this tendency will also cause the flow rate at the second valve port 311 to gradually decrease.

[0070] In summary, due to the difference in flow area and elastic structure between the first valve core assembly 20 and the second valve core assembly 30, even though the first valve port 211 is designed as a small hole throttling structure, the flow rate at the first valve port 211 is still greater than the flow rate at the second valve port 311.

[0071] Preferably, the elastic member 34 is a spring; of course, in other embodiments, the elastic member 34 may also adopt other elastic structures, which are not limited here.

[0072] like Figures 9 to 11As shown, the present invention also provides a first air-conditioning system 201, which includes a compressor 50, a first heat exchanger 60, a second heat exchanger 61, a four-way valve 70 and a two-way throttle valve 100, the two-way throttle valve 100 includes a first two-way throttle valve 80 and a second two-way throttle valve 81, the first heat exchanger 60 is connected between the C port of the four-way valve 70 and one end of the second valve core assembly 30 of the first two-way throttle valve 80 close to the first two-way throttle valve 80, the second heat exchanger 61 is connected between the E port of the four-way valve 70 and one end of the second valve core assembly 30 of the second two-way throttle valve 81 close to the second two-way throttle valve 81, one end of the first valve core assembly 20 of the first two-way throttle valve 80 close to the first two-way throttle valve 80 is connected to one end of the first valve core assembly 20 of the second two-way throttle valve 81 close to the second two-way throttle valve 81, and the compressor 50 is connected between the D port of the four-way valve 70 and the S port of the four-way valve 70.

[0073] The first air conditioning system 201 is mainly a system with many components and a long air conditioning system pipeline 90, and the two-way throttle valve 100 suitable for use at this time is a two-way throttle valve 100 with throttling at one end and full circulation at the other end. When the first air conditioning system 201 is cooling, the low-temperature and low-pressure gas is compressed by the compressor 50 to form a high-temperature and high-pressure gas. The high-temperature and high-pressure gas enters the first heat exchanger 60 through the four-way valve 70, and is condensed into a medium-temperature and high-pressure liquid through the first heat exchanger 60. The medium-temperature and high-pressure liquid enters the second valve cavity 12 of the first two-way throttle valve 80, and then flows into the first channel 41 through the gap between the second valve seat 31 and the valve tube 10, and then enters the first valve port 211. At this time, the medium-temperature and high-pressure liquid pushes the first valve core 22 open, enters the second seat cavity, and then enters the first valve cavity 11. Since the fluid is fully circulated at the first valve port 211, the medium-temperature and high-pressure liquid flowing through the first two-way throttle valve 80 at this time is only relatively When flowing through an air-conditioning system pipeline 90, there is no throttling effect. The medium-temperature and high-pressure liquid flows out of the first valve cavity 11 of the first two-way throttle valve 80 and then flows into the first valve cavity 11 of the second two-way throttle valve 81, flows into the second channel 42 through the gap between the first valve seat 21 and the valve tube 10, and then flows into the second valve port 311, pushes the second valve core 32 open and flows into the second seat cavity 312, and finally enters the second valve cavity 12. The medium-temperature and high-pressure liquid is throttled to a low-temperature and low-pressure liquid at the second valve port 311, and then enters the second heat exchanger 61, evaporates through the second heat exchanger 61 to form a low-temperature and low-pressure gas, and finally enters the compressor 50 through the four-way valve 70, thereby completing the refrigeration cycle.

[0074] When the first air conditioning system 201 is heating, the low-temperature and low-pressure gas is compressed by the compressor 50 to form a high-temperature and high-pressure gas. The high-temperature and high-pressure gas enters the second heat exchanger 61 through the four-way valve 70, and releases heat through the second heat exchanger 61 to become a medium-temperature and high-pressure liquid. The medium-temperature and high-pressure liquid enters the second valve cavity 12 of the second two-way throttle valve 81, and then flows into the first channel 41 through the gap between the second valve seat 31 and the valve tube 10, and then enters the first valve port 211. At this time, the medium-temperature and high-pressure liquid pushes the first valve core 22 open, enters the first seat cavity 212, and then enters the first valve cavity 11. Since the fluid is fully circulated at the first valve port 211, the medium-temperature and high-pressure liquid flowing through the second two-way throttle valve 81 at this time is only equivalent to It flows through an air-conditioning system pipeline 90 without a throttling effect. The medium-temperature and high-pressure gas flows out of the first valve cavity 11 of the second two-way throttle valve 81 and then flows into the first valve cavity 11 of the first two-way throttle valve 80, flows into the second channel 42 through the gap between the first valve seat 21 and the valve tube 10, and then flows into the second valve port 311, pushes the second valve core 32 open and flows into the second seat cavity 312, and finally enters the second valve cavity 12. The medium-temperature and high-pressure liquid is throttled to a low-temperature and low-pressure liquid or a gas-liquid two-phase medium at the second valve port 311, and then enters the first heat exchanger 60, evaporates through the first heat exchanger 60 to form a low-temperature and low-pressure gas, and finally enters the compressor 50 through the four-way valve 70, thereby completing the heating cycle.

[0075] It is worth noting that the pipelines connecting the second heat exchanger 61 and the second two-way throttle valve 81 in series can be connected in parallel in multiple numbers, and the specific number depends on the specific situation of the air-conditioning system 200. That is, the first air-conditioning system 201 includes at least two second heat exchangers 61 and at least two second two-way throttle valves 81, each of the second heat exchangers 61 is connected between the E port of the four-way valve 70 and one end of the second valve core assembly 30 of each second two-way throttle valve 81 close to the second two-way throttle valve 81, and one end of the first valve core assembly 20 of each second two-way throttle valve 81 close to the second two-way throttle valve 81 is connected to each other.

[0076] The two-way throttle valve 100 with full circulation of the first valve core component 20 and throttling of the second valve core component 30 is applied to the first air-conditioning system 201, and is mainly used in one-to-many situations to solve the problem of large cooling loss along the way when the cooling and heating cycles share one two-way throttle valve 100 when the air-conditioning system pipeline 90 is long.

[0077] like Fig.12As shown, the present invention also provides a second air-conditioning system 202, which includes a compressor 50, a first heat exchanger 60, a second heat exchanger 61, a four-way valve 70 and a two-way throttle valve 100, the first heat exchanger 60 is connected between the E port of the four-way valve 70 and one end of the first valve core assembly 20 of the two-way throttle valve 100 close to the two-way throttle valve 100, the second heat exchanger 61 is connected between the C port of the four-way valve 70 and one end of the second valve core assembly 30 of the two-way throttle valve 100 close to the two-way throttle valve 100, and the compressor 50 is connected between the D port of the four-way valve 70 and the S port of the four-way valve 70.

[0078] The second air conditioning system 202 is mainly a system with fewer components and a shorter air conditioning system pipeline 90, and the two-way throttle valve 100 applicable at this time is a two-way throttle valve 100 with throttling at one end and small holes at the other end. When the second air conditioning system 202 is cooling, the low-temperature and low-pressure gas is compressed by the compressor 50 to form a high-temperature and high-pressure gas. The high-temperature and high-pressure gas enters the first heat exchanger 60 through the four-way valve 70 and is condensed into a medium-temperature and high-pressure liquid through the first heat exchanger 60. The medium-temperature and high-pressure liquid enters the first valve cavity 11 of the two-way throttle valve 100, and then flows into the second channel 42 through the gap between the first valve seat 21 and the valve tube 10, and then enters the second valve port 311. At this time, the medium-temperature and high-pressure liquid pushes the second valve core 32 up. Opens, enters the second seat cavity 312, and then enters the second valve cavity 12. Since the fluid is throttled at the second valve port 311, the medium-temperature and high-pressure liquid flows through the two-way throttle valve 100 and is throttled into a low-temperature and low-pressure liquid or a low-temperature and low-pressure gas-liquid two-phase state, and then flows out of the second valve cavity 12 of the two-way throttle valve 100 and flows into the second heat exchanger 61. It evaporates in the second heat exchanger 61 to form a low-temperature and low-pressure steam, and finally enters the compressor 50 through the four-way valve 70, thereby completing the refrigeration cycle.

[0079] When the second air conditioning system 202 is defrosted, the low-temperature and low-pressure gas is compressed by the compressor 50 to form a high-temperature and high-pressure gas. The high-temperature and high-pressure gas enters the second heat exchanger 61 through the four-way valve 70 and is condensed into a medium-temperature and high-pressure liquid through the second heat exchanger 61. The medium-temperature and high-pressure liquid enters the second valve cavity 12 of the two-way throttle valve 100, and then flows into the first channel 41 through the gap between the second valve seat 31 and the valve pipe 10, and then enters the first valve port 211. At this time, the medium-temperature and high-pressure liquid pushes the first valve core 22 open and enters The fluid flows into the first seat cavity 212 and then into the first valve cavity 11. Since the fluid is throttled into a low-temperature and low-pressure liquid or a gas-liquid two-phase medium by a small hole at the first valve port 211, the flow area increases at this time, and the fluid volume increases accordingly. The low-temperature and low-pressure liquid or gas-liquid two-phase medium flows out of the first valve cavity 11 of the two-way throttle valve 100 and then flows into the first heat exchanger 60. It evaporates through the first heat exchanger 60 to form a low-temperature and low-pressure gas, and finally enters the compressor 50 through the four-way valve 70, thereby completing the defrost cycle.

[0080] The two-way throttle valve 100 with small-hole throttling of the first valve core component 20 and throttling of the second valve core component 30 is applied to the second air-conditioning system 202, mainly used in refrigeration and freezing occasions, to solve the problem that the refrigerant flow rate needs to be greatly increased when the air-conditioning system 200 is defrosted in a long-term refrigeration environment.

[0081] It should be explained that the above-mentioned air-conditioning system 200 is either the first air-conditioning system 201 or the second air-conditioning system 202 .

[0082] The two-way throttle valve 100 provided by the present invention, when the first valve port 211 and the second valve port 311 are opened, by making the flow area of ​​the first flow channel larger than the flow area of ​​the second flow channel, not only can the two-way flow and one-way throttling function of the two-way throttle valve 100 be realized, but also, when the two-way throttle valve 100 is in a defrosting condition, the requirements of low pressure and large flow under this condition can be met.

[0083] The technical features of the above-described embodiments may be arbitrarily combined. To make the description concise, not all possible combinations of the technical features in the above-described embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0084] The above-mentioned embodiments only express several implementation methods of the present invention, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the invention patent. It should be pointed out that, for ordinary technicians in this field, several variations and improvements can be made without departing from the concept of the present invention, and these all belong to the protection scope of the present invention. Therefore, the protection scope of the patent of the present invention shall be subject to the attached claims.

Claims

1. A two-way throttle valve, comprising a valve tube (10), wherein two ends of the valve tube (10) are respectively provided with a first valve core assembly (20) and a second valve core assembly (30), wherein the first valve core assembly (20) comprises a first valve core (22), wherein the first valve core assembly (20) has a first valve port (211), wherein the first valve core (22) is movably arranged in the valve tube (10) and is capable of opening / closing the first valve port (211), wherein the first valve core (22) and the inner wall of the first valve port (211) cooperate to form a first flow channel; The second valve core assembly (30) comprises a second valve core (32), the second valve core assembly (30) has a second valve port (311), the second valve core (32) is movably arranged in the valve tube (10) and is capable of opening / closing the second valve port (311), and the second valve core (32) and the inner wall of the second valve port (311) cooperate to form a second flow channel; It is characterized in that When the first valve port (211) and the second valve port (311) are opened, the flow area of ​​the first flow channel is greater than the flow area of ​​the second flow channel, and the second valve core (32) cooperates with the second valve port (311) to achieve throttling; The valve pipe (10) is connected to an air conditioning system pipeline (90); a connecting piece (40) is further provided in the valve pipe (10); the first valve core assembly (20) is installed at one end of the connecting piece (40); the connecting piece (40), the first valve core assembly (20) and the second valve core assembly (30) are coaxially arranged; The diameter of the first valve port (211) is D1, the diameter of the air conditioning system pipeline (90) is D3, and D1 and D3 satisfy the following relationship: D1<D3; Alternatively, the connecting piece (40) is provided with a first channel (41), the first channel (41) being connected to the first valve port (211); the diameter of the first channel (41) is D2, and D1, D2 and D3 satisfy the following relationship: D2≥D1≥D3.

2. The two-way throttle valve according to claim 1, characterized in that: The diameter of the second valve port (311) is D4, and D1 and D4 satisfy the following relationship: D4>D1>(1 / 3)D4.

3. The two-way throttle valve according to claim 1, characterized in that: The first valve core assembly (20) comprises a first valve seat (21), the first valve core (22) is movably disposed in the first valve seat (21), and the first valve port (211) is opened in the first valve seat (21); A flow area S1 of a gap between a side wall of the first valve core (22) and an inner wall of the first valve seat (21) is larger than a flow area S2 at the first valve port (211).

4. The two-way throttle valve according to claim 1, characterized in that: The second valve core assembly (30) comprises a second valve seat (31), the second valve core (32) is movably disposed in the second valve seat (31), and the second valve port (311) is opened in the second valve seat (31); The flow area of ​​the gap between the side wall of the second valve core (32) and the inner wall of the second valve seat (31) is smaller than the flow area at the second valve port (311).

5. The two-way throttle valve according to claim 1, characterized in that: The second valve core assembly (30) comprises a second valve seat (31), and the second valve core (32) is movably disposed in the second valve seat (31); A second sealing head (33) and an elastic member (34) are provided in the second valve seat (31); the second sealing head (33) is provided at an end of the second valve seat (31) away from the first valve core assembly (20); two ends of the elastic member (34) are respectively abutted against the second valve core (32) and the second sealing head (33), so that the second valve core (32) has a tendency to reduce the flow area of ​​the second flow channel.

6. The two-way throttle valve according to claim 1, characterized in that: The first channel (41) is configured as a linear channel inclined relative to the axial direction of the connecting piece (40).

7. A first air conditioning system, characterized in that: The first air conditioning system comprises a compressor (50), a first heat exchanger (60), a second heat exchanger (61), a four-way valve (70) and at least two two-way throttle valves according to any one of claims 1 and 3 to 5, wherein the two-way throttle valve comprises a first two-way throttle valve (80) and a second two-way throttle valve (81), wherein the first heat exchanger (60) is connected between the C port of the four-way valve (70) and an end of the first two-way throttle valve (80) close to the second valve core assembly (30), the second heat exchanger (61) is connected between the E port of the four-way valve (70) and an end of the second two-way throttle valve (81) close to the second valve core assembly (30), an end of the first two-way throttle valve (80) close to the first valve core assembly (20) is connected to an end of the second two-way throttle valve (81) close to the first valve core assembly (20), and the compressor (50) is connected between the D port of the four-way valve (70) and the S port of the four-way valve (70).

8. The first air conditioning system according to claim 7, characterized in that: There are at least two second heat exchangers (61), and there are at least two second two-way throttle valves (81). Each of the second heat exchangers (61) is connected between the E port of the four-way valve (70) and one end of each second two-way throttle valve (81) close to its second valve core assembly (30), and one end of each second two-way throttle valve (81) close to its first valve core assembly (20) is connected to each other.

9. A second air conditioning system, characterized in that: The second air-conditioning system comprises a compressor (50), a first heat exchanger (60), a second heat exchanger (61), a four-way valve (70) and at least one two-way throttle valve as described in any one of claims 1 to 5, wherein the first heat exchanger (60) is connected between the E port of the four-way valve (70) and an end of the two-way throttle valve close to the first valve core assembly (20), the second heat exchanger (61) is connected between the C port of the four-way valve (70) and an end of the two-way throttle valve close to the second valve core assembly (30), and the compressor (50) is connected between the D port of the four-way valve (70) and the S port of the four-way valve (70).

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