Throttle valve

Abstract

The utility model relates to the technical field of valves, in particular to a throttling valve. The throttling valve comprises a first valve element assembly, the first valve element assembly comprises a first valve seat, a first valve element and an elastic piece, the first valve seat is provided with a first opening, a first valve port and a first containing hole, the first valve element and the elastic piece are arranged in the first containing hole, and one end of the first valve element is connected to the first valve seat through the elastic piece; and the other end is movably matched with the first valve port so as to adjust the flow at the first valve port. When the elastic piece pushes the first valve element to move to the limit in the direction close to the first valve port, a gap is formed between the first valve element and the first valve port in the radial direction of the first valve element assembly. According to the throttling valve, the problem that an existing throttling valve is high in valve opening difficulty under the low-pressure-difference working condition is solved.

Description

Technical Field

[0001] The present application relates to the field of valve technology, and in particular to a throttle valve. Background Art

[0002] Throttle valves are often used in air-conditioning systems to adjust the flow of refrigerant. In related technologies, throttle valves usually include a valve seat, a valve core, and an elastic member. The valve seat is provided with a valve port. The valve core and the elastic member are both installed in the valve seat. The valve core moves in the valve seat under the elastic force of the elastic member and the pressure of the refrigerant to open and close the valve port. However, when the throttle valve is in a closed state, the valve core is often pressed against the valve port under the action of the elastic member, which results in a large pressure difference being required to overcome the elastic force of the elastic member when opening the valve, thereby increasing the difficulty of opening the valve. Utility Model Content

[0003] Based on this, it is necessary to provide a throttle valve to solve the problem that the existing throttle valve is difficult to open under low pressure difference conditions.

[0004] The present application provides a throttle valve, which includes a valve tube and a first valve core assembly, wherein the valve tube has a first valve cavity, and the first valve core assembly is installed in the first valve cavity; the first valve core assembly includes a first valve seat, a first valve core and an elastic member, wherein the first valve seat is provided with a first opening, a first valve port and a first accommodating hole communicating with the first opening and the first valve port, and the first opening is communicated with the first valve cavity; the first valve core and the elastic member are arranged in the first accommodating hole, and one end of the first valve core is connected to the first valve seat through the elastic member, and the other end is movably matched with the first valve port to adjust the flow rate at the first valve port; wherein, when the first valve core moves in a direction away from the first valve port, the elastic member has a tendency to push the first valve core to move toward the first valve port to reset, and when the elastic member pushes the first valve core to move toward the first valve port to a limit, there is a gap between the first valve core and the first valve port along the radial direction of the first valve core assembly.

[0005] In one embodiment, the first valve core includes a main body and a throttling portion, one end of the throttling portion is connected to the main body and the elastic member through the main body, and the other end is movably engaged with the first valve port; wherein the throttling portion includes a plurality of throttling sections connected in sequence, and along the axial direction of the first valve core and in the direction from the main body to the throttling portion, the cross-sectional areas of the plurality of throttling sections tend to decrease in sequence.

[0006] In one embodiment, the number of the throttling sections is five, and the five throttling sections are respectively defined as a first throttling section, a second throttling section, a third throttling section, a fourth throttling section and a fifth throttling section from the main body to the throttling section; wherein the first throttling section, the third throttling section, the fourth throttling section and the fifth throttling section all extend in a columnar shape, and along the axial direction of the first valve core and in the direction from the main body to the throttling section, the cross-sectional area of ​​the second throttling section gradually decreases.

[0007] In one embodiment, the first throttling section is configured to work in response to the system pressure difference △P1, and 0<△P1<0.3MPa; wherein, the inner diameter d of the first valve port, the stiffness coefficient k of the elastic member, the outer diameter d1 of the first throttling section, the vertical distance h1 from the end of the first throttling section away from the main body to the main body, and the flow rate Q1 of the first valve port when the first throttling section is working, satisfy, 0.942d<d1<0.95d, h1=△P1*πd 2 / 4 / k, Q1=100*△P1*(πd 2 / 4-πd1 2 / 4).

[0008] In one embodiment, the second throttling section is configured to work in response to the system pressure difference ΔP2, and 0.4MPa<ΔP2<1.4MPa; wherein, when the second throttling section is in the working state, the diameter of the circle where the outer surface of the second throttling section at the corresponding position of the first valve port is defined as d x , the vertical distance from any particle on the circle to the main body is h x , and the outer diameter d3 of the third throttling section, the vertical distance h2 from one end of the second throttling section away from the main body to the main body, and the flow rate Q2 of the first valve port when the second throttling section is working, satisfy, 0.942d<d x <0.819d,h2=△P2*πd 2 / 4 / k,d x =[d3 2 -h x *(d1 2 -d3 2 ) / (h2-h1)] 1 / 2 , Q2=100*△P2*(πd 2 / 4-πd x 2 / 4).

[0009] In one embodiment, the third throttling section is configured to work in response to the system pressure difference △P3, and 1.5MPa<△P3<1.8MPa; wherein, the inner diameter d of the first valve port, the stiffness coefficient k of the elastic member, the outer diameter d3 of the third throttling section, the vertical distance h3 from one end of the third throttling section away from the main body to the main body, and the flow rate Q3 of the first valve port when the third throttling section is working, satisfy, 0.811d<d3<0.819d, h3=△P3*πd 2 / 4 / k, Q3=100*△P3*(πd 2 / 4-πd3 2 / 4).

[0010] In one embodiment, the fourth throttling section is configured to work in response to the system pressure difference △P4, and 2MPa<△P4<2.3MPa; wherein, the inner diameter d of the first valve port, the stiffness coefficient k of the elastic member, the outer diameter d4 of the fourth throttling section, the vertical distance h4 from one end of the fourth throttling section away from the main body to the main body, and the flow rate Q4 of the first valve port when the fourth throttling section is working, satisfy, 0.635d<d4<0.642d, h4=△P4*πd 2 / 4 / k, Q4=100*△P4*(πd 2 / 4-πd4 2 / 4).

[0011] In one embodiment, the fifth throttling section is configured to work in response to the system pressure difference △P5, and 2.4MPa<△P5<3.2MPa; wherein, the inner diameter d of the first valve port, the stiffness coefficient k of the elastic member, the outer diameter d5 of the fifth throttling section, the vertical distance h5 from one end of the fifth throttling section away from the main body to the main body, and the flow rate Q5 of the first valve port when the fifth throttling section is working, satisfy, 0.488d<d5<0.496d, h5=△P5*πd 2 / 4 / k, Q5=100*△P5*(πd 2 / 4-πd5 2 / 4).

[0012] In one embodiment, the throttle valve also includes a second valve core assembly, the valve tube also defines a second valve cavity, and the second valve core assembly is installed in the second valve cavity; wherein the second valve core assembly includes a second valve seat and a second valve core, the second valve seat defines a second opening communicating with the second valve cavity, a second valve port communicating with the first valve cavity, and a second accommodating hole communicating with the second opening and the second valve port, and the second valve core is movably disposed in the second accommodating hole for opening / closing the second valve port.

[0013] In one embodiment, the throttle valve also includes a connecting piece, which is installed in the valve tube and divides the interior of the valve tube into the first valve cavity and the second valve cavity, the first valve seat and the second valve seat are respectively connected to the opposite ends of the connecting piece, and the first valve seat and the inner wall of the first valve cavity are spaced apart to form a first flow gap, and the second valve seat and the inner wall of the second valve cavity are spaced apart to form a second flow gap; wherein the connecting piece is provided with a first channel and a second channel, the first valve port is connected to the second flow gap through the first channel, and the second valve port is connected to the first flow gap through the second channel.

[0014] Compared with the prior art, the throttle valve provided by the present application, when the throttle valve is not working, the first valve core and the elastic member are in a balanced state, and the first valve core has no tendency to move toward the first valve port. At this time, by setting a certain gap between the first valve core and the first valve port, the first valve port has a certain opening. In this way, when the first valve core assembly starts to work, the refrigerant can flow directly from the gap without overcoming the elastic force of the elastic member to push the first valve core, that is, the refrigerant can still open the valve under low pressure difference conditions, which not only reduces the difficulty of opening the valve, but also meets the small flow demand under low pressure difference, and broadens the application scenario. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the conventional technology, the drawings required for use in the embodiments or the conventional technology descriptions are briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work.

[0016] Figure 1 A cross-sectional view of a throttle valve according to an embodiment of the present application;

[0017] Figure 2 for Figure 1 The enlarged view of point A in the middle;

[0018] Figure 3 A schematic structural diagram of a first valve core according to an embodiment of the present application;

[0019] Figure 4 for Figure 3 Enlarged view of point B in the middle.

[0020] The symbols in the figure mean the following:

[0021] 100, throttle valve; 10, valve tube; 11, first valve cavity; 111, first flow gap; 12, second valve cavity; 121, second flow gap; 20, connecting piece; 21, first channel; 22, second channel; 23, first assembly hole; 24, second assembly hole; 30, first valve core assembly; 301, first valve port; 302, first receiving hole; 303, first opening; 31, first valve seat; 311, valve seat body ; 312, head; 32, first valve core; 321, main body; 322, throttling part; 3221, first throttling section; 3222, second throttling section; 3223, third throttling section; 3224, fourth throttling section; 3225, fifth throttling section; 33, elastic member; 40, second valve core assembly; 401, second valve port; 402, second accommodating hole; 403, second opening; 41, second valve seat; 42, second valve core. DETAILED DESCRIPTION

[0022] In order to make the above-mentioned purposes, features and advantages of the present application more obvious and easy to understand, the specific implementation methods of the present application are described in detail below in conjunction with the accompanying drawings. In the following description, many specific details are set forth to facilitate a full understanding of the present application. However, the present application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar improvements without violating the connotation of the present application, so the present application is not limited by the specific embodiments disclosed below.

[0023] It should be noted that when a component is referred to as being "fixed to" or "disposed on" another component, it may be directly on the other component or there may also be a central component. When a component is considered to be "connected to" another component, it may be directly connected to the other component or there may be a central component at the same time. The terms "vertical", "horizontal", "upper", "lower", "left", "right" and similar expressions used in the specification of this application are for illustrative purposes only and do not represent the only implementation method.

[0024] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of the features. In the description of this application, the meaning of "plurality" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0025] In the present application, unless otherwise clearly specified and limited, a first feature being “above” or “below” a second feature may mean that the first feature is directly in contact with the second feature, or the first feature and the second feature are in contact indirectly through an intermediate medium. Moreover, a first feature being “above”, “above”, or “above” a second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. A first feature being “below”, “below”, or “below” a second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0026] Unless otherwise defined, all technical and scientific terms used in the specification of this application have the same meaning as those commonly understood by those skilled in the art to which this application belongs. The terms used in the specification of this application are only for the purpose of describing specific embodiments and are not intended to limit this application. The term "and / or" used in the specification of this application includes any and all combinations of one or more related listed items.

[0027] Throttle valves are often used in air-conditioning systems to adjust the flow of refrigerant. In related technologies, throttle valves usually include a valve seat, a valve core, and an elastic member. The valve seat is provided with a valve port. The valve core and the elastic member are both installed in the valve seat. The valve core moves in the valve seat under the elastic force of the elastic member and the pressure of the refrigerant to open and close the valve port. However, when the throttle valve is in a closed state, the valve core is often pressed against the valve port under the action of the elastic member, which results in a large pressure difference being required to overcome the elastic force of the elastic member when opening the valve, thereby increasing the difficulty of opening the valve.

[0028] See also Figure 1-Figure 4 In order to solve the problem that the existing throttle valve is difficult to open under low pressure difference conditions, the present application provides a throttle valve 100, which is used in an air-conditioning system to achieve throttling of the refrigerant. Specifically, the throttle valve 100 includes a valve tube 10, a first valve core assembly 30 and a second valve core assembly 40, the valve tube 10 has a first valve cavity 11 and a second valve cavity 12, the first valve core assembly 30 is installed in the first valve cavity 11, and the second valve core assembly 40 is installed in the second valve cavity 12. That is, the throttle valve 100 of the present application is a two-way valve, which can achieve two-way flow of refrigerant, wherein, when the refrigerant is flowing, one of the first valve core assembly 30 and the second valve core assembly 40 is in a working state, and the other is in a closed state. Of course, in other embodiments, the throttle valve 100 can also be used only in a system with one-way flow.

[0029] See also Figure 2The first valve core assembly 30 provided in the present application includes a first valve seat 31, a first valve core 32, and an elastic member 33. The first valve seat 31 is provided with a first opening 303 communicating with the first valve cavity 11, a first valve port 301 communicating with the second valve cavity 12, and a first receiving hole 302 communicating with the first opening 303 and the first valve port 301. The first valve core 32 and the elastic member 33 are arranged in the first receiving hole 302, and one end of the first valve core 32 is connected to the first valve seat 31 through the elastic member 33, and the other end is movably matched with the first valve port 301 to adjust the flow rate at the first valve port 301. Among them, when the first valve core 32 moves in the direction away from the first valve port 301, the elastic member 33 has a tendency to push the first valve core 32 to move toward the first valve port 301 to reset, and when the elastic member 33 pushes the first valve core 32 to move toward the first valve port 301 to the limit, there is a gap between the first valve core 32 and the first valve port 301 along the radial direction of the first valve core assembly 30.

[0030] It is understandable that when the throttle valve 100 is not working, the first valve core 32 and the elastic member 33 are in a balanced state, and the first valve core 32 has no tendency to move toward the first valve port 301. At this time, by setting a certain gap between the first valve core 32 and the first valve port 301, the first valve port 301 has a certain opening. In this way, when the first valve core assembly 30 starts to work, the refrigerant can flow directly from the gap without overcoming the elastic force of the elastic member 33 to push the first valve core 32, that is, the refrigerant can still open the valve under low pressure difference conditions, which not only reduces the difficulty of opening the valve, but also meets the small flow demand under low pressure difference, and broadens the application scenario.

[0031] Specifically, in the present embodiment, the first valve core assembly 30 controls the movement of the first valve core 32 by the cooperation of the flow pressure of the refrigerant and the elastic force of the elastic member 33, so as to realize the throttling control of the first valve core 32 on the first valve port 301. Generally, when the first valve core assembly 30 is in the working state, the pressure of the refrigerant is greater than the elastic force of the elastic member 33, and the refrigerant will push the first valve core 32 to move, thereby increasing the flow area at the first valve port 301, so that the refrigerant flows from the first valve port 301 through the first accommodating hole 302 and the first opening 303 in sequence into the first valve cavity 11. When the pressure of the refrigerant is less than the elastic force of the elastic member 33, under the restoring action of the elastic member 33, the first valve core 32 will move in the opposite direction toward the position of the first valve port 301, reduce the flow area at the first valve port 301, and even close the first valve port 301. When the first valve core 32 closes the first valve port 301 , there is still a gap between the first valve core 32 and the first valve port 301 , and the first valve core assembly 30 is in a fully closed but open state, that is, a small amount of refrigerant can still flow out from the first valve port 301 .

[0032] In one embodiment, the first valve seat 31 includes a valve seat body 311 and a head 312, the first opening 303, the first valve port 301 and the first accommodating hole 302 are all opened on the valve seat body 311, the head 312 is arranged on the valve seat body 311 at a position close to the first opening 303, and is limitedly connected to the valve seat body 311, and one end of the head 312 close to the first accommodating hole 302 is fixedly connected to the elastic member 33.

[0033] The sealing head 312 is provided to facilitate the connection between the first valve seat 31 and the elastic member 33, thereby reducing the connection difficulty of the elastic member 33. The sealing head 312 can form a gap or hole for the refrigerant to flow between the first opening 303 and the valve seat body 311 to avoid affecting the flow of the refrigerant.

[0034] In one embodiment, if Figure 2 and Figure 3 As shown, the first valve core 32 includes a main body 321 and a throttle portion 322, one end of the throttle portion 322 is connected to the main body 321 and connected to the elastic member 33 through the main body 321, and the other end is movably matched with the first valve port 301. The throttle portion 322 includes a plurality of throttle sections connected in sequence, and along the axial direction of the first valve core 32 and in the direction from the main body 321 to the throttle portion 322, the cross-sectional areas of the plurality of throttle sections tend to decrease in sequence.

[0035] In traditional technology, the flow area of ​​the throttle valve 100 is usually relatively fixed, and it is impossible to achieve a flow area that changes with the pressure difference, which makes the throttle valve 100 only able to meet the needs of ordinary air-conditioning models, but cannot meet the different working conditions of high-end variable frequency air conditioners. Based on this, high-end variable frequency air conditioners can often only use electronic expansion valves, which also leads to a significant increase in overall costs. However, the present application sets multiple throttling sections on the throttling part 322, and the cross-sectional areas of the multiple throttling sections are different, so that the channel flow formed by the cooperation of the multiple throttling sections and the first valve port 301 is different, thereby realizing flow regulation of different working conditions of the air-conditioning system. In addition, the adjustment structure of the first valve core 32 is simple, which can greatly reduce costs compared to traditional electronic expansion valves.

[0036] Specifically, in this embodiment, Figure 3 and Figure 4 As shown, there are five throttling sections, and from the main body 321 to the throttling section 322, the five throttling sections are respectively defined as the first throttling section 3221, the second throttling section 3222, the third throttling section 3223, the fourth throttling section 3224 and the fifth throttling section 3225. Among them, the first throttling section 3221, the third throttling section 3223, the fourth throttling section 3224 and the fifth throttling section 3225 are all extended in a columnar shape, along the axial direction of the first valve core 32, and from the main body 321 to the throttling section 322, the cross-sectional area of ​​the second throttling section 3222 gradually decreases.

[0037] The present application can achieve flow regulation for five different system working conditions by setting five throttling sections. In addition, since the movement of the throttling section depends on the combined action of the pressure difference and the elastic member 33, and the adjustment accuracy of the elastic member 33 itself is insufficient, the throttling section may fluctuate along the axial direction during operation. The present application sets the first throttling section 3221, the third throttling section 3223, the fourth throttling section 3224 and the fifth throttling section 3225 as a columnar structure. Even if the elastic member 33 fluctuates, the flow area between each throttling section set in a columnar shape and the first valve port 301 can still remain basically unchanged, thereby greatly improving the accuracy of the flow.

[0038] Among them, since the difference in outer diameters between the first throttling section 3221 and the third throttling section 3223 is small, setting the second throttling section 3222 to be columnar requires higher processing accuracy, and the second throttling section 3222 does not require high accuracy in flow regulation under its corresponding working conditions. Therefore, in this embodiment, the second throttling section 3222 is set to be conical. In this way, it can meet the use requirements and reduce the processing difficulty of the second throttling section 3222.

[0039] In addition, the present application specifically provides the size settings of the first throttling section 3221, the second throttling section 3222, the third throttling section 3223, the fourth throttling section 3224 and the fifth throttling section 3225. The size of each throttling section is designed based on the corresponding pressure difference working condition and the elastic performance of the elastic part 33, so that different throttling sections can achieve flow regulation under different working conditions of the air-conditioning system.

[0040] It should be noted that, with the plane where the opening of the first valve port 301 close to the first accommodating hole 302 is located as the reference plane, the flow calculation of each throttling section is based on the annular gap formed between the outer surface of each throttling section and the inner wall of the first valve port 301 on the reference plane.

[0041] Specifically, in one embodiment, the first throttling section 3221 is configured to operate in response to the system pressure difference △P1, and 0<△P1<0.3MPa. That is, the air-conditioning system is in a low pressure difference condition. Among them, the inner diameter d of the first valve port 301, the stiffness coefficient k of the elastic member 33, the outer diameter d1 of the first throttling section 3221, the vertical distance h1 from one end of the first throttling section 3221 away from the main body 321 to the main body 321, and the flow rate Q1 of the first valve port 301 when the first throttling section 3221 is working, satisfy, 0.942d<d1<0.95d, h1=△P1*πd 2 / 4 / k, Q1=100*△P1*(πd 2 / 4-πd1 2 / 4). In this way, the flow control of the first throttling section 3221 under the low pressure difference condition is achieved.

[0042] In one embodiment, the second throttling section 3222 is configured to work in response to the system pressure difference ΔP2, and 0.4MPa<ΔP2<1.4MPa. That is, the air conditioning system is in a medium pressure difference condition. When the second throttling section 3222 is in the working state, the diameter of the circle where the outer surface of the second throttling section 3222 at the corresponding position of the first valve port 301 is defined as d x , the vertical distance from any particle on the circle to the main body 321 is h x , and the inner diameter d of the first valve port 301, the stiffness coefficient k of the elastic member 33, the outer diameter d1 of the first throttling section 3221, the outer diameter d3 of the third throttling section 3223, the vertical distance h2 from the end of the second throttling section 3222 away from the main body 321 to the main body 321, and the flow rate Q2 of the first valve port 301 when the second throttling section 3222 is working, satisfy, 0.942d<d x <0.819d,h2=△P2*πd 2 / 4 / k,d x =[d3 2 -h x *(d1 2 -d3 2 ) / (h2-h1)] 1 / 2 , Q2=100*△P2*(πd 2 / 4-πd x 2 / 4). In this way, the flow control of the second throttling section 3222 under the medium pressure difference condition is achieved.

[0043] It should be noted that the circle where the outer surface of the second throttling section 3222 at a position corresponding to the first valve port 301 is located refers to a cross-sectional circle formed by cutting the outer surface of the second throttling section 3222 at the position of the above-mentioned reference plane.

[0044] In one embodiment, the third throttling section 3223 is configured to operate in response to the system pressure difference △P3, and 1.5MPa<△P3<1.8MPa. That is, the air conditioning system is in rated working condition. Among them, the inner diameter d of the first valve port 301, the stiffness coefficient k of the elastic member 33, the outer diameter d3 of the third throttling section 3223, the vertical distance h3 from the end of the third throttling section 3223 away from the main body 321 to the main body 321, and the flow rate Q3 of the first valve port 301 when the third throttling section 3223 is working, satisfy, 0.811d<d3<0.819d, h3=△P3*πd 2 / 4 / k, Q3=100*△P3*(πd 2 / 4-πd3 2 / 4). In this way, the flow control of the third throttling section 3223 under the rated working condition is achieved.

[0045] In one embodiment, the fourth throttling section 3224 is configured to operate in response to the system pressure difference △P4, and 2MPa<△P4<2.3MPa. That is, the air-conditioning system is in the first high temperature working condition. Among them, the inner diameter d of the first valve port 301, the stiffness coefficient k of the elastic member 33, the outer diameter d4 of the fourth throttling section 3224, the vertical distance h4 from the end of the fourth throttling section 3224 away from the main body 321 to the main body 321, and the flow rate Q4 of the first valve port 301 when the fourth throttling section 3224 is working, satisfy, 0.635d<d4<0.642d, h4=△P4*πd 2 / 4 / k, Q4=100*△P4*(πd 2 / 4-πd4 2 / 4). In this way, the flow control of the fourth throttling section 3224 under the first high temperature condition is achieved.

[0046] In one embodiment, the fifth throttling section 3225 is configured to operate in response to the system pressure difference △P5, and 2.4MPa<△P5<3.2MPa. That is, the air-conditioning system is in the second high temperature working condition. Among them, the inner diameter d of the first valve port 301, the stiffness coefficient k of the elastic member 33, the outer diameter d5 of the fifth throttling section 3225, the vertical distance h5 from the end of the fifth throttling section 3225 away from the main body 321 to the main body 321, and the flow rate Q5 of the first valve port 301 when the fifth throttling section 3225 is working, satisfy, 0.488d<d5<0.496d, h5=△P5*πd 2 / 4 / k, Q5=100*△P5*(πd 2 / 4-πd5 2 / 4). In this way, the flow control of the fifth throttling section 3225 under the second high temperature condition is achieved.

[0047] In summary, the first valve core assembly 30 provided in the present application has a throttling effect, and through the size design of each throttling section, while ensuring the rated working condition flow, it can also meet the requirements of small flow under low pressure difference and large flow under high temperature load, etc. In this way, the effect of the refrigerant flow changing with the pressure difference is achieved, which greatly improves the adjustability of the flow and also greatly improves the flow accuracy under various working conditions.

[0048] In one embodiment, if Figure 1 As shown, the second valve core assembly 40 includes a second valve seat 41 and a second valve core 42. The second valve seat 41 is provided with a second opening 403 connected to the second valve cavity 12, a second valve port 401 connected to the first valve cavity 11, and a second accommodating hole 402 connected to the second opening 403 and the second valve port 401. The second valve core 42 is movably disposed in the second accommodating hole 402 for opening / closing the second valve port 401.

[0049] It can be understood that in this embodiment, the second valve core assembly 40 is a full-circulation structure. Specifically, when the pressure of the refrigerant is greater than the gravity of the second valve core 42, the refrigerant will push the second valve core 42 to move, thereby opening the second valve port 401, so that the refrigerant flows from the second valve port 401 through the second accommodating hole 402 and the second opening 403 in sequence into the second valve cavity 12. Among them, the second valve core 42 can move to completely separate from the second valve port 401, thereby achieving full circulation of the refrigerant, thus meeting the large flow requirements of the air-conditioning system under specific working conditions (such as defrosting conditions, etc.), and effectively improving the working performance of the air-conditioning system. When the pressure of the refrigerant is less than the gravity of the second valve core 42, the second valve core 42 will move toward the position of the first valve port 301 and close the second valve port 401.

[0050] When the second valve port 401 is opened, the refrigerant pressure will be greater than the gravity of the second valve core 42, and the second valve core 42 will always move in the second accommodating hole 402 toward a position away from the second valve port 401, so there is a risk that the second valve core 42 will fall out of the second opening 403. In order to prevent the second valve core 42 from falling out of the second valve seat 41 from the second opening 403, a limiting pin or a conical limiting structure that is set in a contracted manner may be provided at the second opening 403 to limit the movement of the second valve core 42.

[0051] In one embodiment, if Figure 1 As shown, the throttle valve 100 also includes a connecting piece 20, which is installed in the valve tube 10 and divides the inside of the valve tube 10 into a first valve cavity 11 and a second valve cavity 12, and the first valve seat 31 and the second valve seat 41 are respectively connected to the opposite ends of the connecting piece 20, and the first valve seat 31 and the inner wall of the first valve cavity 11 are arranged to form a first flow gap 111, and the second valve seat 41 and the inner wall of the second valve cavity 12 are arranged to form a second flow gap 121. Among them, the connecting piece 20 is provided with a first channel 21 and a second channel 22, the first valve port 301 is connected to the second flow gap 121 through the first channel 21, and the second valve port 401 is connected to the first flow gap 111 through the second channel 22.

[0052] The connecting member 20 cooperates with the first valve core assembly 30 and the second valve core assembly 40 through its first channel 21 and the second channel 22, respectively, to achieve the effect of two-way flow of the throttle valve 100. In addition, the arrangement of the first channel 21 and the second channel 22 can reduce the flow resistance of the refrigerant, which is conducive to improving the stability of the throttle valve 100.

[0053] Further, in one embodiment, the two ends of the connecting piece 20 are respectively provided with a first assembly hole 23 and a second assembly hole 24, the first assembly hole 23 is in communication with the first channel 21, and a portion of the first valve seat 31 is inserted into the first assembly hole 23 and is welded and fixed to the connecting piece 20. The second assembly hole 24 is in communication with the second channel 22, and a portion of the second valve seat 41 is inserted into the second assembly hole 24 and is welded and fixed to the connecting piece 20. In this way, the connection strength between the first valve core assembly 30, the second valve core assembly 40 and the connecting piece 20 is greatly improved, and the stability of the overall structure of the throttle valve 100 is improved.

[0054] When assembling the throttle valve 100 provided in the present application, the first valve seat 31 can be first pressed into the first assembly hole 23 of the connecting piece 20, and the second valve seat 41 can be pressed into the second assembly hole 24 to achieve interference pre-fit. After that, fixation is achieved by welding. Further, the first valve core 32, the elastic member 33 and the head 312 are placed in the first receiving hole 302 in turn, and the valve seat body 311 is used to limit the head 312 to complete the assembly of the first valve core assembly 30. Similarly, the second valve core 42 is placed in the second receiving hole 402 through the second opening 403, and the second valve core 42 is limited to complete the assembly of the second valve core assembly 40. Finally, the overall structure composed of the first valve core assembly 30, the second valve core assembly 40 and the connecting piece 20 is placed in the valve pipe 10, and the overall fixation is achieved by relying on the necking of the valve pipe 10 and the groove on the surface of the connecting piece 20.

[0055] Furthermore, the throttle valve 100 provided in the present application is a two-way flow and one-way throttling structure. Specifically, when the first valve core assembly 30 is working, the throttle valve 100 is in a throttling state, and the refrigerant first enters the second valve cavity 12 of the valve tube 10. Since the second valve core 42 is affected by the refrigerant flow pressure and its own gravity, it will block the second valve port 401, and the refrigerant cannot flow through the second valve port 401. Therefore, the refrigerant will flow through the second flow gap 121 to the second channel 22 on the connecting member 20, and exert a driving force on the first valve core 32, so that the first valve core 32 moves and gradually increases the flow area of ​​the first valve port 301, and then flows into the first valve cavity 11 through the first accommodating hole 302 and the first opening 303 in sequence. During this period, the movement of the first valve core 32 is controlled by the pressure difference and the elastic force of the elastic member 33, thereby realizing variable flow regulation of the refrigerant.

[0056] When the second valve core assembly 40 is working, the throttle valve 100 is in a full flow state, and the refrigerant first enters the first valve cavity 11 of the valve tube 10. At this time, the first valve core 32 is affected by the refrigerant flow pressure and will block the first valve port 301, or only a small amount of refrigerant can flow through the gap at the first valve port 301, while most of the refrigerant will flow to the first channel 21 on the connecting member 20 through the first flow gap 111, and push the second valve core 42, so that the second valve core 42 moves and opens the second valve port 401, and then flows into the second valve cavity 12 through the second accommodating hole 402 and the second opening 403 in sequence. During this period, the second valve core 42 basically does not restrict the flow at the second valve port 401, thereby achieving full circulation of the refrigerant.

[0057] 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.

[0058] The above-described embodiments only express several implementation methods of the present application, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the patent application. It should be pointed out that, for a person of ordinary skill in the art, several variations and improvements can be made without departing from the concept of the present application, and these all belong to the protection scope of the present application. Therefore, the scope of patent protection of the present application shall be subject to the attached claims.

Claims

1. A throttle valve, comprising a valve tube (10) and a first valve core assembly (30), wherein the valve tube (10) has a first valve cavity (11), and the first valve core assembly (30) is installed in the first valve cavity (11); It is characterized in that The first valve core assembly (30) comprises a first valve seat (31), a first valve core (32) and an elastic member (33); the first valve seat (31) is provided with a first opening (303), a first valve port (301) and a first receiving hole (302) communicating with the first opening (303) and the first valve port (301); the first opening (303) is communicated with the first valve cavity (11); the first valve core (32) and the elastic member (33) are arranged in the first receiving hole (302), and one end of the first valve core (32) is connected to the first valve seat (31) through the elastic member (33), and the other end is movably matched with the first valve port (301) to adjust the flow rate at the first valve port (301); When the first valve core (32) moves in a direction away from the first valve port (301), the elastic member (33) has a tendency to push the first valve core (32) to move closer to the first valve port (301) to reset, and when the elastic member (33) pushes the first valve core (32) to move closer to the first valve port (301) to a limit, a gap is provided between the first valve core (32) and the first valve port (301) along the radial direction of the first valve core assembly (30).

2. The throttle valve according to claim 1, characterized in that: The first valve core (32) comprises a main body (321) and a throttle portion (322), one end of the throttle portion (322) is connected to the main body (321) and connected to the elastic member (33) via the main body (321), and the other end is movably matched with the first valve port (301); The throttling portion (322) includes a plurality of throttling sections connected in sequence, and along the axial direction of the first valve core (32) and in the direction from the main body (321) to the throttling portion (322), the cross-sectional areas of the plurality of throttling sections tend to decrease in sequence.

3. The throttle valve according to claim 2, characterized in that: The number of the throttling sections is five, and in the direction from the main body (321) to the throttling section (322), the five throttling sections are respectively defined as a first throttling section (3221), a second throttling section (3222), a third throttling section (3223), a fourth throttling section (3224) and a fifth throttling section (3225); Among them, the first throttling section (3221), the third throttling section (3223), the fourth throttling section (3224) and the fifth throttling section (3225) all extend in a columnar shape, and along the axial direction of the first valve core (32), and in the direction from the main body (321) to the throttling section (322), the cross-sectional area of ​​the second throttling section (322) gradually decreases.

4. The throttle valve according to claim 3, characterized in that: The first throttling section (3221) is configured to operate in response to a system pressure difference ΔP1, and 0<ΔP1<0.3MPa; Wherein, the inner diameter d of the first valve port (301), the stiffness coefficient k of the elastic member (33), the outer diameter d1 of the first throttling section (3221), the vertical distance h1 from one end of the first throttling section (3221) away from the main body (321) to the main body (321), and the flow rate Q1 of the first valve port (301) when the first throttling section (3221) is in operation, satisfy the following conditions: 0.942d<d1<0.95d, h1=△P1*πd 2 / 4 / k, Q1=100*△P1*(πd 2 / 4-πd1 2 / 4).

5. The throttle valve according to claim 4, characterized in that: The second throttling section (3222) is configured to operate in response to a system pressure difference ΔP2, and 0.4MPa<ΔP2<1.4MPa; When the second throttling section (3222) is in a working state, the diameter of the circle on which the outer surface of the second throttling section (3222) at a position corresponding to the first valve port (301) is defined as d x , the vertical distance from any particle on the circle to the main body (321) is h x , and the outer diameter d3 of the third throttling section (3223), the vertical distance h2 from one end of the second throttling section (3222) away from the main body (321) to the main body (321), and the flow rate Q2 of the first valve port (301) when the second throttling section (3222) is in operation, satisfy, 0.942d<d x <0.819d,h2=△P2*πd 2 / 4 / k,d x =[d3 2 -h x *(d1 2 -d3 2 ) / (h2-h1)] 1 / 2 , Q2=100*△P2*(πd 2 / 4-πd x 2 / 4).

6. The throttle valve according to claim 3, characterized in that: The third throttling section (3223) is configured to operate in response to a system pressure difference ΔP3, and 1.5MPa<ΔP3<1.8MPa; Wherein, the inner diameter d of the first valve port (301), the stiffness coefficient k of the elastic member (33), the outer diameter d3 of the third throttling section (3223), the vertical distance h3 from one end of the third throttling section (3223) away from the main body (321) to the main body (321), and the flow rate Q3 of the first valve port (301) when the third throttling section (3223) is in operation, satisfy, 0.811d<d3<0.819d, h3=△P3*πd 2 / 4 / k, Q3=100*△P3*(πd 2 / 4-πd3 2 / 4).

7. The throttle valve according to claim 3, characterized in that: The fourth throttling section (3224) is configured to operate in response to a system pressure difference ΔP4, and 2MPa<ΔP4<2.3MPa; Wherein, the inner diameter d of the first valve port (301), the stiffness coefficient k of the elastic member (33), the outer diameter d4 of the fourth throttling section (3224), the vertical distance h4 from one end of the fourth throttling section (3224) away from the main body (321) to the main body (321), and the flow rate Q4 of the first valve port (301) when the fourth throttling section (3224) is in operation, satisfy, 0.635d<d4<0.642d, h4=△P4*πd 2 / 4 / k, Q4=100*△P4*(πd 2 / 4-πd4 2 / 4).

8. The throttle valve according to claim 3, characterized in that: The fifth throttling section (3225) is configured to operate in response to a system pressure difference ΔP5, and 2.4MPa<ΔP5<3.2MPa; Wherein, the inner diameter d of the first valve port (301), the stiffness coefficient k of the elastic member (33), the outer diameter d5 of the fifth throttling section (3225), the vertical distance h5 from one end of the fifth throttling section (3225) away from the main body (321) to the main body (321), and the flow rate Q5 of the first valve port (301) when the fifth throttling section (3225) is in operation, satisfy, 0.488d<d5<0.496d, h5=△P5*πd 2 / 4 / k, Q5=100*△P5*(πd 2 / 4-πd5 2 / 4).

9. The throttle valve according to claim 1, characterized in that The throttle valve further comprises a second valve core assembly (40), the valve tube (10) further comprises a second valve cavity (12), and the second valve core assembly (40) is installed in the second valve cavity (12); Wherein, the second valve core assembly (40) includes a second valve seat (41) and a second valve core (42); the second valve seat (41) is provided with a second opening (403) communicating with the second valve cavity (12), a second valve port (401) communicating with the first valve cavity (11), and a second accommodating hole (402) communicating with the second opening (403) and the second valve port (401); the second valve core (42) is movably disposed in the second accommodating hole (402) for opening / closing the second valve port (401).

10. The throttle valve according to claim 9, characterized in that The throttle valve further comprises a connecting piece (20), wherein the connecting piece (20) is installed in the valve tube (10) and divides the interior of the valve tube (10) into the first valve chamber (11) and the second valve chamber (12); the first valve seat (31) and the second valve seat (41) are respectively connected to opposite ends of the connecting piece (20); the first valve seat (31) and the inner wall of the first valve chamber (11) are spaced apart to form a first flow gap (111); the second valve seat (41) and the inner wall of the second valve chamber (12) are spaced apart to form a second flow gap (121); The connecting member (20) is provided with a first channel (21) and a second channel (22); the first valve port (301) is connected to the second flow gap (121) via the first channel (21); and the second valve port (401) is connected to the first flow gap (111) via the second channel (22).

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