An electrically operated valve

Abstract

This application provides an electric valve. The valve seat assembly of the electric valve includes a valve port portion. A valve core assembly is axially movable and cooperates with the valve port portion. The valve core assembly has a balance channel that can balance the axial pressure of the valve core assembly. The valve core assembly includes a valve core portion, which includes a first conical surface and a second conical surface. The second conical surface is located below the first conical surface. The valve port portion has a first fillet. The first conical surface abuts against the first fillet. The angle of the first conical surface is θ1, and the angle of the second conical surface is θ2, satisfying θ1 < θ2, where 15° ≤ θ1 ≤ 45°. When the customer requires at least two flow curves, this application can meet the customer's needs, and the flow curves can be richer. At the same time, the angle setting of θ1 can not only improve the sealing performance when the first conical surface abuts against the first fillet, but also guide the process of the first conical surface abutting against the first fillet. This can improve the coaxiality of the valve core portion and the valve port portion, reduce the wear of the valve port portion, and improve the service life of the electric valve.

Description

Technical Field

[0001] This application relates to the field of thermal management technology, specifically to an electric valve for an automotive thermal management system. Background Technology

[0002] In related technologies, electric valves include a valve seat assembly and a valve core assembly. The valve seat assembly has a valve port, and the valve core assembly can cooperate with the valve port to control the flow rate at the valve port. The valve core assembly has a balancing channel that can balance the axial pressure of the valve core assembly. The sealing surface of the valve core assembly is a single segment, and the outer diameter of the sealing surface decreases from top to bottom. With this design, the flow curve is relatively simple. In addition, in related technologies, the angle of the sealing surface of the valve core assembly is set relatively large, which can easily lead to a decrease in the coaxiality between the valve core assembly and the valve port. Wear may occur at the valve port, resulting in a decrease in sealing performance. Utility Model Content

[0003] The purpose of this application is to provide an electric valve that can meet the customer's flow curve requirements while ensuring the reliability of the electric valve's sealing.

[0004] To achieve the above objectives, this application provides the following technical solution:

[0005] An electric valve includes a valve seat assembly and a valve core assembly. The valve seat assembly includes a valve port. The valve core assembly is axially movable along the electric valve and engages with the valve port. The valve core assembly has a balancing channel that can balance the axial pressure of the valve core assembly. The valve core assembly includes a valve core portion, which includes a first conical surface and a second conical surface. The second conical surface is located below the first conical surface. The valve port portion has a first fillet. The first conical surface abuts against the first fillet. The angle of the first conical surface is θ1, and the angle of the second conical surface is θ2, satisfying θ1 < θ2, where 15° ≤ θ1 ≤ 45°.

[0006] In one technical solution provided in this application, the electric valve includes a valve seat assembly and a valve core assembly. The valve seat assembly includes a valve port. The valve core assembly can move along the axial direction of the electric valve and cooperate with the valve port. The valve core assembly has a balance channel that can balance the axial pressure of the valve core assembly. The valve core assembly includes a valve core portion, which includes a first conical surface and a second conical surface. The second conical surface is located below the first conical surface. The valve port has a first fillet. The first conical surface abuts against the first fillet. The angle of the first conical surface is θ1, and the angle of the second conical surface is θ2, satisfying θ1 < θ2, where 15° ≤ θ1 ≤ 45°. When the customer requires at least two flow curves, this solution can meet the customer's needs, and the flow curves can be richer. At the same time, the angle setting of θ1 can not only improve the sealing performance when the first conical surface abuts against the first fillet, but also guide the process of the first conical surface abutting against the first fillet. This can improve the coaxiality of the valve core portion and the valve port portion, reduce the wear of the valve port portion, and improve the service life of the electric valve. Attached Figure Description

[0007] Figure 1 This is a front view structural schematic diagram of the valve component provided in this application;

[0008] Figure 2 yes Figure 1 The diagram shows a cross-sectional view of the valve component along plane AA.

[0009] Figure 3 yes Figure 2 A partially enlarged structural diagram of the valve component at point A;

[0010] Figure 4 yes Figure 2 The diagram shows a partially enlarged view of the valve component at point B.

[0011] Figure 5 yes Figure 2 A cross-sectional view of the valve core of the valve component shown.

[0012] Figure 6 yes Figure 2 A cross-sectional view of the second valve seat portion of the valve component shown.

[0013] Figure 7 yes Figure 2 The diagram shows the flow curve of the valve component. Detailed Implementation

[0014] To make the objectives, technical solutions, and advantages of this utility model clearer, the embodiments of the utility model will be further described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are merely illustrative of the utility model and are not intended to limit the utility model.

[0015] Electric valves are widely used in automotive thermal management systems, such as vehicle air conditioning systems and vehicle battery cooling systems. In these systems, electric valves are generally used as throttling or switching elements. This application uses an electric valve as an example of an electronic expansion valve with throttling function. The electric valve includes a valve component 1, a coil assembly (not shown in the figure), and a valve body (not shown in the figure). The coil assembly is located on the outer periphery of the valve component 1, and the two are sealed together to prevent moisture or other impurities from the external environment from entering the gap between the coil assembly and the valve component 1, thereby preventing corrosion or failure of the component. At least a portion of the valve component 1 is located in the inner cavity formed by the valve body. The valve component 1 is fixedly connected or limited to the valve body. The coil assembly is connected to the valve body by screws. Of course, in other embodiments, the coil assembly and the valve body can be connected by snap-fit ​​or other means.

[0016] refer to Figures 1-6 In one embodiment of the valve component 1 provided in this application, the valve component 1 includes a rotor assembly 11, a valve seat assembly 12, a valve core assembly 13, a nut assembly 14, a rod component 15, and a sleeve 16. The valve seat assembly 12 has a valve seat cavity 12a, and part of the rod component 15 and the valve core assembly 13 are located in the valve seat cavity 12a. The valve seat assembly 12 is fixedly connected to the sleeve 16, and the fixing method includes welding, etc. The sleeve 16 is sleeved on the outer periphery of the rotor assembly 11. The rotor assembly 11 is fixedly connected to or limited to one end of the rod component 15, and the fixing method includes welding, snap-fit, etc. The nut assembly 14 includes a main body 141 and a connecting plate 142. The main body 141 is formed by injection molding with the connecting plate 142 as an insert. The connecting plate 142 is fixedly connected to the valve seat assembly 12, and the connection method includes welding, snap-fit, etc. The rod component 15 is threadedly engaged with the main body 141. The valve seat assembly 12 has a valve port 121, and the coil assembly includes a stator assembly (not shown). When the rotor assembly 11 rotates circumferentially under the magnetic field excitation of the stator assembly, the rotor assembly 11 drives the rod component 15 to rotate. The rod component 15 can drive the valve core assembly 13 to perform linear reciprocating motion along the axial direction of the electric valve. In this way, the valve core assembly 13 can adjust the opening of the valve port 121 by moving closer to or further away from the valve port 121, thereby adjusting the flow rate of the refrigerant through the valve port 121. The valve seat assembly 12 includes a first channel 124 and a second channel 125, which can be connected through the valve port 121. In this embodiment, the first channel 124 can function as an inlet channel, and the second channel 125 can function as an outlet channel. Of course, the flow directions of the two can be opposite. In some other embodiments, other transmission mechanisms such as planetary gears can be used to drive the rotor assembly 11 to drive the valve core assembly 13.

[0017] The valve core assembly 13 has a balance channel 133. In this embodiment, the balance channel 133 extends through the valve core assembly 13 axially, so as to connect the valve seat cavity 12a with the second channel 125. The balance channel 133 can balance the axial pressure of the valve core assembly 13, which can reduce the valve opening resistance and ensure the valve opening reliability of the electric valve. The valve core assembly 13 includes a valve core portion 131, which includes a first conical surface 1311 and a second conical surface 1312. The second conical surface 1312 is located below the first conical surface 1311. In this embodiment, the second conical surface 1312 extends along the end of the first conical surface 1311. Of course, in other embodiments, a vertical section can be provided between the first conical surface 1311 and the second conical surface 1312. This allows the fluid to flow from the first channel 124 to the second channel 125 during the valve opening process. First, the flow rate is adjusted by the first conical surface 1311, and then by the second conical surface 1312. This can meet the requirements of two flow curves. When the customer requires at least two flow curves, the flow curves are more abundant and can meet the customer's needs. In this embodiment, the valve port 121 has a first rounded corner 1211a, and the first conical surface 1311 can abut against the first rounded corner 1211a. That is, a line seal is used to seal the valve core assembly 13 and the valve port 121. The angle of the first conical surface 1311 is defined as θ1, and the angle of the second conical surface 1312 is defined as θ2, satisfying θ1 < θ2. This improves the sealing performance when the first conical surface 1311 abuts against the first rounded corner 1211a, and also guides the abutment of the first conical surface 1311 against the first rounded corner 1211a, which is beneficial to the coaxiality of the valve core 131 and the valve port 121. This reduces wear on the valve port 121 and increases the lifespan of the electric valve. (Reference) Figure 7The flow curve shown can be sloped by adjusting θ1 and θ2. The slope represents the rate of flow change. At a small opening (segment A1), corresponding to the flow regulation of the first conical surface 1311, the angle θ1 is smaller, ensuring higher flow regulation accuracy; that is, a smaller slope is required. At a large opening (segment A2), corresponding to the flow regulation of the second conical surface 1312, θ2 > θ1, allowing for lower flow regulation accuracy; the required slope is relatively larger than that of segment A1. Satisfying 15° ≤ θ1 ≤ 45° improves the sealing performance when the first conical surface 1311 abuts against the first fillet 1211a, ensuring proper guidance between the valve core 131 and the valve port 121. This improves the coaxiality of the valve core 131 and the valve port 121, reducing wear on the valve port 121 and extending the lifespan of the electric valve. In other embodiments, the included angle θ1 can satisfy 20°≤θ1≤40°; 25°≤θ1≤45°. This further guides the axial movement of the valve core 131, further improving the sealing performance when the first conical surface 1311 abuts against the first fillet 1211a, and reducing internal leakage of the electric valve. Specifically, in this embodiment, θ1=35°. The radius of the first fillet 1211a is R, and the range of R is 0.06mm≤R≤1.2mm. This facilitates the guidance when the valve core 131 and the valve port 121 mate, improves the coaxiality of the valve core 131 and the valve port 121, reduces wear on the valve port 121, improves the sealing performance when the valve core 131 and the valve port 121 abut against each other, and reduces internal leakage of the electric valve. In other embodiments, the radius R can satisfy 0.08mm≤R≤0.8mm; 0.1mm≤R≤0.3mm, which can further improve the sealing performance of the valve core 131 and the valve port 121, and reduce the internal leakage of the electric valve. Specifically, in this embodiment, R=0.1mm. The limitation of the angle of the first conical surface 1311 being 15°≤θ1≤45° and the limitation of the radius of the first rounded corner 1211a being 0.06mm≤R≤1.2mm can ensure that when the first conical surface 1311 and the first rounded corner 1211a are in contact, the first conical surface 1311 guides the contact, further improving the sealing reliability of both and reducing the internal leakage of the electric valve.

[0018] Specifically, both the first conical surface 1311 and the second conical surface 1312 face the valve port 121. The diameter of the first conical surface 1311 decreases towards the valve port 121, and the diameter of the second conical surface 1312 also decreases towards the valve port 121. Furthermore, the valve core 131 includes rounded corners or chamfers. The ends of the second conical surface 1312 and the valve core 131 transition through the aforementioned rounded corners or chamfers. In this embodiment, rounded corners are specifically used. This allows the valve core 131 to be guided to the valve port 121 as the valve core assembly 13 approaches the valve port 121, reducing collisions between the end of the valve core assembly 13 and the valve port 121, and improving the coaxiality of the valve core assembly 13 and the valve port 121. At the same time, the aforementioned rounded corners or chamfers can slightly adjust the flow rate, thereby improving the flow curve to meet customer needs. In other embodiments, the valve core 131 may further include a third conical surface located below the second conical surface 1312. The third conical surface extends along the end of the second conical surface 1312 and faces the valve port 121. The diameter of the third conical surface decreases towards the valve port 121. The angle of the third conical surface is defined as θ3, satisfying θ2 < θ3. This allows for further adjustment of the flow rate of fluid flowing from the first channel 124 to the second channel 125 via the third conical surface, achieving a three-stage flow curve adjustment function to meet customer needs. Furthermore, the aforementioned rounded corners or chamfers ensure a smooth transition between the third conical surface and the end of the valve core 131, further improving the flow curve. Of course, in other embodiments, a fourth conical surface, a fifth conical surface, etc., can be added, thereby achieving a four-stage flow curve adjustment function, a five-stage flow curve adjustment function, etc., respectively.

[0019] In this embodiment, the valve core 131 and the valve port 121 are both made of metal. Specifically, the valve core 131 is made of one type of stainless steel, and the valve port 121 is made of another type of stainless steel. The Vickers hardness of the metal forming the valve core 131 is HV1, and the Vickers hardness of the metal forming the valve port 121 is HV2, satisfying HV1 > HV2. The hardness of the stainless steel can be changed through heat treatment, specifically including annealing, solution treatment, and precipitation hardening. Specifically, 20HV ≤ (HV1 - HV2) ≤ 80HV, which improves the sealing performance between the valve core 131 and the valve port 121, reduces wear on the valve port 121, improves the reliability of the seal between the valve core 131 and the valve port 121, and reduces the occurrence of internal leakage. In other embodiments, 30HV≤(HV1-HV2)≤60HV; 40HV≤(HV1-HV2)≤80HV, which can further reduce the wear of the valve core 131 and the valve port 121, and ensure the reliability of the seal between the valve core 131 and the valve port 121. Referring to the table below, the difference between the hardness HV1 of the valve core 131 and the hardness HV2 of the valve port 121 is 2HV, resulting in a one-time internal leakage failure rate of 100%. 27.2%; In this embodiment, HV1-HV2 = 40HV, referring to Table 2 below, specifically, HV1 = 302HV, HV2 = 262HV. The experimentally measured one-time internal leakage failure rate is 0%, indicating that the valve core 131 and valve port 121 are reliably sealed; Referring to Table 3 below, the difference between the hardness HV1 of the valve core 131 and the hardness HV2 of the valve port 121 is 81HV, and the one-time internal leakage failure rate is 5.8%. In other embodiments, the valve port 121 can be made of non-metallic materials, such as plastic or rubber materials, which can also ensure the sealing performance of the valve core 131 and valve port 121.

[0020]

[0021] refer to Figures 2-6The valve port 121 includes a straight section 1211. A first rounded corner 1211a is located on the upper side of the straight section 1211. The straight section 1211 extends along the end of the first rounded corner 1211a to form the inner peripheral wall of the second channel 125. The inner diameter of the straight section 1211 is defined as D1, the maximum outer diameter of the first conical surface 1311 is D2, the minimum outer diameter of the first conical surface 1311 is D3, and the diameter of the contact position between the first conical surface 1311 and the first rounded corner 1211a is D4. The following conditions are met: (4D3 / 5+D2 / 5)≤D4≤(D3 / 5+4D2 / 5), D4>D1. This ensures that the contact position between the valve port 121 and the valve core 131 is as close as possible to the middle position of the first conical surface 1311, and further ensures the reliability of the electric valve operation. In other embodiments, the diameter D4 can satisfy (2D3 / 3+D2 / 3)≤D4≤(D3 / 3+2D2 / 3); (4D3 / 5+D2 / 5)≤D4≤(D3 / 4+3D2 / 4). This can further make the contact position between the valve port 121 and the valve core 131 as close as possible to the middle position of the first conical surface 1311, further reducing the influence of the machining error of the valve port 121 and the valve core 131 on the contact stop position, and reducing the phenomenon of the first conical surface 1311 and the first fillet 1211a failing to contact.

[0022] The valve core assembly 13 includes a first cavity 131a. In this embodiment, the first cavity 131a is located in the valve core portion 131 and is arranged along the central axis of the valve core assembly 13. In other embodiments, the first cavity 131a may be arranged off-center from the central axis of the valve core assembly 13. The inner diameter of the first cavity 131a is D6. The valve core portion 131 includes a straight section 1313, and the outer diameter of the straight section 1313 is defined as D5. In this embodiment, D5 = D2, where 8mm ≤ D5 ≤ 18mm, and satisfies 0.125D5 ≤ D6 ≤ 0.47D5. This arrangement can prevent the working medium fluid entering from the first channel 124 from flowing directly and unobstructed into the first cavity 131a after passing through the valve port portion 121. At the same time, it can reduce the refrigerant flow into the first cavity 131a, thereby reducing the noise generated by the refrigerant flowing directly into the first cavity 131a after throttling and expansion, and can also relatively reduce the weight of the valve core assembly 13. For example, the diameter of D5 can be 16mm, and the diameter of D6 can be 2mm, 6mm, or 7.5mm. This configuration allows the working medium to expand rapidly after being throttled through the valve port 121, reducing the flow rate of the working medium directly flowing into the first chamber 131a from the first channel 124. This may lead to eddies in the first chamber 131a, forming a resonance chamber and causing abnormal noise. Furthermore, the relationship between D6 and D5 can be 0.125D5≤D6≤0.40D5; 0.175D5≤D6≤0.35D5; 0.155D5≤D6≤0.375D5. This further reduces the diameter of the first chamber 131a, thereby reducing the flow rate of refrigerant diverted to the first chamber 131a, improving fluid noise, and relatively reducing the weight of the valve core 131. In other embodiments, D5 > D2 must be satisfied to meet the dimensional definition of the inner diameter D6 of the first chamber under different operating conditions.

[0023] refer to Figures 2-6In this embodiment, the valve core 131 further includes a second cavity 131b, which is located below the first cavity 131a and at the end of the valve core 131. The inner diameter of the second cavity 131b is larger than that of the first cavity 131a. The diameter of the inner peripheral wall of the second cavity 131b increases near the valve port 121. This facilitates the positioning of the valve core 131 and the guidance of other tooling when it mates with the valve core 131. It also further reduces the weight of the valve core assembly 13. Simultaneously, the refrigerant flowing into the first channel passes through the inner peripheral wall and top wall of the second cavity 131b. The stepped structure allows the refrigerant to be diverted, resulting in a more uniform fluid distribution, a smoother and more even flow rate, reduced fluid pressure fluctuations, and further reduced noise. In other embodiments, the second cavity 131b may not be provided. The valve core 131 also has a balance hole 131c, which axially penetrates the valve core 131 and communicates with the first cavity 131a, thereby connecting the valve seat cavity 12a with the second channel 125. Specifically, in this embodiment, there are three balance holes 131c. The centers of the three balance holes 131c are connected sequentially to form an equilateral triangle, which ensures that the balance holes 131c can reduce the weight of the valve core 131 to the greatest extent. At the same time, the arrangement of the balance holes 131c can further divert the flowing working medium, improve the fluid flow direction, reduce fluid pressure fluctuations, and also help to improve fluid noise. The circumferentially spaced balance holes 131c can meet the usage requirements of the electric valve under multiple operating conditions. In other embodiments, the balance holes 131c can be of other numbers or located in other positions. Furthermore, the connecting plate 142 of the nut assembly 14 includes a first balance hole 142a. The first balance hole 142a can ensure that the inner cavity 12a of the valve seat is connected to the inner cavity formed by the rotor assembly 11. In this embodiment, the first balance hole 142a, the inner cavity 12a of the valve seat, the balance hole 131c and the second cavity 131b form a balance channel 133, which can ensure the pressure balance between the second channel 125 and the cavity formed by the rotor assembly 11, which is beneficial to reduce the valve opening resistance and thus reduce the driving force for the operation of the valve component 1.

[0024] In this embodiment, the rod component 15 is fixedly connected to the valve core 131, which may include welding, riveting, etc. Specifically, the valve core 131 also includes an upper valve core cavity 131d and a flow hole 131e. The upper valve core cavity 131d is connected to the balance channel 133, and part of the rod component 15 is located in the upper valve core cavity 131d. The flow hole 131e connects the upper valve core cavity 131d with the first cavity 131a. The valve core assembly 13 includes an elastic element 132, which is located in the upper valve core cavity 131d. The upper end of the elastic element 132 abuts against part of the rod component 15, and the lower end of the elastic element 132 abuts against the lower end face forming the upper valve core cavity 131d. The rod component 15 can drive the valve core 131 to move axially through the elastic element 132. The flow hole 131e can achieve pressure balance between the upper valve core cavity 131d and the first cavity 131a, ensuring the axial movement of the valve core 131. In this embodiment, the elastic element 132 provided in the upper cavity 131d of the valve core is specifically a buffer spring. In other embodiments, the upper cavity 131d of the valve core can be provided with a small valve core, and the flow hole 131e functions as a small valve port.

[0025] The valve seat assembly 12 includes a first valve seat portion 122 and a second valve seat portion 123. A valve port portion 121, a first channel 124, and a second channel 125 are located in the second valve seat portion 123. The valve component 1 also includes a sealing assembly 17. The sealing assembly 17 is fixed by snapping together with the second valve seat portion 123 through the first valve seat portion 122. The sealing assembly 17 is located in the inner cavity formed by the first valve seat portion 122. The sealing assembly 17 is located between the straight section 1313 and part of the inner peripheral wall of the first valve seat portion 122. Part of the inner peripheral wall of the first valve seat portion 122 is in clearance fit with the valve core portion 131. The sealing assembly 17 includes a first sealing ring 171 and a first annular member 172. The first sealing ring 171 is made of rubber material, such as a sealing ring. The first sealing ring 171 is pressed between the inner peripheral wall of a portion of the valve seat assembly 17 and the first annular member 172. The first annular member 172 is made of resin material, such as PTFE (polytetrafluoroethylene). The first annular member 172 is clearance-fitted with the first sidewall 1311 of the valve core portion 131 to achieve dynamic sealing.

[0026] The above-described embodiments are merely examples of several implementations of this application, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the utility model patent. It should be noted that those skilled in the art can make various modifications without departing from the concept of this utility model, and these modifications all fall within the protection scope of this utility model.

Claims

1. An electric valve, characterized in that, The electric valve includes a valve seat assembly (12) and a valve core assembly (13). The valve seat assembly (12) includes a valve port (121). The valve core assembly (13) is axially movable along the electric valve and engages with the valve port (121). The valve core assembly (13) has a balance channel (133) that can balance the axial pressure of the valve core assembly (13). The valve core assembly (13) includes a valve core portion (131), which contains... The valve includes a first conical surface (1311) and a second conical surface (1312), the second conical surface (1312) being located below the first conical surface (1311), the valve port (121) having a first rounded corner (1211a), the first conical surface (1311) being able to abut against the first rounded corner (1211a), the angle of the first conical surface (1311) being θ1, the angle of the second conical surface (1312) being θ2, satisfying θ1 < θ2, where 15° ≤ θ1 ≤ 45°.

2. The electric valve according to claim 1, characterized in that, The first conical surface (1311) and the second conical surface (1312) face the valve port (121). The diameter of the first conical surface (1311) decreases towards the valve port (121), and the diameter of the second conical surface (1312) decreases towards the valve port (121). The valve core (131) includes a rounded corner or a chamfer. The end of the second conical surface (1312) and the valve core (131) transition through the rounded corner or the chamfer. Alternatively, the valve core (131) includes a third conical surface located below the second conical surface (1312). The third conical surface faces the valve port (121), and the diameter of the third conical surface decreases towards the valve port (121). The angle of the third conical surface is θ3, satisfying θ2 < θ3. The end of the third conical surface and the valve core (131) transition through the rounded corner or the chamfer.

3. The electric valve according to claim 1 or 2, characterized in that, The radius of the first fillet (1211a) is R, where 0.06mm≤R≤1.2mm.

4. The electric valve according to claim 3, characterized in that, The valve port (121) further includes a straight section (1211), the first rounded corner (1211a) is located on the upper side of the straight section (1211), the inner diameter of the straight section (1211) is D1, the maximum outer diameter of the first conical surface (1311) is D2, the minimum outer diameter of the first conical surface (1311) is D3, and the diameter of the contact position between the first conical surface (1311) and the first rounded corner (1211a) is D4, satisfying (4D3 / 5+D2 / 5)≤D4≤(D3 / 5+4D2 / 5), D4>D1.

5. The electric valve according to claim 4, characterized in that, (2D3 / 3+D2 / 3)≤D4≤(D3 / 3+2D2 / 3); (4D3 / 5+D2 / 5)≤D4≤(D3 / 4+3D2 / 4).

6. The electric valve according to any one of claims 1-5, characterized in that, The valve core (131) is made of a metal material, and the valve port (121) is made of a non-metal material; or, the valve core (131) is made of a metal material, and the valve port (121) is made of a metal material, wherein the hardness of the metal material forming the valve core (131) is HV1, and the hardness of the metal material forming the valve port (121) is HV2, satisfying HV1 > HV2.

7. The electric valve according to claim 6, characterized in that, 20HV≤(HV1-HV2)≤80HV.

8. The electric valve according to any one of claims 4-7, characterized in that, The valve core (131) includes a straight section (1313) with an outer diameter of D5. The valve core assembly (13) has a first cavity (131a) with an inner diameter of D6, where D5 ≥ D2, 8 mm ≤ D5 ≤ 18 mm, and satisfies 0.125D5 ≤ D6 ≤ 0.47D5.

9. The electric valve according to claim 8, characterized in that, 0.125D5≤D6≤0.40D5; 0.175D5≤D6≤0.35D5; 0.155D5≤D6≤0.375D5.

10. The electric valve according to any one of claims 1-9, characterized in that, 20°≤θ1≤40°;25° ≤θ1≤45°.

11. The electric valve according to claim 10, characterized in that, The valve core assembly (13) includes a valve core upper cavity (131d), and the balance channel (133) communicates with the valve core upper cavity (131d); the electric valve includes a rod component (15), the rod component (15) is fixedly connected to the valve core portion (131), the valve core assembly (13) includes an elastic element (132), the elastic element (132) is located in the valve core upper cavity (131d), the upper end of the elastic element (132) abuts against part of the rod component (15), and the lower end of the elastic element (132) abuts against the lower end face forming the valve core upper cavity (131d).

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