Electronic expansion valve and refrigeration equipment

Abstract

The utility model discloses an electronic expansion valve and refrigeration equipment, and relates to the technical field of electronic expansion valves. A valve seat of the electronic expansion valve is provided with a main body part of a valve port; the valve needle can axially move to open or close the valve port; the mounting piece is arranged on the main body part and provided with a flow guide channel, and the silencing block is arranged in the flow guide channel; the first connecting pipe is sleeved with the mounting part, an annular gap is formed between the inner wall of the first connecting pipe and the outer wall of the mounting part, and the mounting part is further provided with a bypass hole communicating the annular gap with the flow guide channel. The flow regulation requirements under different working conditions are met through the annular gap and the bypass hole, normal throttling of the electronic expansion valve is not affected even if the noise reduction net is blocked by impurities, the valve body cannot be blocked, and the normal throttling function of the electronic valve is maintained.

Description

Technical Field

[0001] This utility model relates to the field of electronic expansion valve technology, and in particular to an electronic expansion valve and a refrigeration device. Background Technology

[0002] The electronic expansion valves used in current air conditioning systems are prone to generating flow noise during refrigerant throttling, a problem that is particularly prominent when the indoor unit is running. High-frequency refrigerant noise not only disrupts the quietness of the environment but also directly affects the user experience.

[0003] Current industry solutions primarily focus on valve body structure optimization, including improving valve port shape and adjusting valve cavity geometry. The noise suppression effectiveness of these solutions is strongly correlated with the operating conditions of the refrigeration system. When system pressure, flow rate, and other parameters change, the noise reduction efficiency fluctuates significantly, making it difficult for these solutions to adapt to different refrigeration systems. Utility Model Content

[0004] The main objective of this invention is to provide an electronic expansion valve and a refrigeration device, aiming to...

[0005] To achieve the above objectives, the electronic expansion valve proposed in this utility model includes:

[0006] A valve body assembly, including a valve seat, the valve seat including a body portion having a valve port;

[0007] A valve needle assembly, including a valve needle that is axially movable to open or close the valve port;

[0008] The mounting component is located on the main body and has a flow guide channel communicating with the valve port;

[0009] A silencer block is disposed at the end of the flow guide channel away from the valve port; and

[0010] A first connecting pipe is fitted with the mounting component; there is an annular gap between the inner wall of the first connecting pipe and the outer wall of the mounting component, and the mounting component is provided with a bypass hole that connects the annular gap and the flow channel.

[0011] In one embodiment, the electronic expansion valve further includes an annular bushing, and the valve seat (11) includes a connecting portion protruding from the main body in a direction away from the valve port, the connecting portion being provided with a communicating hole communicating with the valve port;

[0012] The annular bushing is located at one end of the mounting member near the connecting portion. The first connecting pipe and the mounting member abut against the annular bushing. The inner wall of the first connecting pipe and the outer wall of the mounting member form the annular gap in the direction away from the annular bushing. The bypass hole is located on the portion of the mounting member not covered by the annular bushing.

[0013] In one embodiment, the mounting component has a mounting groove at one end away from the muffler block. The inner diameter of the mounting groove is larger than the inner diameter of the flow channel to form a limiting step. The connecting part is embedded in the mounting groove and abuts against the limiting step.

[0014] In one embodiment, the connecting hole is a tapered opening that gradually widens in the direction away from the valve port.

[0015] In one embodiment, the minimum distance from the center of the bypass hole to the valve port is H. b The height of the annular bushing is H. a Satisfying 3mm≤H a <H b ≤10mm.

[0016] In one embodiment, the minimum distance between the surface of the silencer block away from the valve port and the valve port is H, where H ≤ 20 mm.

[0017] In one embodiment, the ratio of the cross-sectional area of ​​the bypass hole to the cross-sectional area of ​​the valve port is in the range of 1-1.5.

[0018] In one embodiment, the minimum distance of the annular gap (c) is H. c 0.2mm < H c <2mm.

[0019] In one embodiment, the ratio of the minimum cross-sectional area of ​​the annular gap to the cross-sectional area of ​​the valve port is in the range of 1-1.5.

[0020] In one embodiment, a plurality of bypass holes are provided at circumferential intervals in the mounting member.

[0021] In one embodiment, the bypass hole is shaped as a straight hole or a flared hole.

[0022] In one embodiment, the silencing block includes at least one silencing mesh through which refrigerant passes.

[0023] In one embodiment, the annular bushing is made of stainless steel or copper.

[0024] This utility model also proposes a refrigeration device, including an electronic expansion valve as described in any of the above embodiments.

[0025] The technical solution of this utility model forms an annular gap between the first connecting pipe and the mounting component. The mounting component has a flow guiding channel, and the flow regulation requirements under different operating conditions are adapted through the annular gap and bypass hole. This solves the problem of high-frequency noise generated by the refrigerant at the throttling valve port due to turbulence and cavitation caused by the sudden increase in flow velocity and pressure change in traditional electronic expansion valves. The different operating conditions are as follows: Under small opening conditions, the refrigerant can flow back from the bypass hole to the flow guiding channel, allowing the refrigerant at the manifold valve port to pass through the silencer block, improving the noise reduction effect. Under fully open or large opening conditions (at least half the valve port opening), the refrigerant flowing out of the valve cavity mainly flows out through the valve port and passes through the flow guiding channel and the silencer block for noise reduction. Furthermore, regardless of whether it is a small opening or a fully open or large opening condition, when impurities in the refrigerant cause the silencer block to become blocked, the bypass hole can also provide an auxiliary flow path for the refrigerant. This effectively avoids the complete blockage of the valve body due to filter clogging, ensuring continuous operation of the system. Attached Figure Description

[0026] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0027] Figure 1 A schematic diagram of an embodiment of the electronic expansion valve provided by this utility model;

[0028] Figure 2 for Figure 1 A magnified view of a section at point A in the middle;

[0029] Figure 3 for Figure 2 A magnified view of a section at point B in the middle;

[0030] Figure 4 For different sizes of H b A line graph showing the corresponding noise values;

[0031] Figure 5 A line graph showing the noise values ​​corresponding to different distances H;

[0032] Figure 6 The CFD simulation diagram shows the fluid velocity distribution of the electronic expansion valve.

[0033] Figure 7 Line graph showing the ratio of the cross-sectional area of ​​the bypass orifice and the valve port to the corresponding noise value;

[0034] Figure 8This is a line graph showing the ratio of the cross-sectional area of ​​the annular gap and the valve port to the corresponding noise value.

[0035] Explanation of icon numbers:

[0036] 1A, First connecting pipe;

[0037] c. Annular gap;

[0038] 10. Valve body assembly;

[0039] 11. Valve seat; 12. Main body; 12a. Valve port; 13. Connecting part; 13a. Communicating hole;

[0040] 20. Valve needle assembly; 21. Valve needle;

[0041] 31. Mounting component; 31a. Flow channel; 31b. Bypass hole; 31c. Mounting groove; 31d. Limiting step; 32. Silencing block; 321. Silencing mesh;

[0042] 40. Annular bushing.

[0043] The realization of the purpose, functional features and advantages of this utility model will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0044] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present utility model.

[0045] It should be noted that if the embodiments of this utility model involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0046] Furthermore, if the embodiments of this utility model involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this utility model.

[0047] The electronic expansion valves used in current air conditioning systems are prone to generating flow noise during refrigerant throttling, a problem that is particularly prominent when the indoor unit is running. High-frequency refrigerant noise not only disrupts the quietness of the environment but also directly affects the user experience.

[0048] Current industry solutions primarily focus on valve body structure optimization, including improving valve port shape and adjusting valve cavity geometry. The noise suppression effectiveness of these solutions is strongly correlated with the operating conditions of the refrigeration system. When system pressure, flow rate, and other parameters change, the noise reduction efficiency fluctuates significantly, making it difficult for these solutions to adapt to different refrigeration systems.

[0049] This invention proposes an electronic expansion valve, which aims to solve the problem of refrigerant noise generated by electronic expansion valves.

[0050] Please see Figures 1 to 3 In one embodiment of the present invention, the electronic expansion valve includes a valve body assembly 10, a valve needle assembly 20, a first connecting pipe 1A, a mounting component 31, a silencer block 32, and an annular bushing 40. The valve seat 11 includes a connecting portion 13 protruding from the main body 12 in a direction away from the valve port 12a. The connecting portion 13 is provided with a connecting hole 13a that communicates with the valve port 12a.

[0051] An annular bushing 40 is provided at one end of the mounting member 31 near the connecting part 13. The first connecting pipe 1A and the mounting member 31 abut against the annular bushing 40. The inner wall of the first connecting pipe 1A and the outer wall of the mounting member 31 form an annular gap c in the direction away from the annular bushing 40. The bypass hole 31b is provided in the part of the mounting member 31 that is not covered by the annular bushing 40.

[0052] In another embodiment, the annular bushing 40 can be omitted, that is, the electronic expansion valve includes a valve body assembly 10, a valve needle assembly 20, a first connecting pipe 1A, a mounting component 31, and a silencer block 32.

[0053] The valve body assembly 10 includes a valve seat 11, the valve seat 11 includes a main body portion 12 having a valve port 12a, and the valve needle assembly 20 includes a valve needle 21 that is axially movable to open or close the valve port 12a.

[0054] Mounting component 31 is provided on the main body 12 (e.g., by snap-fit, welding, adhesive fixation, etc.). Mounting component 31 has a flow channel 31a communicating with valve port 12a. Silencing block 32 is provided at the end of flow channel 31a away from valve port 12a. Mounting component 31 is sleeved on the first connecting pipe 1A. There is an annular gap c between the inner wall of the first connecting pipe 1A and the outer wall of mounting component 31. Mounting component 31 is provided with a bypass hole 31b that communicates the annular gap c and flow channel 31a.

[0055] The minimum inner diameter of the first connecting pipe 1A is greater than the maximum outer diameter of the mounting part 31. The first connecting pipe 1A is fixed to the main body 12 of the valve seat 10. For example, a mark is made on the bottom of the main body 12, and the first connecting pipe 1A is welded to the valve seat 10 at the mark. Alternatively, a groove for pre-fixing the first connecting pipe 1A is opened at the bottom of the main body 12. The first connecting pipe 1A is fixed in the groove and can be further welded. Similarly, the fixing of the mounting part 31 to the main body 12 can also refer to the fixing of the first connecting pipe 1A.

[0056] The technical solution of this utility model solves the problem of high-frequency noise generated by turbulence and cavitation caused by a sudden increase in flow velocity and pressure change at the throttling valve orifice in traditional electronic expansion valves, through the formation of an annular gap between the first connecting pipe and the mounting component. The mounting component has a flow guiding channel. After passing through the valve orifice, the refrigerant enters the flow guiding channel and is divided into fine streams in the silencing block, reducing the flow velocity and constraining the flow direction, thus reducing turbulent collisions and vibration noise. At the same time, because of the existence of the bypass hole, even if the silencing mesh is blocked by impurities, it will not affect the normal throttling of the electronic expansion valve, and will not cause the valve body to be blocked, thus maintaining the normal throttling function of the electronic valve.

[0057] Taking the installation component 31 installed in the first connecting pipe 1A as an example.

[0058] When the electronic expansion valve is at a small opening, the flow velocity through the valve port 12a is relatively large, and the bypass hole 31b is relatively close to the valve port 12a. Under the action of negative pressure difference, the refrigerant is more likely to flow back from the downstream through the annular gap c through the bypass hole 31b, and then merge with the central jet of the valve port 12a, so that more refrigerant flows through the silencer block 32 to reduce noise and improve the noise reduction effect.

[0059] Furthermore, due to the presence of the bypass hole 31b, even if the silencing mesh 321 is blocked by impurities, it can still flow out through the bypass hole 31b to the annular gap c, without affecting the normal throttling of the electronic expansion valve, and will not cause the valve body 10 to be blocked, thus maintaining the normal throttling function of the electronic valve.

[0060] When the electronic expansion valve is fully open or at a large opening, the refrigerant is throttled and mainly flows out through the guide channel 31a and the silencing block 32. It is divided into thin streams in the silencing mesh 321 (such as honeycomb or porous structure) of the silencing block 22, the flow velocity is reduced and the flow direction is constrained, reducing turbulent collision and vibration noise.

[0061] In addition, because of the existence of the bypass hole 31b, even if the silencing mesh 321 is blocked by impurities, it can still flow out to the annular gap c through the bypass hole 31b, without affecting the normal throttling of the electronic expansion valve, and will not cause the valve body 10 to be blocked, thus maintaining the normal throttling function of the electronic valve.

[0062] Understandably, without changing the mounting component 31 and the silencing block 32, the size of different connecting pipes can be adapted by changing the wall thickness of the annular bushing 40.

[0063] Furthermore, the technical solution of this utility model, by using the cooperation of the annular bushing 40 and the mounting part 31, not only fixes the flow but also forms a controllable bypass gap, adapting to the flow regulation needs under different working conditions. By solving the problem of high-frequency noise generated by the refrigerant in the traditional electronic expansion valve due to the sudden increase in flow velocity and pressure change at the throttling valve port 12a, the refrigerant enters the guide channel 31a after passing through the valve port 12a. It is divided into fine streams in the multiple silencing meshes 321 (such as honeycomb or porous structure) of the silencing block 32, the flow velocity is reduced and the flow direction is constrained, reducing turbulent collision and vibration noise.

[0064] Setting up the annular bushing 40 and mounting bracket 31 does not require changing the structure of the expansion valve body because the silencer block 32 has multiple silencer meshes 321. After the refrigerant passes through the silencer block 32, any air bubbles in the refrigerant will be broken down into smaller bubbles, preventing large bubbles from bursting and generating noise. The sound energy is absorbed and weakened, reducing the noise level. At the same time, because of the existence of the bypass hole 31b, even if the silencer meshes 321 are blocked by impurities, it will not affect the normal throttling of the electronic expansion valve, and will not cause the valve body to become blocked, maintaining the normal throttling function of the electronic valve.

[0065] Thus, the annular bushing 40 and the mounting part 31 can be used as independent optional accessories. The annular bushing 40 can be adapted to the first connecting pipe 1A of different sizes, which has strong versatility and adaptability.

[0066] The electronic expansion valve includes a nut and a lead screw. The nut is sealed to the valve body and is located on the top of the valve body. The lead screw is threaded to the nut. The valve body is also fitted with a housing, which covers the lead screw and nut. The lead screw passes through the nut and is fixed to a limiting plate at the end away from the nut. The limiting plate is connected to a rotor. A coil assembly can be fitted outside the housing. Under the electromagnetic action of the coil assembly, the lead screw is driven to rotate circumferentially through the rotor and the limiting plate. The end of the lead screw away from the limiting plate is connected to the valve needle 21. Because the nut is fixed to the valve body, the valve needle 21 moves up and down axially with the lead screw, thereby adjusting the opening degree of the flow channel formed between the opening and the valve port 12a.

[0067] There are various ways to connect the valve needle 21 to the lead screw. In this embodiment, in order to prevent the valve needle 21 from rotating with the lead screw, the valve needle 21 is connected to the lead screw through a bearing. The end of the lead screw is fixed by a locking member. The locking member abuts against the bearing to drive the valve needle 21 to move up and down, and does not rotate with the lead screw in the circumferential direction.

[0068] In addition, a compression spring is provided between the lead screw and the bearing. The compression spring stores elastic force when the valve needle 21 moves upward in the axial direction and releases it when the valve needle 21 moves downward in the axial direction, so that the valve needle 21 can also have a certain adjustment capability when sealing the valve port 12a.

[0069] In other embodiments, the valve needle 21 and the lead screw are engaged by a threaded structure; or the valve needle 21 and the lead screw are elastically connected by a spring; or the valve needle 21 and the lead screw assembly can be connected as a whole by welding or interference fitting.

[0070] There are various ways to connect the valve needle 21 to the lead screw. The specific method to choose depends on the valve's design requirements, operating environment, and operational needs.

[0071] The silencing block 32 includes at least one silencing mesh 321 through which refrigerant passes. Specifically, the silencing mesh 321 is a multi-layered filter. The silencing mesh 321 includes multiple mesh openings, which can refine the bubbles in the refrigerant into smaller bubble groups, thereby reducing the high-frequency noise generated by bubble bursting.

[0072] The cross-sectional shape of the mesh can be circular, rectangular, or irregular (such as spiral or honeycomb), and the diameter can be set to be smaller than the size of common large air bubbles in refrigerant to ensure that air bubbles are forcibly broken into tiny air bubbles as they pass through.

[0073] Understandably, when the refrigerant flows through valve port 12a into guide channel 31a, air bubbles enter the mesh of silencer block 32 along with the refrigerant. Due to the narrow channel and surface tension, large bubbles are broken down into smaller bubbles (e.g., diameter reduced from 5 mm to 0.5 mm). The energy released when these tiny bubbles burst is significantly reduced, thereby reducing high-frequency noise. Furthermore, the multiple meshes disperse the refrigerant flow velocity, preventing turbulent noise generated by localized high-speed flow.

[0074] Compared to existing technologies that rely solely on valve port 12a or valve cavity shape optimization, this invention offers greater specificity and noise reduction effectiveness. Furthermore, the parameters of the silencer block 32 can be flexibly adjusted according to the refrigerant flow and pressure range of different refrigeration systems, making it suitable for various application scenarios and easy to install and maintain.

[0075] Please refer to Figure 1 and Figure 2 Specifically, multiple bypass holes 31b are provided at circumferential intervals along the journal neck.

[0076] Multiple bypass holes 31b ensure that the refrigerant can find an unobstructed outlet under any circumstances. Understandably, the size of each bypass hole 31b can be adjusted to meet specific needs, ensuring that under normal operating conditions, the refrigerant is primarily refined through the silencer block 32. However, in the event of filter clogging, the multiple bypass holes 31b provide multiple backup flow paths, ensuring that the refrigerant can continue to flow and maintain normal system operation.

[0077] Multiple bypass holes 31b are evenly distributed on the sidewall of the journal journal. These bypass holes 31b can be arranged at equal intervals along the circumference of the journal journal, or their distribution can be optimized according to the direction and velocity of the refrigerant flow to ensure that the refrigerant can flow out from a single, unobstructed outlet regardless of its direction of inflow. This improves the uniformity of refrigerant flow and reduces the possibility of localized pressure buildup. Furthermore, the number of bypass holes 31b can be adjusted according to the specific operating conditions required in the application; for example, increasing the number of bypass holes 31b can improve safety, or reducing the number can simplify the structure.

[0078] Specifically, the number and size of the bypass holes 31b can be adjusted according to actual needs to adapt to different operating conditions. Under normal circumstances, the total cross-sectional area of ​​the bypass holes 31b is greater than or equal to the cross-sectional area of ​​the valve port 12a, and the cross-sectional area of ​​a single bypass hole 31b is smaller than that of the valve port 12a, to ensure that under normal operating conditions, the refrigerant is mainly refined through the filter screen.

[0079] In other words, under small opening conditions, the refrigerant can flow back from the bypass hole 31b to the guide channel 31a, allowing the refrigerant at the manifold 12 to pass through the silencer block 32, thus improving the noise reduction effect. When fully open or at a large opening (at least halfway open of the valve port 12), the refrigerant flowing from the valve chamber 11 mainly flows out through the valve port 12 and passes through the guide channel 31a, where it passes through the silencer block 32 for noise reduction. Furthermore, regardless of whether it's a small opening or a fully open or large opening condition, if impurities in the refrigerant cause the silencer block 32 to become blocked, the bypass hole 31b can still provide an auxiliary flow path for the refrigerant. This effectively prevents the valve body 10 from becoming completely blocked due to filter clogging, ensuring continuous system operation.

[0080] It should be noted that the cross-sectional area, also known as the flow cross-sectional area, refers to the actual flow area of ​​the fluid when it passes through the orifice. This is different from the nominal cross-sectional area of ​​the orifice because the actual fluid flow is affected by the viscosity effect, which causes the flow stream to contract, thus forming the minimum flow cross-sectional area. In other words, the flow cross-sectional area is the effective flow area of ​​the fluid when it passes through the orifice.

[0081] Reference Figure 3 Specifically, the mounting part 31 has a mounting groove 31c at the end away from the muffler block 32. The inner diameter of the mounting groove 31c is larger than the inner diameter of the guide channel 31a to form a limiting step 31d. The connecting part 13 is embedded in the mounting groove 31c and abuts against the limiting step 31d.

[0082] An annular limiting step 31d is formed between the mounting groove 31c and the flow guiding channel 31a. The noise-absorbing block 32 is installed on the annular limiting step 31d. It can be understood that the noise-absorbing block 32 can be interference-fitted with the annular limiting step 31d. To increase its reliability, it can be fixed to the mounting part 31 by means of adhesive, riveting, etc. Installing the noise-absorbing block 32 in the mounting groove 31c allows the noise-absorbing block 32 to be firmly fixed in the predetermined position, avoiding the increase of complexity and cost due to the use of additional fixing devices.

[0083] Under small opening conditions, the refrigerant, after throttling, flows into the guide channel 31a through valve port 12a. Because the refrigerant flows out of valve port 12a from valve seat 11 in the direction of guide channel 31a, most of the refrigerant flows through guide channel 31a. Furthermore, the refrigerant can flow back into guide channel 31a through bypass hole 31b, allowing the refrigerant to pass through the silencing block 32 at valve port 12. After passing through the silencing block 32, the sound energy is absorbed and weakened. If there are air bubbles in the refrigerant, they will be broken down into smaller bubbles, preventing large bubbles from bursting and generating noise, thus reducing the noise level. Simultaneously, due to the presence of bypass hole 31b, even if the multi-layer filter screen of the silencing block 32 in guide channel 31a is clogged with impurities, it will not affect the normal throttling of the electronic expansion valve and will not cause the valve body to become blocked.

[0084] Under fully open or wide-opening conditions, the refrigerant mainly flows out through the silencer block 32 in the flow guide channel 31a. After passing through the silencer block 32, the sound energy of the refrigerant is absorbed and weakened. If there are air bubbles in the refrigerant, they will be refined into smaller bubbles, preventing large bubbles from bursting and generating noise, thus reducing the noise level. At the same time, because of the existence of the bypass hole 31b, even if the multi-layer filter screen of the silencer block 32 in the flow guide channel 31a is blocked by impurities, it will not affect the normal throttling of the electronic expansion valve and will not cause the valve body to become blocked.

[0085] The annular bushing 40 can be adjusted in size as needed, making the silencing structure a universal component and improving its compatibility with different connecting pipes.

[0086] In one embodiment, the bypass orifice 31b adopts a tapered flared design (e.g., small inlet diameter and large outlet diameter) to further reduce the flow rate.

[0087] In one embodiment, the bypass hole 31b is a through hole with a constant diameter.

[0088] Please refer to Figure 2 The height of the annular bushing 40 is Ha, and the minimum distance from the center of the bypass hole 31b to the valve port 12a is H. b Satisfying 3mm≤H a <H b ≤10mm. In order to ensure the normal function of the bypass hole 31b, the annular bushing 40 should be avoided from blocking the bypass hole 31b.

[0089] H a The thickness is greater than 3mm to ensure manufacturability. If it is too small, the contact area between the annular bushing 40 and the first connecting pipe 1A will be too small, which is not conducive to the pre-fixation of the first connecting pipe 1A during assembly, so as to facilitate subsequent welding. a ≤H b The purpose of ≤10mm is to ensure that the bypass hole 31b is as close as possible to the valve port 12a while meeting process requirements. This way, when the refrigerant is ejected from the valve port 12a in a jet-like manner under small opening conditions, its velocity is very high. According to Bernoulli's equation in fluid mechanics, the higher the velocity, the lower the pressure. As the refrigerant flows downstream from the valve port 12a, its velocity gradually decreases, and its pressure gradually recovers. The closer the bypass hole 31b is to the valve port 12a, the lower the pressure at the bypass hole 31b relative to the downstream. Therefore, under the influence of the negative pressure difference, the refrigerant can more easily flow back from the downstream through the annular gap c and through the bypass hole 31b, then merge with the central jet and pass through the silencing mesh 321. If the bypass hole 31b is too far from the valve port 12a, the negative pressure difference becomes smaller or even positive, causing the refrigerant in the central jet to flow towards the annular gap c through the bypass hole 31b, resulting in some refrigerant not flowing through the silencing mesh for noise reduction.

[0090] Furthermore, even under fully open or wide-open conditions, the refrigerant can mainly flow out through the silencer block 32 of the flow channel 211. After the refrigerant flows out through the silencer block 32, the sound energy is absorbed and weakened. If there are air bubbles in the refrigerant, they will be refined into small air bubbles, avoiding the noise generated by the rupture of large air bubbles and reducing the noise level.

[0091] Regardless of whether it's in a small opening condition or a fully or large opening condition, the bypass hole 31b is close to the valve port 12a, shortening the path from the valve port 12a to the bypass hole 31b. Even when the silencing mesh 321 of the silencing block 32 is blocked by impurities, the fluid can still flow out through the bypass hole 31b to the annular gap c, without affecting the normal throttling of the electronic expansion valve or causing the valve body 10 to become blocked, thus maintaining the normal throttling function of the electronic valve.

[0092] The table below shows the minimum distance H from the center of bypass hole 31b to valve port 12a. b Noise levels corresponding to different sizes (where the noise level of the electronic expansion valve without the above-mentioned silencing structure in the first connecting pipe 1A is 45.57dB):

[0093] Hb size / mm 4 6 8 10 12 14 Noise level in dB(A) 38.97 38.96 39.03 39.09 41.25 42.51

[0094] Based on the content of the table above and in combination Figure 4 The noise levels can be clearly compared with H b The size range of 4mm-10mm provides better noise control. Although the noise level increases when the size is greater than 10mm, it is still less than the noise level of 45.57dB of the electronic expansion valve without the above-mentioned silencing structure.

[0095] Specifically, the minimum distance between the surface of the silencing block 32 furthest from the valve port 12a and the valve port 12a is H, where H ≤ 20 mm. The valve port 12a is the core noise source generated by the sudden change in flow velocity and turbulence during refrigerant throttling. The silencing block 32's proximity to the valve port 12a (H ≤ 20 mm) ensures that the inlet of the silencing mesh 321 is as close as possible to the noise-generating area, absorbing and scattering sound wave energy before it diffuses with the flow, thus achieving near-field sound energy interception and avoiding sound energy attenuation delay and efficiency loss caused by long-distance propagation. However, if the silencing block 32 is too close to the valve port 12a, it may affect the refrigerant flow, increase flow resistance, and reduce system efficiency. Limiting H to ≤ 20 mm effectively reduces noise without significantly increasing flow resistance.

[0096] If the silencer block 32 is too far from the valve port 12a (H>20mm), the silencer block cannot absorb and dissipate sound energy in time at the place with the greatest noise, and the noise reduction effect will not be achieved. The distance between the silencer block 32 and the valve port 12a is limited by the first connecting pipe 1A, and the installation space between the air conditioner indoor unit valve body and the first connecting pipe 1A is limited in length.

[0097] The table below shows the H distance and the corresponding noise value range.

[0098]

[0099] Based on the content of the table above and in combination Figure 5 The noise levels show that when the distance H between the silencing block 32 and the valve port 12a is greater than 20mm, the silencing effect weakens and the noise increases. Therefore, if low-noise operation is required, H should be controlled within a range of less than 20mm.

[0100] Further integration Figure 6 The main body in the picture and Figure 1 Correspondingly, there are curved and straight pipe sections, with valve port 12a located at the bottom of the main body. Figure 6 On the left side of the screen, there is a speed and color chart. The colors, from red to dark blue, correspond to the speed values. The legend shows that the speed range is from 0 to 77.61 m / s, and the brighter the color, the higher the speed.

[0101] The highest fluid velocity occurs in certain areas, especially at the section from the opening to the straight pipe, based on experimental observations of the transparent valve body and CFD simulation calculations. Figure 6 It can be seen that the core area of ​​the throttling noise is within 20mm behind the valve port 12a (i.e., H≤20mm), such as Figure 6 The simulation calculation cloud diagram is shown in the figure. Figure 6 The fluid in the valve port 12a is visible as a bluish-green fluid. Therefore, the entire silencing structure needs to be installed in the core area of ​​the throttling noise for the best noise reduction effect, i.e., H≤20mm.

[0102] Furthermore, the ratio of the cross-sectional area of ​​the bypass hole 31b to the cross-sectional area of ​​the valve port 12a ranges from 1 to 1.5. The cross-sectional area is the flow channel cross-sectional area of ​​the hole. The reason why the total cross-sectional area of ​​the bypass hole 31b is greater than or equal to the cross-sectional area of ​​the valve port 12a is to ensure that the flow capacity in the fully open state is not affected. The reason why it is less than or equal to 1.5 times is that if the cross-sectional area of ​​the bypass hole 31b is too large, a lot of refrigerant will flow away from the bypass hole 31b without sufficient noise reduction by the silencer block 32, thus weakening the noise reduction effect.

[0103] The table below shows the ratio of the cross-sectional area of ​​the bypass orifice to that of the valve port and the corresponding noise values.

[0104]

[0105]

[0106] Based on the content of the table above and in combination Figure 7 The noise levels show that when the ratio of the cross-sectional area of ​​the bypass hole 31b to that of the valve port 12a is greater than 1.5, the noise reduction effect weakens and the noise increases. Therefore, if low-noise operation is required, the ratio of the bypass hole to the valve port should be controlled within the range of ≤1.5.

[0107] Furthermore, the ratio of the cross-sectional area of ​​the annular gap c to the cross-sectional area of ​​the valve port 12a ranges from 1 to 1.5. The reason why the minimum cross-sectional area of ​​the annular gap c is greater than or equal to the cross-sectional area of ​​the valve port 12a is to ensure that the flow capacity in the fully open state is not affected. The reason why it is less than or equal to 1.5 times is that if the cross-sectional area of ​​the annular gap c is too large, it will occupy the space of the silencing block 32, resulting in a smaller cross-sectional area of ​​the silencing block 32. That is, the volume of the silencing block 32 used to refine bubbles and absorb sound energy will decrease, and the silencing effect will be worse.

[0108] The table below shows the ratio of the annular gap c to the cross-sectional area of ​​the valve port 12a and the corresponding noise values.

[0109] Annular gap / valve port 1 1.2 1.5 1.7 1.9 2.1 Noise level in dB(A) 39.89 40.06 40.01 41.01 41.92 42.95

[0110] Based on the content of the table above and in combination Figure 8 The noise levels show that when the ratio of the annular gap c to the cross-sectional area of ​​the valve port 12a is greater than 1.5, the silencing effect weakens and the noise increases. Therefore, if low-noise operation is required, the ratio of the annular gap c to the valve port 12a should be controlled within the range of ≤1.5.

[0111] Please refer to Figure 2 Specifically, the distance of the annular gap c is Hc, where 0.2mm < Hc < 2mm. By precisely controlling the refrigerant flow rate and pressure release rate of the bypass diversion, noise can be suppressed while avoiding excessive diversion that would reduce throttling efficiency.

[0112] Specifically, the flow cross-sectional area of ​​the annular gap c is larger than that of the valve port 12a. The annular gap c is a bypass structure in the design, allowing some refrigerant to pass through, thereby reducing flow and pressure fluctuations in the main channel. If the flow cross-sectional area of ​​the annular gap c is larger than that of the valve port 12a, it means that the bypass channel is wider than the main channel, which can divert more refrigerant, helping to reduce flow velocity and pressure fluctuations in the main channel, thereby reducing noise.

[0113] Specifically, the connecting hole 13a is a gradually expanding conical opening in the direction away from the valve port 12a. Specifically, the valve body has a conical flare at the bottom, facing away from the valve cavity, which connects to the valve port 12a. The conical flare is located at the bottom of the valve body, extending away from the valve cavity, and its inner wall is a gradually expanding cone shape (e.g., cone angle 15°–30°), with its end connecting to the valve port 12a. When the refrigerant flows out from the valve port 12a, the conical flare acts as a gradual expansion, allowing the fluid to transition smoothly, reducing sudden changes in flow velocity, thereby reducing turbulence and pressure drop. This not only improves energy efficiency but also reduces noise.

[0114] In one embodiment, the annular bushing 40 is made of stainless steel or copper.

[0115] In one embodiment, the annular bushing 40 is made of an elastic material (such as rubber), which deforms and reduces the gap under high pressure, automatically suppressing excessive flow diversion. In summary, by adjusting the gap size through the bushing thickness, the flow diversion ratio between the main channel and the bypass is dynamically balanced, avoiding sudden pressure changes.

[0116] This utility model also proposes a refrigeration device, which can be a household air conditioner (inverter air conditioner), a commercial freezer, an industrial refrigeration system, a cold chain logistics equipment, a heat pump system, etc.

[0117] The refrigeration equipment includes the aforementioned electronic expansion valve. The specific structure of the electronic expansion valve is as described in the above embodiments. Since this refrigeration equipment adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be elaborated here.

[0118] The above description is merely an exemplary embodiment of the present utility model and does not limit the scope of protection of the present utility model. Any equivalent structural transformations made based on the technical concept of the present utility model and the contents of the present utility model specification and drawings, or direct / indirect applications in other related technical fields, are included within the scope of protection of the present utility model.

Claims

1. An electronic expansion valve, characterized in that, include: A valve body assembly, including a valve seat, the valve seat including a body portion having a valve port; A valve needle assembly, including a valve needle that is axially movable to open or close the valve port; The mounting component is located on the main body and has a flow guide channel communicating with the valve port; A noise-absorbing block is located at the end of the flow guide channel away from the valve port; as well as A first connecting pipe is fitted with the mounting component; there is an annular gap between the inner wall of the first connecting pipe and the outer wall of the mounting component, and the mounting component is provided with a bypass hole that connects the annular gap and the flow channel.

2. The electronic expansion valve as described in claim 1, characterized in that, The electronic expansion valve includes an annular bushing, and the valve seat includes a connecting portion protruding from the main body in a direction away from the valve port, the connecting portion being provided with a communicating hole communicating with the valve port; The annular bushing is located at one end of the mounting member near the connecting portion. The first connecting pipe and the mounting member abut against the annular bushing. The inner wall of the first connecting pipe and the outer wall of the mounting member form the annular gap in the direction away from the annular bushing. The bypass hole is located on the portion of the mounting member not covered by the annular bushing.

3. The electronic expansion valve as described in claim 2, characterized in that, The mounting component has a mounting groove at one end away from the muffler block. The inner diameter of the mounting groove is larger than the inner diameter of the flow channel to form a limiting step. The connecting part is embedded in the mounting groove and abuts against the limiting step.

4. The electronic expansion valve as described in claim 2, characterized in that, The connecting hole is a tapered opening that gradually widens in the direction away from the valve port.

5. The electronic expansion valve as described in claim 2, characterized in that, The minimum distance from the center of the bypass hole to the valve port is H. b The height of the annular bushing is H. a Satisfying 3mm≤H a <H b ≤10mm.

6. The electronic expansion valve as described in claim 1, characterized in that, The minimum distance between the surface of the silencer block away from the valve port and the valve port is H, where H ≤ 20 mm.

7. The electronic expansion valve as described in claim 1, characterized in that, The ratio of the cross-sectional area of ​​the bypass hole to the cross-sectional area of ​​the valve port is in the range of 1-1.

5.

8. The electronic expansion valve as described in claim 1, characterized in that, The ratio of the minimum cross-sectional area of ​​the annular gap to the cross-sectional area of ​​the valve port is in the range of 1-1.

5.

9. The electronic expansion valve as described in claim 1, characterized in that, The minimum distance of the annular gap is H. c 0.2mm < H c <2mm.

10. The electronic expansion valve as claimed in claim 1, characterized in that, Multiple bypass holes are provided at circumferential intervals on the mounting component.

11. The electronic expansion valve as claimed in claim 1, characterized in that, The bypass hole is either a straight hole or a flared hole.

12. The electronic expansion valve as claimed in claim 1, characterized in that, The silencing block includes at least one silencing mesh through which refrigerant passes.

13. The electronic expansion valve as described in claim 2, characterized in that, The annular bushing is made of stainless steel or copper.

14. A refrigeration device, characterized in that, Includes the electronic expansion valve as described in any one of claims 1 to 13.

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