Electronic expansion valve and refrigeration apparatus

Abstract

The utility model discloses an electronic expansion valve and refrigeration plant relates to electronic expansion valve technical field, this electronic expansion valve includes valve body, transmission subassembly, valve needle and mounting seat, and valve body has the valve mouth, transmission subassembly includes nut and screw rod, and nut is sealedly connected with valve body, and screw rod is cooperated with the nut thread, valve needle is connected with screw rod, and can be axially removed to open or close the valve mouth, and the circumferential side of mounting seat is sealedly connected with the inner wall of valve body, and the resonance cavity is defined between mounting seat and nut, and the valve cavity that communicates valve mouth is defined with valve body and mounting seat, and mounting seat has the guide channel that is arranged coaxially with nut, and valve needle is worn guide channel and is matched with the clearance of guide channel, wherein, mounting seat still is equipped with the sound -absorbing passage that communicates resonance cavity and valve cavity. The utility model provides technical scheme to utilize mounting seat and divide resonance cavity and valve cavity, and construct the sound -absorbing ware structure through resonance cavity and sound -absorbing passage to reduce the noise that high pressure refrigerant produces in the flow process in valve cavity because of the flow rate mutation.

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] Existing electronic expansion valves generate refrigerant noise during the throttling process (due to the sudden change in flow velocity at the valve port, which causes severe turbulence and cavitation effects, resulting in high-frequency noise). The valve cavity is one of the locations with the highest refrigerant noise, especially affecting the user experience of the indoor unit of the air conditioner. Utility Model Content

[0003] The main purpose of this invention is to propose an electronic expansion valve and a refrigeration device, which aims to use a mounting base to separate an upper and lower resonant cavity and a valve cavity, and to construct a silencer structure through the resonant cavity and the silencer channel, thereby reducing the noise generated by sudden changes in flow velocity of the high-pressure refrigerant during the flow process.

[0004] To achieve the above objectives, this utility model proposes an electronic expansion valve, comprising:

[0005] The valve body has a valve port;

[0006] The transmission assembly includes a nut and a lead screw, wherein the nut is sealed to the valve body and the lead screw is threadedly engaged with the nut;

[0007] A valve needle, connected to the lead screw, is axially movable to open or close the valve port; and

[0008] The mounting base has a periphery that is sealed to the inner wall of the valve body. A resonant cavity is defined between the mounting base and the nut. A valve cavity communicating with the valve port is defined between the valve body and the mounting base. The mounting base has a guide channel coaxially arranged with the nut. The valve needle passes through the guide channel and is clearance-fitted with the guide channel. The mounting base also has a noise-absorbing channel communicating with the resonant cavity and the valve cavity.

[0009] In one embodiment, the mounting base includes an annular base and a journal coaxially disposed with respect to the annular base in a direction away from the nut. The outer diameter of the journal is smaller than the outer diameter of the annular base, forming a stepped surface. The noise-absorbing channel is disposed on the stepped surface, and the guide channel passes through the annular base and the journal.

[0010] In one embodiment, two silencing channels are provided opposite to each other on the annular base, and the line connecting the centers of the two silencing channels passes through the center of the annular base.

[0011] In one embodiment, the valve body has an opening on its periphery for installing a refrigerant connection pipe, and the line connecting the centers of the two silencing channels is parallel to the axis of the opening.

[0012] In one embodiment, the silencing channel is shaped as an oblong or circular hole in cross-section.

[0013] In one embodiment, the cross-sectional area of ​​any one of the silencing channels is greater than the minimum area of ​​the valve port.

[0014] In one embodiment, the length of the silencing channel is L, and the equivalent diameter of the silencing channel is d, where L≥2d.

[0015] In one embodiment, the outer diameter of the annular base is D, and L ≤ D / 4.

[0016] In one embodiment, d ≤ 0.2D, 1 ≤ L / d ≤ 3.

[0017] In one embodiment, the valve port includes a straight edge section that mates with the outer wall of the valve needle and a tapered flared section disposed away from the valve cavity.

[0018] This utility model also proposes a refrigeration device, including the electronic expansion valve as described above.

[0019] This invention's technical solution regulates refrigerant flow through the cooperation of a valve needle and valve port. A Helmholtz resonator structure is formed through a resonant cavity and a silencer channel, converting the noise energy generated by high-speed fluid into heat energy, ultimately reducing the operating noise of the air conditioner's indoor unit. The mounting base connects to the inner wall of the valve body on its periphery, and its top, bottom of the nut, and side wall of the valve body together seal to separate the resonant cavity and the valve cavity. Liquid refrigerant enters the valve cavity through the opening on the periphery of the valve body. The valve needle, driven by a screw, moves downwards, adjusting the opening of the bottom valve port. When the refrigerant is forced through the narrow valve port, its flow velocity increases sharply (producing a whistling sound similar to water flowing through a narrow pipe). When the high-pressure refrigerant enters the resonant cavity from the valve cavity through the silencer channel, the flow velocity decreases due to the sudden expansion of the cross-sectional area (from the orifice to the cavity), and the pressure fluctuation is dispersed. The sound waves are reflected multiple times within the resonant cavity and cancel each other out. Furthermore, the guide channel, in cooperation with the valve needle, can suppress mechanical noise caused by valve needle vibration. Attached Figure Description

[0020] 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.

[0021] Figure 1 A schematic diagram of an embodiment of the electronic expansion valve provided by this utility model;

[0022] Figure 2 for Figure 1 Schematic diagram of the cross-sectional structure at point AA;

[0023] Figure 3 for Figure 1 A schematic diagram of the structure of one embodiment of the mounting base;

[0024] Figure 4 for Figure 3 A structural diagram from another perspective;

[0025] Figure 5 A line graph comparing the internal noise levels of electronic expansion valves with and without mounting base structures at different valve opening degrees;

[0026] Figure 6 A bar chart comparing noise levels at different frequency bands for structures with and without installation.

[0027] Explanation of icon numbers:

[0028] 10. Valve body; 11. Valve port; 11a. Straight edge section; 11b. Conical flared section; 12. Opening; 10a. Resonance cavity; 10b. Valve cavity; 20. Transmission assembly; 21. Nut; 22. Lead screw; 30. Valve needle; 40. Mounting seat; 41. Silencing channel; 42. Guide channel; 40a. Annular base; 40b. Journal neck; 40c. Stepped surface.

[0029] 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

[0030] 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.

[0031] 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.

[0032] 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.

[0033] Existing electronic expansion valves generate refrigerant noise during the throttling process (due to the sudden change in flow velocity at the valve port, which causes severe turbulence and cavitation effects, resulting in high-frequency noise). The valve cavity is one of the locations with the highest refrigerant noise, especially affecting the user experience of the indoor unit of the air conditioner.

[0034] This invention proposes an electronic expansion valve, which aims to use a mounting base to separate an upper and lower resonant cavity and a valve cavity, and to construct a silencer structure through the resonant cavity and a silencer channel, thereby reducing the noise generated by sudden changes in flow velocity of high-pressure refrigerant during the flow of the valve cavity.

[0035] Please see Figures 1 to 4 In one embodiment of the present invention, the electronic expansion valve includes a valve body 10, a transmission assembly 20, a valve needle 30 and a lead screw 22. The valve body 10 has an opening 12 on its periphery and a valve port 11 at its bottom. Figure 1 An opening 12 is formed in the valve body 10 for the insertion of a refrigerant connection pipe. The valve body 10 is welded and sealed to the refrigerant connection pipe. The valve body 10 is also welded and sealed to another refrigerant connection pipe. The transmission assembly 20 includes a nut 21 and a lead screw 22. The nut 21 is sealed to the valve body 10 and is located on the top of the valve body 10. The lead screw 22 is threadedly engaged with the nut 21. The valve body 10 is also fitted with a housing, which covers the lead screw 22 and the nut 21. The lead screw 22 passes through the nut 21. 2. The end away from the nut 21 is fixed to the limiting plate (not shown in the figure), and the limiting plate is connected to the rotor; a coil assembly (not shown in the figure) can be sleeved on the outside of the housing, so that the electromagnetic action of the coil assembly drives the lead screw 22 to rotate circumferentially through the rotor and the limiting plate. The end of the lead screw 22 away from the limiting plate is connected to the valve needle 30. Since the nut 21 is fixed to the valve body 10, the valve needle 30 moves up and down axially with the lead screw 22, so that the opening degree of the flow channel formed between the opening 12 and the valve port 11 can be adjusted.

[0036] There are various ways to connect the valve needle 30 and the lead screw 22. In this embodiment, in order to prevent the valve needle 30 from rotating with the lead screw 22, the valve needle 30 and the lead screw 22 are connected by a bearing. The end of the lead screw 22 is fixed by a locking member. The locking member abuts against the bearing to drive the valve needle 30 to move up and down, and does not rotate with the lead screw 22 in the circumferential direction.

[0037] In addition, a compression spring is provided between the lead screw 22 and the bearing. The compression spring stores elastic force when the valve needle 30 moves upward in the axial direction and releases it when the valve needle 30 moves downward in the axial direction, so that the valve needle 30 can also have a certain adjustment capability when sealing the valve port 11.

[0038] In other embodiments, the valve needle 30 and the lead screw 22 are engaged by a threaded structure; or the valve needle 30 and the lead screw 22 are elastically connected by a spring; or the valve needle 30 and the lead screw 22 assembly can be connected as a whole by welding or interference fitting.

[0039] There are various ways to connect the valve needle 30 and the lead screw 22. The specific method to choose depends on the valve's design requirements, the operating environment, and operational needs.

[0040] Liquid refrigerant enters valve chamber 10b through opening 12 on the side of valve seat. Valve needle 30 is driven downward by screw 22 to adjust the opening of bottom horn-shaped valve port 11. When the refrigerant is forced through the narrow valve port 11, the flow rate increases sharply. When the high-speed refrigerant passes through the valve port 11, turbulence and pressure pulsation are generated (similar to the whistling sound of water flowing through a narrow water pipe).

[0041] To reduce refrigerant noise in valve cavity 10b, a mounting seat 40 is provided inside valve body 10. The periphery of mounting seat 40 is sealed to the inner wall of valve body 10 (by welding or interference fit, etc.). Resonance cavity 10a is defined between mounting seat 40 and nut 21. Valve body 10 and mounting seat 40 define valve cavity 10b that connects opening 12 and valve port 11. Mounting seat 40 is also provided with a noise reduction channel 41 that connects resonance cavity 10a and valve cavity 10b.

[0042] The mounting base 40 is connected to the inner wall of the valve cavity 10b through its periphery. The top of the mounting base 40, together with the bottom of the nut 21 and the side wall of the valve cavity 10b, forms a seal to separate the upper and lower cavities. The mounting base 40 is provided with a sound-absorbing channel 41, which connects the resonant cavity 10a and the valve cavity 10b to form a "bottleneck + cavity" structure (analogous to the bottle mouth and bottle body). When the high-pressure refrigerant enters the upper cavity from the valve cavity 10b through the sound-absorbing channel 41, the flow rate decreases due to the sudden expansion of the cross-sectional area (from the hole to the cavity), and the pressure fluctuation is dispersed. The noise-reduced refrigerant flows out axially from the lower cavity through the trumpet-shaped valve port 11 and enters the evaporator to complete the heat exchange.

[0043] The silencing channel 41 and the resonant cavity 10a form an acoustic structure similar to a Helmholtz resonator. The silencing channel 41 is equivalent to a sound mass element, and the resonant cavity 10a is a sound capacitive element. When the high-pressure fluid enters the resonant cavity 10a through the silencing channel 41, it undergoes an adiabatic expansion effect due to the sudden expansion of volume, and part of the kinetic energy is converted into heat energy.

[0044] Furthermore, the Helmholtz resonator (resonance cavity 10a and silencing channel 41) is directly integrated inside the valve body 10, eliminating the need for an external silencer or changes to the external dimensions of the valve body 10, thus meeting the requirements of compact design.

[0045] To prevent the valve needle 30 from shaking and causing noise, the mounting base 40 has a guide channel 42 coaxially set with the nut 21. The valve needle 30 passes through the guide channel 42 and is clearance-fitted with the guide channel 42 to suppress the mechanical noise caused by the vibration of the valve needle 30. This solves the problem of noise caused by the high-speed flow of refrigerant during the throttling process of traditional electronic expansion valves, which affects the user experience, especially in the indoor unit of air conditioners.

[0046] It should be noted that the valve port 11 includes a straight edge section 11a that mates with the outer wall of the valve needle 30 and a tapered flared section 11b located away from the valve cavity 10b. The inner diameter of the valve port 11 is measured by selecting the inner diameter of the straight edge section 11a. That is, the valve port 11 is a channel for refrigerant to flow through, and the minimum inner diameter of this channel is the inner diameter of the valve port 11.

[0047] The technical solution of this utility model regulates the refrigerant flow rate through the cooperation of valve needle 30 and valve port 11. A Helmholtz resonator structure is formed through resonant cavity 10a and silencing channel 41, which converts the noise energy generated by high-speed fluid into heat energy, ultimately reducing the operating noise of the indoor unit of the air conditioner. The mounting base 40 is connected to the inner wall of valve body 10 through the periphery. The top, bottom of nut 21 and side wall of valve body 10 are sealed together to form a separation between resonant cavity 10a and valve cavity 10b. Liquid refrigerant enters valve cavity 10b from the opening 12 on the periphery of valve body 10. Valve needle 30 is driven downward by lead screw 22 to adjust the opening of bottom valve port 11. When the refrigerant is forced to pass through the narrow valve port 11, the flow rate increases sharply (producing a whistling sound similar to water flowing through a narrow water pipe). When high-pressure refrigerant enters resonant cavity 10a from valve cavity 10b through silencing channel 41, the flow rate decreases due to the sudden expansion of cross-sectional area (from hole to cavity). The pressure fluctuation is dispersed, and the sound waves are reflected multiple times in resonant cavity 10a and cancel each other out. In addition, the guide channel 42 works in conjunction with the valve needle 30 to suppress mechanical noise caused by the vibration of the valve needle 30.

[0048] Combination Figures 2 to 4Specifically, the mounting base 40 includes an annular base 40a and a journal 40b coaxially disposed with the annular base 40a in a direction away from the nut 21. The outer diameter of the journal 40b is smaller than the outer diameter of the annular base 40a, forming a stepped surface 40c. A noise-absorbing channel 41 is disposed on the stepped surface 40c, and a guide channel 42 passes through the annular base 40a and the journal 40b.

[0049] The annular base 40a is sealed to the inner wall of the valve body 10 to ensure the sealing of the resonant cavity 10a. The outer diameter of the journal 40b is smaller than the outer diameter of the annular base 40a, so that there is a gap between the journal 40b and the inner wall of the valve body 10 for the refrigerant to enter the resonant cavity 10a from the silencer channel 41. The gap is larger than the size of the step surface 40c.

[0050] Understandably, the aperture of the silencing channel 41 is smaller than that of the stepped surface 40c, and the silencing channel 41 is located near the outer wall of the journal 40b or at the center of the stepped surface 40c.

[0051] In one embodiment, the annular base 40a is tightly fitted to the inner wall of the valve body 10 by a seal.

[0052] In one embodiment, the annular base 40a is sealed to the inner wall of the valve body 10 by welding.

[0053] Specifically, the valve body 10 has a first mounting groove for mounting the nut 21 and a second mounting groove for mounting the annular base 40a. The inner diameter of the first mounting groove is larger than that of the second mounting groove, forming a stepped inner cavity in the axial direction of the valve body 10. The annular base 40a is mounted in the second mounting groove (with interference fit or welding). The nut 21 also has a guide section extending toward the annular base 40a. The outer wall of the valve needle 30 is clearance-fitted with the guide section, thereby forming a secondary guide with the guide channel 42 to suppress mechanical noise caused by the vibration of the valve needle 30.

[0054] In one embodiment, the guide segment abuts against the surface of the annular base 40a.

[0055] In one embodiment, there is a gap between the end of the guide section and the surface of the annular base 40a, and the outer wall of the valve needle 30 seals the gap.

[0056] Specifically, two silencing channels 41 are provided opposite to each other on the annular base 40a, and the center line connecting the two silencing channels 41 passes through the center of the annular base 40a.

[0057] An annular gap is formed between the journal 40b and the inner wall of the valve body 10. A connecting pipe is provided at the opening 12 on the periphery of the valve body 10. The refrigerant entering the valve cavity 10b through the connecting pipe will enter the silencing channel 41 through the gap. The silencing channel 41 and the resonant cavity 10a constitute a Helmholtz resonator, which is used to reduce the noise generated by the refrigerant flow. Multiple silencing channels 41 can provide a stronger silencing effect.

[0058] In this embodiment, two silencing channels 41 are provided at the annular base 40a. The center line connecting the two oppositely arranged silencing channels 41 passes through the center of the annular base 40a to ensure that the two silencing channels 41 are evenly distributed on the circumference, thereby producing a balanced effect when the fluid passes through, avoiding excessive local pressure or noise concentration. In addition, the symmetrical arrangement helps to improve the precision of manufacturing and assembly, ensuring that the position of each silencing channel 41 is accurate, thereby optimizing the silencing performance.

[0059] When some of the muffler channels 41 are partially blocked by impurities (such as carbonized particles in refrigeration oil), the remaining muffler channels 41 can still maintain their muffler function and avoid overall failure.

[0060] When the refrigerant passes through the silencing channel 41, it will exert a radial impact force on the annular base 40a. The symmetrical silencing channel 41 reduces the impact force of the refrigerant on the annular base 40a, and allows the sound wave to enter the resonant cavity 10a through the symmetrical channel, forming a standing wave interference in the cavity.

[0061] Combination Figure 1 and Figure 4 Specifically, the valve body 10 has an opening 12 on its circumference. The line connecting the centers of the two silencers 41 is parallel to the axis of the opening 12. The axis of the opening 12 refers to the centerline of the opening 12 (such as the refrigerant inlet) on the circumference of the valve body 10. The opening 12 is circular, and the axis (such as...) Figure 4 As shown, the line connecting the center of the two symmetrical silencing channels (perpendicular to the valve port axis) passes through the center of the annular base, forming a diameter symmetrical about the center. Thus, after the refrigerant enters the valve body 10 from the opening 12, the line connecting the silencing channels 41 is parallel to the axis of the opening 12 (rather than perpendicular or inclined), resulting in optimal flow path symmetry. This avoids abrupt changes in refrigerant flow direction, reducing pressure loss and improving energy efficiency. When sound waves enter from the opening 12, the parallel layout ensures that the sound wave path lengths of the two silencing channels 41 are consistent, enhancing the silencing effect and reducing noise.

[0062] In this embodiment, the silencing channel 41 has a waist-shaped orifice in cross-section. A waist-shaped orifice refers to an elliptical-like hole, wider in the middle and narrower at both ends. This shape helps guide fluid through more smoothly, reducing the generation of eddies and turbulence, thereby lowering noise. The wider middle section allows more fluid to pass through, while the narrower ends help maintain a stable flow rate. The waist-shaped orifice is also mechanically more robust, especially under pressure or vibration, preventing cracks or damage caused by stress concentration.

[0063] In a Helmholtz resonator, the geometry of the neck directly affects the resonant frequency and noise reduction effect. The waist-shaped aperture, through its unique shape, adjusts the propagation path of sound waves, enhancing sound energy dissipation and thus more effectively reducing noise at specific frequencies. Furthermore, waist-shaped apertures are easier to fabricate, especially when precise control of the aperture shape is required; their shape may be easier to process than complex polygons.

[0064] In other embodiments, the silencing channel 41 is shaped like a circular hole in cross-section.

[0065] Specifically, to reduce noise, the cross-sectional area of ​​any silencing channel 41 is larger than the area of ​​the valve port 11. The valve port 11 is the main throttling point, where the refrigerant velocity reaches its peak, causing severe turbulence and cavitation noise (the main noise source). If the cross-sectional area of ​​the silencing channel 41 is smaller than the area of ​​the valve port 11, the refrigerant will undergo secondary throttling at the silencing channel 41, and the velocity will increase again, leading to increased noise. To reduce noise, the volume of the resonant cavity 10a needs to be increased, which in turn increases the volume of the valve body 10.

[0066] Combination Figure 2 and Figure 3 To determine the areas of the silencer channel 41 and the valve port 11, the area of ​​the valve port 11 (e.g., the size of the opening 12 when the needle valve is fully open) can be determined based on the required cooling capacity of the air conditioner. Then, the silencer channel 41 is determined, typically with an area 1.2 to 2 times that of the valve port 11. Through simulated water flow and noise tests, the shape (e.g., oblong or round hole) and number of the silencer channel 41 are fine-tuned to ensure noise reduction without affecting cooling.

[0067] Specifically, the length of the silencing channel 41 is L, and the equivalent diameter of the silencing channel 41 is d, where L≥2d.

[0068] Specifically, the outer diameter of the annular base 40a is D, and L≤D / 4.

[0069] In fluid mechanics, the equivalent diameter is often used to convert rectangular or elliptical pipes into equivalent circular pipes to simplify calculations.

[0070] A Helmholtz resonator typically consists of a cavity and a neck, with the neck serving as the channel connecting the cavity to the external environment. When sound waves enter the neck, the air inside the cavity resonates due to pressure changes, thereby absorbing sound waves of specific frequencies and achieving a noise reduction effect. The noise reduction channel 41 (neck) and the resonant cavity 10a (cavity) are designed based on this principle.

[0071] The length and diameter of the neck affect the resonant frequency. If L is too short, the inertial mass required for resonance may not be effectively formed, or the sound waves may not reflect sufficiently within the channel, affecting the noise reduction effect. On the other hand, an excessively long length may increase flow resistance, affecting the flow of refrigerant and even leading to excessive pressure loss. Therefore, to ensure that the neck has sufficient length to maintain effective acoustic performance while avoiding the efficiency reduction caused by being too short, L ≥ 2d is set.

[0072] Furthermore, D is the outer diameter of the annular base 40a, which is the size of the cavity. If the neck is too long (relative to the cavity size), it may affect the resonance effect of the cavity or cause uneven distribution of sound waves within the cavity, reducing the noise reduction efficiency. Therefore, in order to maintain a reasonable ratio between the cavity and the neck and ensure the effectiveness of resonance, L ≤ D / 4 is set.

[0073] Specifically, d ≤ 0.2D, to ensure that the silencing channel 41 is narrow enough to generate sufficient resistance when the fluid passes through, thereby slowing down the flow rate and reducing turbulence and noise. At the same time, the narrow silencing channel 41 helps to form the Helmholtz resonance effect, because the neck of the resonator (i.e., the silencing channel 41) needs a certain degree of narrowness to enhance the reflection and cancellation of sound waves.

[0074] Specifically, 1 ≤ L / d ≤ 3, and this ratio controls the relationship between the channel's length and diameter. If L / d is too small, such as equal to 1, the channel is relatively short and wide; if it is equal to 3, it is relatively long and narrow. Choosing this range involves balancing acoustic performance and fluid dynamics. A short channel may not effectively create resonance, while a channel that is too long may increase flow resistance and affect the refrigerant flow rate. A middle ground needs to be found that effectively reduces noise without significantly impacting system efficiency.

[0075] Furthermore, if d is very small, more precise machining techniques are required, but the limitation of L / d balances the machining difficulty and performance requirements, facilitating manufacturing and ensuring that the channel is not too long, thus avoiding material waste and increased structural complexity. D, d, and L can be directly measured using calipers or micrometers, but if there is deformation or error, multiple measurements are required to obtain the average value (avoiding defective areas such as pits and weld points). If there is a defect on the end face, the maximum distance should be taken for curved or arc-shaped surfaces (multiple measurements should be taken to obtain the average value).

[0076] Specifically, the valve port 11 includes a straight edge section 11a that mates with the outer wall of the valve needle 30. The valve body 10 has a tapered flared section 11b at its bottom, extending away from the valve cavity 10b, which connects to the valve port 11. The tapered flared section 11b is located at the bottom of the valve body 10, extending away from the valve cavity 10b. Its inner wall is a gradually expanding cone shape (e.g., cone angle 15°–30°), and its end connects to the straight edge section 11a of the valve port 11. When the refrigerant flows out of the valve port 11, the tapered flared section 11b acts as a gradual expansion mechanism, allowing the fluid to transition smoothly, reducing sudden changes in flow velocity, and thus reducing turbulence and pressure drop. This not only improves energy efficiency but also reduces noise.

[0077] Electronic expansion valves offer higher control precision and faster response times, making them suitable for refrigeration systems requiring precise temperature control or variable load operation.

[0078] 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.

[0079] 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.

[0080] Combined with reference Figure 5 The table below shows the noise levels of electronic expansion valves with and without mounting bases forming a silencing channel and resonance cavity at different valve openings.

[0081]

[0082] Through tables and Figure 5 The noise levels can be clearly compared under different valve opening degrees. By setting up a mounting base to form a silencing channel and resonance cavity, the noise of the refrigerant in the valve cavity is controlled compared to the existing solution (without a mounting base structure).

[0083] Reference Figure 6 In the figure, the vertical axis represents the numerical value of noise intensity, and the height of the bar reflects the noise intensity at the corresponding frequency for electronic expansion valves with mounting bases (white) or without mounting bases (blue). The higher the value, the louder the noise.

[0084] The horizontal axis of the graph represents noise frequency in Hertz (Hz), ranging from 25 Hz to 20000 Hz. These values ​​represent the center frequencies of different frequency bands (e.g., 25 Hz is low frequency, 20000 Hz is high frequency), used to analyze noise characteristics across the entire frequency range (from low to high frequency). The values ​​below the horizontal axis correspond to the scores for each frequency band (each bar chart), i.e., the units of noise optimization. Negative values ​​indicate the optimization effect of electronic expansion valves with mounting bases (white); positive values ​​indicate the degree of deterioration. For example, at 80 Hz, the electronic expansion valve with a mounting base (white) shows a noise optimization of 10.3 units compared to the electronic expansion valve without a mounting base (blue), meaning that at 80 Hz, the noise is improved compared to the electronic expansion valve without a mounting base.

[0085] Combining the noise level and positive / negative values, it can be seen that the low-frequency range of the electronic expansion valve (this product) with a mounting base structure is significantly improved. Although the high-frequency range deteriorates, its contribution to the overall noise is relatively low, so the total noise level can be significantly reduced.

[0086] 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: The valve body has a valve port; The transmission assembly includes a nut and a lead screw, wherein the nut is sealed to the valve body and the lead screw is threadedly engaged with the nut; A valve needle, connected to the lead screw, is axially movable to open or close the valve port; and The mounting base has a periphery that is sealed to the inner wall of the valve body. A resonant cavity is defined between the mounting base and the nut. A valve cavity communicating with the valve port is defined between the valve body and the mounting base. The mounting base has a guide channel coaxially arranged with the nut. The valve needle passes through the guide channel and is clearance-fitted with the guide channel. The mounting base also has a noise-absorbing channel communicating with the resonant cavity and the valve cavity.

2. The electronic expansion valve as described in claim 1, characterized in that, The mounting base includes an annular base and a journal coaxially disposed with the annular base in a direction away from the nut. The outer diameter of the journal is smaller than the outer diameter of the annular base, forming a stepped surface. The noise-absorbing channel is disposed on the stepped surface, and the guide channel passes through the annular base and the journal.

3. The electronic expansion valve as described in claim 2, characterized in that, The noise reduction channels are provided opposite to each other on the annular base, and the line connecting the centers of the two oppositely provided noise reduction channels passes through the center of the annular base.

4. The electronic expansion valve as described in claim 3, characterized in that, The valve body has an opening on its periphery for installing a refrigerant connection pipe, and the line connecting the centers of the two silencer channels is parallel to the axis of the opening.

5. The electronic expansion valve as described in claim 2, characterized in that, The silencing channel has a cross-sectional shape of either an oblong or round hole.

6. The electronic expansion valve as described in claim 2, characterized in that, The cross-sectional area of ​​any one of the silencing channels is greater than the minimum area of ​​the valve port.

7. The electronic expansion valve as described in claim 2, characterized in that, The length of the silencing channel is L, and the equivalent diameter of the silencing channel is d, where L≥2d.

8. The electronic expansion valve as described in claim 7, characterized in that, The outer diameter of the annular base is D, and L ≤ D / 4.

9. The electronic expansion valve as described in claim 8, characterized in that, d≤0.2D, 1≤L / d≤3.

10. The electronic expansion valve as claimed in claim 1, characterized in that, The valve port includes a straight edge section that mates with the outer wall of the valve needle and a tapered flared section disposed away from the valve cavity.

11. A refrigeration device, characterized in that, Includes the electronic expansion valve as described in any one of claims 1 to 10.

Images