A multi-stage throttling noise reduction device for a electronic expansion valve

Abstract

The application discloses a same-flow multi-stage throttling noise reduction device of an electronic expansion valve, and relates to the technical field of air conditioner vibration reduction and noise reduction, comprising a reversing device, a capillary tube group and an electronic expansion valve, wherein the reversing device is connected with the electronic expansion valve through the capillary tube group; the capillary tube group is formed by connecting a plurality of capillary tubes with different lengths in parallel; and the reversing device guides the refrigerant to flow into the capillary tubes with different lengths according to the pressure of the refrigerant at the inlet. The application first depressurizes the refrigerant to a certain extent before ensuring that the refrigerant always flows into the electronic expansion valve from the direction perpendicular to the valve needle, reduces the refrigerant pressure entering the electronic expansion valve, and significantly reduces the cavitation noise of the refrigerant.

Description

Technical Field

[0001] This invention relates to the field of air conditioning vibration reduction and noise reduction technology, and in particular to a multi-stage throttling and noise reduction device for an electronic expansion valve with the same flow direction. Background Technology

[0002] Electronic expansion valves are a common type of throttling device in air conditioning systems. They rely on the movement of a valve needle to control the area of ​​the throttling channel, thereby regulating the refrigerant flow. The process of refrigerant flowing through the electronic expansion valve during throttling generates flow-induced noise, causing user dissatisfaction and potentially leading to complaints in severe cases.

[0003] The flow-induced noise of electronic expansion valves is mainly caused by two factors: first, vibration noise caused by the high-speed refrigerant impacting the valve needle and resulting in vibration; second, cavitation noise caused by the drastic changes in refrigerant pressure during throttling and cavitation. Vibration noise occurs when refrigerant flows in along the end pipe coaxial with the valve needle and flows out along the end pipe perpendicular to the valve needle; in this case, the high-speed refrigerant directly impacts the end face of the valve needle, causing it to vibrate and radiate noise. Cavitation noise typically occurs when the inlet refrigerant pressure is relatively high; in this case, the pressure drop of the refrigerant during throttling is large, causing a violent process of cavitation bubble growth and collapse, which also radiates noise.

[0004] To address the vibration noise caused by the high-speed refrigerant impacting the valve needle, existing noise reduction technologies ensure that the refrigerant always flows into the electronic expansion valve from the end pipe perpendicular to the valve needle axis, thereby preventing the refrigerant from directly impacting the conical surface of the valve needle. For example, Chinese patent CN101210752A (published July 2, 2008) discloses an electronic expansion valve throttling device. This device uses four one-way valves in the pipe assembly containing the electronic expansion valve. Two of these one-way valves are connected in series with the electronic expansion valve and align with its forward flow direction, while the other two are connected in parallel with the electronic expansion valve and align with its reverse flow direction. This ensures that the electronic expansion valve guides the refrigerant to flow into the electronic expansion valve from the end pipe perpendicular to the valve needle axis, regardless of whether it is in cooling or heating mode. For example, Chinese patent CN110836549A (published on February 25, 2020) discloses an electronic expansion valve device, a heat pump system, and an air conditioning system. By adding a reversing device with four ports to both ends of the electronic expansion valve, the refrigerant flowing through the electronic expansion valve can always maintain a unidirectional flow regardless of the direction of inflow or outflow. However, existing noise reduction technologies cannot effectively address the cavitation noise generated by the large refrigerant pressure drop during throttling.

[0005] Therefore, those skilled in the art are dedicated to developing a co-current multi-stage throttling noise reduction device for electronic expansion valves, which can solve both the vibration noise problem and the cavitation noise problem of electronic expansion valves. Summary of the Invention

[0006] In view of the above-mentioned deficiencies of the prior art, the technical problem to be solved by the present invention is how to reduce the flow-induced noise of the electronic expansion valve in the air conditioning system.

[0007] To achieve the above objectives, the present invention provides a multi-stage throttling and noise reduction device for an electronic expansion valve, characterized in that it includes a reversing device, a capillary tube assembly, and an electronic expansion valve, wherein the reversing device is connected to the electronic expansion valve through the capillary tube assembly, the capillary tube assembly is composed of multiple capillary tubes of different lengths connected in parallel, and the reversing device guides the refrigerant into the capillary tubes of different lengths based on the pressure of the refrigerant at the inlet.

[0008] Furthermore, the reversing device includes a cylinder, a spring, and a piston. The piston and the spring are disposed inside the cylinder. The spring is placed vertically, and the piston is fixedly connected to the cylinder through the spring.

[0009] Furthermore, the reversing device also includes a first positioning ring and a second positioning ring. The first positioning ring is fixed on the side near the top of the cylinder body, and the second positioning ring is fixed on the side near the bottom of the cylinder body. The piston is disposed between the first positioning ring and the second positioning ring.

[0010] Furthermore, the cylinder body has an inlet hole at the bottom and an outlet hole group on the side of the cylinder body that is connected to the capillary group. The outlet hole group includes multiple outlet holes, and the multiple outlet holes are respectively connected to capillary tubes of different lengths.

[0011] Furthermore, a circular flow passage is provided at the bottom end of the piston, and a horn-shaped flow passage is provided on the side of the piston. The horn-shaped flow passage faces the outlet hole group, and the circular flow passage and the horn-shaped flow passage are interconnected.

[0012] Furthermore, the capillary assembly also includes a connecting pipe, the reversing device is connected to the electronic expansion valve through the connecting pipe, the connecting pipe is connected to the outlet hole near the inlet hole, and the connecting pipe is provided with a connecting pipe check valve, which ensures that the refrigerant can only flow from the reversing device to the electronic expansion valve.

[0013] Furthermore, the capillary tube becomes shorter the closer it is to the inlet orifice.

[0014] Furthermore, the capillary assembly also includes multiple one-way valves, with each capillary connected in series with one of the one-way valves, which ensure that the refrigerant can only flow from the reversing device to the electronic expansion valve.

[0015] Furthermore, the reversing device includes an outdoor reversing device and an indoor reversing device, the capillary assembly includes an outdoor capillary assembly and an indoor capillary assembly, the outdoor reversing device is connected to the outdoor unit of the air conditioner and the outdoor capillary assembly, the indoor reversing device is connected to the indoor unit of the air conditioner and the indoor capillary assembly, the outdoor capillary assembly and the indoor capillary assembly are simultaneously connected to the inlet horizontal pipe of the electronic expansion valve, and the outdoor unit of the air conditioner and the indoor unit of the air conditioner are connected to the compressor.

[0016] Furthermore, it also includes a first outlet check valve and a second outlet check valve. The electronic expansion valve is connected to the outdoor reversing device and the outdoor unit of the air conditioner through the first outlet check valve. The first outlet check valve allows the refrigerant to flow only from the electronic expansion valve to the outdoor reversing device and the outdoor unit of the air conditioner. The electronic expansion valve is connected to the indoor reversing device and the indoor unit of the air conditioner through the second outlet check valve. The second outlet check valve allows the refrigerant to flow only from the electronic expansion valve to the indoor reversing device and the indoor unit of the air conditioner.

[0017] Existing technologies only address valve needle vibration noise by ensuring refrigerant always flows into the electronic expansion valve from a direction perpendicular to the valve needle. However, they fail to solve the cavitation noise problem caused by excessive refrigerant pressure flowing into the electronic expansion valve. This invention connects a set of capillary tubes of varying lengths to the inlet of the electronic expansion valve. By judging the inlet refrigerant pressure, the refrigerant is guided into the capillary tubes of specific lengths for depressurization. The depressurized refrigerant is then guided into the electronic expansion valve. Before ensuring the refrigerant always flows into the electronic expansion valve from a direction perpendicular to the valve needle, the refrigerant is depressurized to a certain extent, reducing the refrigerant pressure entering the electronic expansion valve and significantly reducing refrigerant cavitation noise.

[0018] Currently, there is no specific method in the technology to guide refrigerant into a capillary tube of a specific length by judging the pressure of the inlet refrigerant. This invention designs a reversing device with a built-in spring and piston. After the refrigerant at a certain pressure enters the reversing device, the balance between the inlet refrigerant pressure and the spring force pushes the piston to move, causing the spring connected to the piston to compress (or stretch) by a certain length. This causes the flow orifice inside the piston to connect with the outlet orifice at a specific location, thereby guiding the refrigerant into the capillary tube of a specific length.

[0019] In existing technologies, the main solution to ensure that refrigerant always flows into the electronic expansion valve from the same direction is through a four-way directional valve. This requires a corresponding electronic control system, which has poor reliability and high cost. This invention utilizes a series-parallel combination of several one-way valves and an electronic expansion valve to achieve refrigerant flow in the same direction. The electronic expansion valve is connected in series with two one-way valves in the same direction, and then in parallel with two more one-way valves in the opposite direction. This ensures that the refrigerant flows in the same direction through the electronic expansion valve, whether in cooling or heating mode.

[0020] The present invention has at least the following beneficial technical effects:

[0021] 1. By ensuring that the refrigerant always flows into the electronic expansion valve from a direction perpendicular to the valve needle, the problem of valve needle vibration noise is solved. At the same time, the refrigerant pressure entering the electronic expansion valve is reduced, which can significantly reduce the cavitation noise of the refrigerant.

[0022] 2. No pressure sensor is needed to determine the refrigerant inlet pressure, the control method is simple and reliable, and the cost is low.

[0023] 3. By using a series and parallel combination of several one-way valves and electronic expansion valves, the refrigerant can flow in the same direction. No electrical control is required, the system is stable, and the cost is low.

[0024] The following will further explain the concept, specific structure, and technical effects of the present invention in conjunction with the accompanying drawings, so as to fully understand the purpose, features, and effects of the present invention. Attached Figure Description

[0025] Figure 1 This is a schematic diagram of the overall structure of a multi-stage throttling and noise reduction device for an electronic expansion valve according to a preferred embodiment of the present invention.

[0026] Figure 2 This is a dimensional diagram of the reversing device of a multi-stage throttling and noise reduction device for an electronic expansion valve according to a preferred embodiment of the present invention.

[0027] Figure 3 A schematic diagram of refrigerant flow in the first refrigeration mode of a multi-stage throttling and noise reduction device with an electronic expansion valve according to a preferred embodiment of the present invention.

[0028] Figure 4 A schematic diagram of refrigerant flow in a second refrigeration mode for a co-current multi-stage throttling and noise reduction device for an electronic expansion valve, according to a preferred embodiment of the present invention.

[0029] Figure 5 This is a schematic diagram of refrigerant flow in the third refrigeration mode of a multi-stage throttling and noise reduction device with an electronic expansion valve according to a preferred embodiment of the present invention.

[0030] Figure 6 This is a schematic diagram of refrigerant flow in the first heating mode of a multi-stage throttling and noise reduction device for an electronic expansion valve according to a preferred embodiment of the present invention.

[0031] Figure 7 A schematic diagram of refrigerant flow in the second heating mode of a multi-stage throttling and noise reduction device for an electronic expansion valve according to a preferred embodiment of the present invention.

[0032] Figure 8 This is a schematic diagram of refrigerant flow in the third heating mode of a multi-stage throttling and noise reduction device with an electronic expansion valve according to a preferred embodiment of the present invention.

[0033] Figure 9 A comparison diagram of the noise reduction effect of a co-flow direction multi-stage throttling device for an electronic expansion valve, according to a preferred embodiment of the present invention, in refrigeration mode with a conventional structure.

[0034] Figure 10 A comparison diagram of the noise reduction effect of a co-current multi-stage throttling device for an electronic expansion valve, according to a preferred embodiment of the present invention, in heating mode, compared with that of a conventional structure.

[0035] Figure 11 This is a schematic diagram of the overall structure of a co-current multi-stage throttling and noise reduction device for an electronic expansion valve, according to a second preferred embodiment of the present invention.

[0036] Figure 12 This is a dimensional diagram of the commutation device of a multi-stage throttling and noise reduction device for an electronic expansion valve according to a second preferred embodiment of the present invention.

[0037] Figure 13 This is a schematic diagram of refrigerant flow in refrigeration mode of a co-current multi-stage throttling and noise reduction device for an electronic expansion valve, which is a second preferred embodiment of the present invention.

[0038] Figure 14 This is a schematic diagram of refrigerant flow in heating mode of a co-current multi-stage throttling and noise reduction device for an electronic expansion valve, which is a second preferred embodiment of the present invention.

[0039] Figure 15 This is a schematic diagram of the overall structure of a multi-stage throttling and noise reduction device for an electronic expansion valve in the same direction of flow, which is a third preferred embodiment of the present invention.

[0040] Figure 16 A dimensional diagram of the commutation device of a multi-stage throttling and noise reduction device for an electronic expansion valve according to a third preferred embodiment of the present invention;

[0041] Figure 17This is a schematic diagram of refrigerant flow in refrigeration mode of a multi-stage throttling and noise reduction device with an electronic expansion valve according to a third preferred embodiment of the present invention.

[0042] Figure 18 This is a schematic diagram of refrigerant flow in heating mode of a multi-stage throttling and noise reduction device with an electronic expansion valve according to a third preferred embodiment of the present invention.

[0043] Wherein, 1-Outdoor side reversing device; 101-Outdoor side cylinder; 102-Outdoor side first positioning ring; 103-Outdoor side spring; 104-Outdoor side piston; 105-Outdoor side circular flow hole; 106-Outdoor side second positioning ring; 107-Outdoor side inlet hole; 108-Outdoor side outlet hole group; 1080-Outdoor side connecting pipe outlet hole; 1081-Outdoor side first outlet hole; 1082-Outdoor side second outlet hole; 1083-Outdoor side third outlet hole; 1084-Outdoor side fourth outlet hole; 1085-Outdoor side fifth outlet hole; 109-Outdoor side horn-shaped flow passage; 2-Outdoor side capillary assembly; 201-Outdoor side first capillary; 202-Outdoor side second capillary; 203-Outdoor side third capillary; 204-Outdoor side fourth capillary; 205-Outdoor side fifth capillary; 3-Outdoor side check valve assembly; 301-Outdoor side first check valve; 302-Outdoor side second check valve; 303-Outdoor side third check valve; 304-Outdoor side fourth check valve; 305-Outdoor side fifth check valve; 300-Outdoor side connecting pipe check valve; 4-Indoor side reversing device; 40 1-Indoor cylinder block; 402-Indoor first positioning ring; 403-Indoor spring; 404-Indoor piston; 405-Indoor circular flow hole; 406-Indoor second positioning ring; 407-Indoor inlet hole; 408-Indoor outlet hole group; 4080-Indoor connecting pipe outlet hole; 4081-Indoor first outlet hole; 4082-Indoor second outlet hole; 4083-Indoor third outlet hole; 4084-Indoor fourth outlet hole; 4085-Indoor fifth outlet hole; 409-Indoor trumpet-shaped flow hole; 5 - Indoor capillary assembly; 501- Indoor first capillary; 502- Indoor second capillary; 503- Indoor third capillary; 504- Indoor fourth capillary; 505- Indoor fifth capillary; 6- Indoor check valve assembly; 601- Indoor first check valve; 602- Indoor second check valve; 603- Indoor third check valve; 604- Indoor fourth check valve; 605- Indoor fifth check valve; 600- Indoor connecting pipe check valve; 7- Electronic expansion valve; 8- First outlet check valve; 9- Second outlet check valve. Detailed Implementation

[0044] The following description, with reference to the accompanying drawings, illustrates several preferred embodiments of the present invention to make its technical content clearer and easier to understand. The present invention can be embodied in many different forms, and the scope of protection of the present invention is not limited to the embodiments mentioned herein.

[0045] In the accompanying drawings, components with the same structure are indicated by the same numerical designation, and components with similar structures or functions are indicated by similar numerical designations. The dimensions and thicknesses of each component shown in the drawings are arbitrary, and the present invention does not limit the dimensions and thicknesses of each component. To make the illustrations clearer, the thickness of some components has been appropriately exaggerated in the drawings.

[0046] like Figure 1 As shown, in a preferred embodiment of the present invention, a multi-stage throttling and noise reduction device for an electronic expansion valve in the same flow direction includes: an outdoor-side reversing device 1, an outdoor-side cylinder 101, an outdoor-side first positioning ring 102, an outdoor-side spring 103, an outdoor-side piston 104, an outdoor-side circular flow passage 105, an outdoor-side second positioning ring 106, an outdoor-side inlet hole 107, an outdoor-side outlet hole group 108, an outdoor-side horn-shaped flow passage 109, an outdoor-side capillary group 2, and an outdoor-side... 3. Side check valve assembly, 4. Indoor side reversing device, 401. Indoor side cylinder, 402. Indoor side first positioning ring, 403. Indoor side spring, 404. Indoor side piston, 405. Indoor side circular flow hole, 406. Indoor side second positioning ring, 407. Indoor side inlet hole, 408. Indoor side outlet hole assembly, 409. Indoor side horn-shaped flow hole, 5. Indoor side capillary assembly, 6. Indoor side check valve assembly, 7. Electronic expansion valve, 8. First outlet check valve, 9. Second outlet check valve.

[0047] The outdoor reversing device 1 includes an outdoor cylinder 101, an outdoor first positioning ring 102, an outdoor spring 103, an outdoor piston 104, and an outdoor second positioning ring 106. The outdoor cylinder 101 has an outdoor inlet hole 107 at its bottom and an outdoor outlet hole group 108 on its side. The first positioning ring 102 on the outdoor side is fixed near the top of the outdoor cylinder 101, and the second positioning ring 106 on the outdoor side is fixed near the bottom of the outdoor cylinder 101. The outdoor piston 104 is placed between the first positioning ring 102 and the second positioning ring 106 on the outdoor side. The bottom end of the outdoor piston 104 has an outdoor circular flow hole 105, and the side of the outdoor piston 104 has an outdoor horn-shaped flow hole 109, and the outdoor circular flow hole 105 and the outdoor horn-shaped flow hole 109 are interconnected. The outdoor spring 103 is placed vertically, and the upper part of the outdoor spring 103 is fixedly connected to the center of the top of the outdoor cylinder 101, and the lower part is fixedly connected to the center of the top of the outdoor piston 104.

[0048] The outdoor capillary assembly 2 consists of three capillary tubes of different lengths connected in parallel. Each capillary tube is connected to an outlet hole on the side of the outdoor cylinder 101 in the outdoor reversing device 1. The capillary tubes closer to the outdoor inlet hole 107 are shorter. A connecting pipe outlet hole is provided on the side of the outdoor cylinder 101 near the outdoor inlet hole 107. The connecting pipe is connected to the connecting pipe outlet hole and the electronic expansion valve 7. The connecting pipe does not have a capillary tube, but it is equipped with a connecting pipe check valve.

[0049] The outdoor one-way valve group 3 consists of 4 one-way valves connected in parallel. Among them, 3 one-way valves are connected in series with each capillary tube of the outdoor capillary tube group 2, and 1 one-way valve is connected to the outdoor connecting pipe outlet hole 1080 of the outdoor reversing device 1. The flow direction of each one-way valve is consistent, and the refrigerant can only flow from the outdoor capillary tube to the outdoor one-way valve (i.e. from the outdoor first capillary tube 201 to the outdoor first one-way valve 301, from the outdoor second capillary tube 202 to the outdoor second one-way valve 302, and from the outdoor third capillary tube 203 to the outdoor third one-way valve 303).

[0050] The indoor reversing device 4 has the same structure as the outdoor reversing device 1, and the orientation of the indoor outlet hole group 408 and the indoor horn-shaped flow hole 409 of the indoor reversing device 4 is opposite to that of the outdoor outlet hole group 108 and the outdoor horn-shaped flow hole 109 of the outdoor reversing device 1; the indoor capillary group 5 is composed of three capillary tubes of different lengths connected in parallel, and each capillary tube is connected to each outlet hole on the side of the indoor cylinder 401 in the indoor reversing device 4.

[0051] The indoor one-way valve group 6 is also composed of 4 one-way valves connected in parallel. Among them, 3 one-way valves are connected in series with each capillary of the indoor capillary group 5, and 1 one-way valve is connected to the indoor connecting pipe outlet hole 4080 of the indoor reversing device 4. The flow direction of each one-way valve is consistent, and the refrigerant can only flow from the indoor capillary to the indoor one-way valve (i.e. from the indoor first capillary 501 to the indoor first one-way valve 601, from the indoor second capillary 502 to the indoor second one-way valve 602, and from the indoor third capillary 503 to the indoor third one-way valve 603).

[0052] The inlet horizontal pipe of the electronic expansion valve 7 is connected to both the outdoor one-way valve group 3 and the indoor one-way valve group 6. The outlet vertical pipe of the electronic expansion valve 7 is connected to both the first outlet one-way valve 8 and the second outlet one-way valve 9. After the first outlet one-way valve 8 is connected in parallel with the outdoor unit, it is connected to the outdoor inlet hole 107 at the bottom of the outdoor cylinder 101 of the outdoor reversing device 1. The flow direction of the first outlet one-way valve 8 ensures that the refrigerant can only flow from the outlet vertical pipe of the electronic expansion valve 7 through the first outlet one-way valve 8 to the outdoor unit. After the second outlet one-way valve 9 is connected in parallel with the indoor unit, it is connected to the inlet hole 407 at the bottom of the indoor cylinder 401 of the indoor reversing device 4. The flow direction of the second outlet one-way valve 9 ensures that the refrigerant can only flow from the outlet vertical pipe of the electronic expansion valve 7 through the second outlet one-way valve to the indoor unit.

[0053] like Figure 2 As shown, in the outdoor reversing device 1 and the indoor reversing device 4, the relationship between the cylinder height L, the spring natural length L1, the piston length L4, and the distance between the piston bottom surface and the cylinder bottom surface L6 is L > L1 + L4 + L6; the relationship between the cylinder inner diameter D, the inner diameter d3 of the first positioning ring and the second positioning ring, and the diameter d2 of the inlet hole and the circular flow hole is D > d3 > d2.

[0054] Inside the outdoor reversing device 1 and the indoor reversing device 4, the relationship between the height L2 of the distance between the bottom of the first positioning ring and the upper wall of the cylinder and the thickness h of the first positioning ring is: L2 > h; the relationship between the distance l of the center of the uppermost outlet hole from the upper wall of the cylinder, the radius d1 of the outlet hole, the height L2 of the distance between the bottom of the first positioning ring and the upper wall of the cylinder, the piston height L4, the depth L5 of the circular flow hole, and the diameter d4 of the large end of the horn-shaped flow hole is: l > L2 + L4 - L5 + d4 / 2 - d1 / 2; the relationship between the variable length L3 of the spring and the distance h of the distance between the center of the uppermost outlet hole and the upper wall of the cylinder is: l > L2 + L4 - L5 + d4 / 2 - d1 / 2; The relationship between the distance l, the outlet orifice diameter d1, and the outlet orifice spacing l0 is: L3≥l+5d1 / 2+l0; the relationship between the outlet orifice diameter d1, the outlet orifice spacing l0, and the large end diameter d4 of the horn-shaped flow orifice is: d4=d1+l0; the relationship between the variable length of the spring L3 and the piston height L4 is: L4≥L3; the relationship between the piston height L4, the circular flow orifice depth L5, and the large end diameter d4 of the horn-shaped flow orifice is: L4>L5+d4 / 2; the relationship between the distance L6 between the top of the first positioning ring and the upper wall of the cylinder body and the thickness h of the first positioning ring is: L6>h.

[0055] like Figure 3The diagram shows the refrigerant flow in the system under the first cooling mode in this example. The dashed arrows indicate the refrigerant flow process, and the refrigerant inlet pressure is relatively low at this time. Specifically, the low-pressure refrigerant enters the outdoor unit through the outdoor inlet hole 107 and fills the lower part of the outdoor cylinder 101, pushing the outdoor piston 104 upwards and compressing the outdoor spring 103. This causes the outdoor flared flow hole 109 to connect with the outdoor third outlet hole 1083, at which point the outdoor piston 104 is in a lower position. After flowing through the outdoor circular flow hole 105 and the outdoor flared flow hole 109, the low-pressure refrigerant enters the outdoor third capillary tube 203, achieving a pressure drop, then passes through the outdoor third check valve 303, enters the electronic expansion valve 7 for throttling, and then enters the indoor unit through the second outlet check valve 9. After being pressurized by the compressor, it enters the outdoor unit, completing one cooling cycle. After the refrigerant flows out of the electronic expansion valve 7, it does not pass through the first outlet check valve 8 to enter the outdoor unit because the pressure at the outdoor unit outlet is higher than the outlet pressure of the electronic expansion valve 7. Similarly, after the refrigerant flows through the second outlet check valve 9, it does not enter the indoor reversing device 4 because the inlet pressure of the electronic expansion valve 7 is higher than the inlet pressure of the indoor reversing device 4.

[0056] like Figure 4 The diagram shows the refrigerant flow in the system under the second cooling mode in this example, where the refrigerant inlet pressure is at a medium pressure level. Specifically, the medium-pressure refrigerant enters the outdoor unit through the outdoor inlet hole 107 and fills the lower part of the outdoor cylinder 101, pushing the outdoor piston 104 upwards and compressing the outdoor spring 103. This causes the outdoor flared orifice 109 to connect with the outdoor second outlet hole 1082, at which point the outdoor piston 104 is in the middle position. After flowing through the outdoor circular orifice 105 and the outdoor flared orifice 109, the medium-pressure refrigerant enters the outdoor second capillary tube 202, achieving a pressure drop, then passes through the outdoor second check valve 302, enters the electronic expansion valve 7 for throttling, and then enters the indoor unit through the second outlet check valve 9. After being pressurized by the compressor, it enters the outdoor unit, completing one cooling cycle. The refrigerant does not enter the outdoor unit through the first outlet check valve 8 after exiting the electronic expansion valve 7 because the pressure at the outdoor unit outlet is higher than the outlet pressure of the electronic expansion valve 7. Meanwhile, the refrigerant will not enter the indoor reversing device 4 after flowing through the second outlet check valve 9 because the inlet pressure of the electronic expansion valve 7 is higher than the inlet pressure of the indoor reversing device 4.

[0057] like Figure 5The diagram shows the refrigerant flow in the system under the third cooling mode in this example. At this time, the refrigerant inlet pressure is at a high pressure level. Specifically, the high-pressure refrigerant enters the outdoor unit through the outdoor inlet hole 107 and fills the lower part of the outdoor cylinder 101, pushing the outdoor piston 104 upwards and compressing the outdoor spring 103. This causes the outdoor flared orifice 109 to connect with the outdoor first outlet hole 1081, at which point the outdoor piston 104 is in the high position. After flowing through the outdoor circular orifice 105 and the outdoor flared orifice 109, the high-pressure refrigerant enters the outdoor first capillary tube 201, achieving a pressure drop. It then passes through the outdoor first check valve 301, enters the electronic expansion valve 7 for throttling, and then passes through the second outlet check valve 9 to enter the indoor unit. After being pressurized by the compressor, it enters the outdoor unit, completing one cooling cycle. The refrigerant does not pass through the first outlet check valve 8 after exiting the electronic expansion valve 7 because the pressure at the outdoor unit outlet is higher than the outlet pressure of the electronic expansion valve 7. Meanwhile, the refrigerant will not enter the indoor reversing device 4 after flowing through the second outlet check valve 9 because the inlet pressure of the electronic expansion valve 7 is higher than the inlet pressure of the indoor reversing device 4.

[0058] like Figure 6 The diagram shows the refrigerant flow in the system during the first heating mode in this example, where the refrigerant inlet pressure is low. Specifically, the low-pressure refrigerant enters the indoor unit through the indoor inlet port 407 and fills the lower part of the indoor cylinder 401, pushing the indoor piston 404 upwards and compressing the indoor spring 403. This causes the indoor flared orifice 409 to connect with the indoor third outlet port 4083, at which point the indoor piston 404 is in a lower position. After flowing through the indoor circular orifice 405 and the indoor flared orifice 409, the low-pressure refrigerant enters the indoor third capillary tube 503, achieving a pressure drop, then passes through the indoor third check valve 603, enters the electronic expansion valve 7 for throttling, and then passes through the first outlet check valve 8 to enter the outdoor unit. After being pressurized by the compressor, it enters the indoor unit, completing one heating cycle. The refrigerant does not enter the indoor unit through the second outlet check valve 9 after exiting the electronic expansion valve 7 because the outlet pressure of the indoor unit is higher than the outlet pressure of the electronic expansion valve 7. Meanwhile, the refrigerant will not enter the outdoor reversing device 1 after flowing through the first outlet check valve 8 because the inlet pressure of the electronic expansion valve 7 is higher than the inlet pressure of the outdoor reversing device 1.

[0059] like Figure 7The diagram shows the refrigerant flow in the system during the second heating mode in this example. The refrigerant inlet pressure is at a medium pressure level. Specifically, the medium-pressure refrigerant enters the indoor unit through the indoor inlet hole 407 and fills the lower part of the indoor cylinder 401, pushing the indoor piston 404 upwards and compressing the indoor spring 403. This causes the indoor flared orifice 409 to connect with the indoor second outlet hole 4082, at which point the indoor piston 404 is in the middle position. After flowing through the indoor circular orifice 405 and the indoor flared orifice 409, the medium-pressure refrigerant enters the indoor second capillary tube 502, achieving a pressure drop. It then passes through the indoor second check valve 602, enters the electronic expansion valve 7 for throttling, and then passes through the first outlet check valve 8 to enter the outdoor unit. After being pressurized by the compressor, it enters the indoor unit, completing one heating cycle. The refrigerant does not pass through the second outlet check valve 9 to enter the indoor unit after flowing out of the electronic expansion valve 7 because the outlet pressure of the indoor unit is higher than the outlet pressure of the electronic expansion valve 7. Similarly, the refrigerant does not enter the outdoor reversing device 1 after flowing through the first outlet check valve 8 because the inlet pressure of the electronic expansion valve 7 is higher than the inlet pressure of the outdoor reversing device 1.

[0060] like Figure 8 The diagram shows the refrigerant flow in the system during the third heating mode in this example. The refrigerant inlet pressure is at a high pressure level. Specifically, the high-pressure refrigerant enters the indoor unit through the indoor inlet port 407 and fills the lower part of the indoor cylinder 401, pushing the indoor piston 404 upwards and compressing the indoor spring 403. This causes the indoor flared orifice 409 to connect with the indoor first outlet port 4081, placing the indoor piston 404 at its highest position. After flowing through the indoor circular orifice 405 and the indoor flared orifice 409, the high-pressure refrigerant enters the indoor first capillary tube 501, achieving a pressure drop. It then passes through the indoor first check valve 601, enters the electronic expansion valve 7 for throttling, and then through the first outlet check valve 8 into the outdoor unit. After being pressurized by the compressor, it enters the indoor unit, completing one heating cycle. The refrigerant does not enter the indoor unit through the second outlet check valve 9 after exiting the electronic expansion valve 7 because the outlet pressure of the indoor unit is higher than the outlet pressure of the electronic expansion valve 7. Meanwhile, the refrigerant will not enter the outdoor reversing device 1 after flowing through the first outlet check valve 8 because the inlet pressure of the electronic expansion valve 7 is higher than the inlet pressure of the outdoor reversing device 1.

[0061] like Figure 9As shown, in cooling mode, the simulated noise values ​​near the electronic expansion valve of the present invention example and the original scheme (only electronic expansion valve, no capillary tube, reversing device, or check valve) are compared at different electronic expansion valve inlet pressures (outlet pressure is 1 MPa). It can be seen that when the inlet pressure is 2 MPa, 2.5 MPa, and 3 MPa, the noise value of the present invention example is lower than that of the traditional scheme.

[0062] like Figure 10 As shown, in heating mode, the simulated noise values ​​near the electronic expansion valve of the present invention example and the original scheme (only electronic expansion valve, no capillary tube, reversing device, or check valve) are compared at different electronic expansion valve inlet pressures (outlet pressure is 0.8 MPa). It can be seen that when the inlet pressure is 2 MPa, 2.5 MPa, and 3 MPa, the noise value of the present invention example is lower than that of the traditional scheme.

[0063] Example 2

[0064] like Figure 11 The diagram shows the overall structure of the second preferred embodiment of the present invention, with the same names for each number as in the first embodiment. The difference from the first embodiment is that the spring is installed between the piston bottom surface of the reversing device and the lower inner wall surface of the cylinder. Figure 12 A dimensional diagram of the outdoor reversing device of the second embodiment is provided. The relationship between the natural length L1 of the spring and the distance L6 from the upper end face of the second positioning ring to the lower inner wall of the cylinder is L1 = L6. The relationship between the other dimensions is the same as that of the first embodiment.

[0065] like Figure 13 The diagram shows a flow process in a refrigeration mode in the second preferred embodiment of the present invention, where the refrigerant inlet pressure is at a medium pressure level. Specifically, the medium-pressure refrigerant enters the outdoor unit through the outdoor inlet hole 107 and fills the lower part of the outdoor cylinder 101, pushing the outdoor piston 104 upwards and stretching the outdoor spring 103. This causes the outdoor horn-shaped flow hole 109 to connect with the outdoor second outlet hole 1082, at which point the outdoor piston 104 is in the middle position. After flowing through the outdoor circular flow hole 105 and the outdoor horn-shaped flow hole 109, the medium-pressure refrigerant enters the outdoor second capillary tube 202, achieving a pressure drop, then passes through the outdoor second check valve 302, enters the electronic expansion valve 7 for throttling, and then enters the indoor unit through the second outlet check valve 9. After being pressurized by the compressor, it enters the outdoor unit, completing one refrigeration cycle. The refrigerant does not enter the outdoor unit through the first outlet check valve 8 after exiting the electronic expansion valve 7 because the pressure at the outdoor unit outlet is higher than the outlet pressure of the electronic expansion valve 7. Meanwhile, the refrigerant will not enter the indoor reversing device 4 after flowing through the second outlet check valve 9 because the inlet pressure of the electronic expansion valve 7 is higher than the inlet pressure of the indoor reversing device 4.

[0066] like Figure 14 The diagram shows a flow process in a heating mode in the second preferred embodiment of the present invention, where the refrigerant inlet pressure is at a medium pressure level. Specifically, the medium-pressure refrigerant enters the indoor unit through the indoor inlet hole 407 and fills the lower part of the indoor cylinder 401, pushing the indoor piston 404 upwards and stretching the indoor spring 403. This causes the indoor horn-shaped flow hole 409 to connect with the indoor second outlet hole 4082, at which point the indoor piston 404 is in the middle position. After flowing through the indoor circular flow hole 405 and the indoor horn-shaped flow hole 409, the medium-pressure refrigerant enters the indoor second capillary tube 502, achieving a pressure drop, then passes through the indoor second check valve 602, enters the electronic expansion valve 7 for throttling, and then enters the outdoor unit through the first outlet check valve 8. After being pressurized by the compressor, it enters the indoor unit, completing one heating cycle. The refrigerant does not enter the indoor unit through the second outlet check valve 9 after exiting the electronic expansion valve 7 because the outlet pressure of the indoor unit is higher than the outlet pressure of the electronic expansion valve 7. Meanwhile, the refrigerant will not enter the outdoor reversing device 1 after flowing through the first outlet check valve 8 because the inlet pressure of the electronic expansion valve 7 is higher than the inlet pressure of the outdoor reversing device 1.

[0067] Example 3

[0068] like Figure 15 The diagram shows the overall structure of the third preferred embodiment of the present invention, with the names of the various numbers being the same as those in the first embodiment. The difference from the first embodiment is that the number of outlet holes in the outdoor side outlet hole group 108 is 6, the number of capillaries in the outdoor side capillary group 2 is 5, and the number of one-way valves in the outdoor side check valve group 3 is 6; the number of capillaries and one-way valves on the indoor side are the same as those on the outdoor side. Figure 16 A dimensional diagram of the reversing device in the third embodiment is provided. Inside the reversing device, the relationship between the variable length L3 of the spring, the distance l from the center of the uppermost outlet hole to the upper wall of the cylinder, the outlet hole diameter d1, and the outlet hole spacing l0 is: L3 ≥ l + 9d1 / 2 + l0. The relationships between the remaining dimensions are the same as in the first embodiment.

[0069] like Figure 17The diagram shows a flow process in a refrigeration mode in the third preferred embodiment of the present invention. At this time, the refrigerant inlet pressure is at a medium pressure level. Specifically, the medium-pressure refrigerant enters the outdoor unit through the outdoor inlet hole 107 and fills the lower part of the outdoor cylinder 101, pushing the outdoor piston 104 upwards and compressing the outdoor spring 103. This causes the outdoor horn-shaped flow hole 109 to connect with the outdoor third outlet hole 1083, at which point the outdoor piston 104 is in the middle position. After flowing through the outdoor circular flow hole 105 and the outdoor horn-shaped flow hole 109, the medium-pressure refrigerant enters the outdoor third capillary tube 203, achieving a pressure drop, then passes through the outdoor third check valve 303, enters the electronic expansion valve 7 for throttling, and then enters the indoor unit through the second outlet check valve 9. After being pressurized by the compressor, it enters the outdoor unit, completing one refrigeration cycle. The refrigerant does not enter the outdoor unit through the first outlet check valve 8 after exiting the electronic expansion valve 7 because the pressure at the outdoor unit outlet is higher than the outlet pressure of the electronic expansion valve 7. Meanwhile, the refrigerant will not enter the indoor reversing device 4 after flowing through the second outlet check valve 9 because the inlet pressure of the electronic expansion valve 7 is higher than the inlet pressure of the indoor reversing device 4.

[0070] like Figure 18 The diagram shows a flow process in a heating mode in the third preferred embodiment of the present invention. At this time, the refrigerant inlet pressure is at a medium pressure level. Specifically, the medium-pressure refrigerant enters the indoor unit through the indoor inlet hole 407 and fills the lower part of the indoor cylinder 401, pushing the indoor piston 404 upwards and stretching the indoor spring 403. This causes the indoor horn-shaped flow hole 409 to connect with the indoor third outlet hole 4083, at which point the indoor piston 404 is in the middle position. After flowing through the indoor circular flow hole 405 and the indoor horn-shaped flow hole 409, the medium-pressure refrigerant enters the indoor third capillary tube 503, achieving a pressure drop, then passes through the indoor third check valve 603, enters the electronic expansion valve 7 for throttling, and then enters the outdoor unit through the first outlet check valve 8. After being pressurized by the compressor, it enters the indoor unit, completing one heating cycle. The refrigerant does not enter the indoor unit through the second outlet check valve 9 after exiting the electronic expansion valve 7 because the pressure at the indoor unit outlet is higher than the outlet pressure of the electronic expansion valve 7. Meanwhile, the refrigerant will not enter the outdoor reversing device 1 after flowing through the first outlet check valve 8 because the inlet pressure of the electronic expansion valve 7 is higher than the inlet pressure of the outdoor reversing device 1.

[0071] The preferred embodiments of the present invention have been described in detail above. It should be understood that those skilled in the art can make numerous modifications and variations based on the concept of the present invention without creative effort. Therefore, all technical solutions that can be obtained by those skilled in the art based on the concept of the present invention through logical analysis, reasoning, or limited experimentation on the basis of existing technology should be within the scope of protection defined by the claims.

Claims

1. A multi-stage throttling and noise reduction device for an electronic expansion valve in the same flow direction, characterized in that, The device includes a reversing device, a capillary tube assembly, and an electronic expansion valve. The reversing device is connected to the electronic expansion valve via the capillary tube assembly. The capillary tube assembly consists of multiple capillary tubes of different lengths connected in parallel. The reversing device guides the refrigerant into the capillary tubes of different lengths based on the refrigerant pressure at the inlet. The capillary tube assembly also includes multiple one-way valves, with each capillary tube connected in series with one of the one-way valves. The one-way valves ensure that the refrigerant can only flow from the reversing device to the electronic expansion valve. The reversing device includes a cylinder, a spring, and a piston. The piston and the spring are disposed inside the cylinder body. The spring is placed vertically, and the piston is fixedly connected to the cylinder body through the spring. The bottom of the cylinder body has an inlet hole, and the side of the cylinder body connected to the capillary assembly has an outlet hole assembly. The outlet hole assembly includes multiple outlet holes, which are respectively connected to capillary tubes of different lengths. The bottom end of the piston has a circular flow passage, and the side of the piston has a trumpet-shaped flow passage facing the outlet hole assembly. The circular flow passage and the trumpet-shaped flow passage are interconnected.

2. The co-current multi-stage throttling and noise reduction device for an electronic expansion valve as described in claim 1, characterized in that, The reversing device further includes a first positioning ring and a second positioning ring. The first positioning ring is fixed on the side near the top of the cylinder body, and the second positioning ring is fixed on the side near the bottom of the cylinder body. The piston is disposed between the first positioning ring and the second positioning ring.

3. The co-current multi-stage throttling and noise reduction device for an electronic expansion valve as described in claim 1, characterized in that, The capillary tube assembly also includes a connecting tube, through which the reversing device is connected to the electronic expansion valve. The connecting tube is connected to the outlet hole near the inlet hole. A one-way valve is provided on the connecting tube, which allows the refrigerant to flow only from the reversing device to the electronic expansion valve.

4. The co-current multi-stage throttling and noise reduction device for an electronic expansion valve as described in claim 1, characterized in that, The capillary tube is shorter the closer it is to the inlet orifice.

5. The co-current multi-stage throttling and noise reduction device for an electronic expansion valve as described in claim 1, characterized in that, The reversing device includes an outdoor reversing device and an indoor reversing device. The capillary assembly includes an outdoor capillary assembly and an indoor capillary assembly. The outdoor reversing device is connected to the outdoor unit of the air conditioner and the outdoor capillary assembly. The indoor reversing device is connected to the indoor unit of the air conditioner and the indoor capillary assembly. The outdoor capillary assembly and the indoor capillary assembly are simultaneously connected to the inlet horizontal pipe of the electronic expansion valve. The outdoor unit of the air conditioner and the indoor unit of the air conditioner are connected to the compressor.

6. The co-current multi-stage throttling and noise reduction device for an electronic expansion valve as described in claim 5, characterized in that, It also includes a first outlet check valve and a second outlet check valve. The electronic expansion valve is connected to the outdoor reversing device and the outdoor unit of the air conditioner through the first outlet check valve. The first outlet check valve allows the refrigerant to flow only from the electronic expansion valve to the outdoor reversing device and the outdoor unit of the air conditioner. The electronic expansion valve is connected to the indoor reversing device and the indoor unit of the air conditioner through the second outlet check valve. The second outlet check valve allows the refrigerant to flow only from the electronic expansion valve to the indoor reversing device and the indoor unit of the air conditioner.

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