Electronic expansion valve and air conditioning system with same

Abstract

The utility model provides an electronic expansion valve and an air-conditioning system with the electronic expansion valve, the electronic expansion valve comprises a valve body component, a valve body component, a valve core component, a valve core component and a valve core component, the valve needle assembly is arranged in the containing cavity, the valve needle assembly is arranged corresponding to the valve port, and the valve needle assembly can move relative to the valve port so as to adjust the flow at the valve port; the connecting pipeline is connected with the valve body assembly and communicates with the containing cavity, when the electronic expansion valve is in a fully-closed state, a gap is formed between the valve needle assembly and the valve port, and fluid in the connecting pipeline can communicate with the containing cavity through the gap; wherein the minimum diameter of the valve port is between 4.5 mm and 9 mm. By means of the technical scheme, the problem that in the prior art, a control valve can throttle refrigerant fluid can be solved.

Description

[0001] The present application claims priority to the patent application with the application number 2024207377262, the utility model name "Electronic expansion valve and air conditioning system with the same", filed on April 10, 2024, with the State Intellectual Property Office of China. TECHNICAL FIELD

[0002] The utility model relates to air conditioning technical field, specifically, an electronic expansion valve and air conditioning system with the same. BACKGROUND

[0003] At present, in the air conditioning system with dehumidification function, the air conditioning system comprises a fluid circulation loop and a control valve, and a first heat exchanger and a second heat exchanger are arranged on the indoor side of the air conditioning system, the control valve is arranged on the fluid circulation loop and between the first heat exchanger and the second heat exchanger, the air conditioning system has a refrigeration and heating mode and a dehumidification mode, when the air conditioning system is in the refrigeration and heating mode, the control valve is in a full open state, and the first heat exchanger and the second heat exchanger can be regarded as an integral heat exchanger to release heat or absorb heat, when the air conditioning system is in the dehumidification mode, the second heat exchanger is a condenser, and the refrigerant fluid releases heat through the second heat exchanger, then flows out of the second heat exchanger and enters the control valve, the control valve can control the flow of the refrigerant fluid, so that the refrigerant fluid passes through the control valve at a small flow rate to reduce the pressure, and at this time, the first heat exchanger acts as an evaporator to absorb heat and achieve the dehumidification effect.

[0004] In the prior art, in order to prevent the refrigerant fluid from generating a large pressure drop in the flow process of the first heat exchanger and the second heat exchanger, the pipe diameter of the fluid circulation loop between the first heat exchanger and the second heat exchanger is usually set to be large, but this will cause material waste, and when the refrigerant fluid flows through the control valve, the control valve will also have a certain throttling effect on the fluid, affecting the circulation of the refrigerant fluid. SUMMARY

[0005] The utility model provides an electronic expansion valve and air conditioning system with the same to solve the problem that the control valve in the prior art will throttle the refrigerant fluid.

[0006] According to one aspect of the utility model, an electronic expansion valve is provided, which comprises: a valve body assembly having a receiving cavity, a valve port and a communication hole are arranged on the valve body assembly, and the valve port and the communication hole are respectively communicated with the receiving cavity; a valve needle assembly arranged in the receiving cavity, the valve needle assembly is arranged corresponding to the valve port, and the valve needle assembly can move relative to the valve port to adjust the flow rate at the valve port; a connecting pipeline connected with the valve body assembly, the connecting pipeline is communicated with the receiving cavity, when the electronic expansion valve is in a full closed state, there is a gap between the valve needle assembly and the valve port, and the fluid in the connecting pipeline can communicate with the receiving cavity through the gap; wherein the minimum diameter at the valve port is between 4.5-9mm.

[0007] The electronic expansion valve comprises a valve body assembly, a valve needle assembly, and a connecting pipeline. The valve needle assembly can adjust the flow rate at the valve port. When the electronic expansion valve is in a full-closed state, there is a gap between the valve needle assembly and the valve port. Fluid entering the accommodating cavity through the connecting pipeline can flow to the other side of the connecting pipeline through the gap between the valve needle assembly and the valve port, that is, the electronic expansion valve can have a certain flow capacity at this time. Therefore, the electronic expansion valve can be applied as a control valve in an air conditioning system to throttle the refrigerant fluid to realize the dehumidification function of the air conditioning system. The valve needle assembly can adjust the flow rate through the electronic expansion valve to meet the needs of air conditioners with different refrigerating capacities according to the actual air conditioning system. By setting the minimum diameter of the valve port to be between 4.5-9 mm, the electronic expansion valve can be applied to the flow requirements of the mainstream household split air conditioner indoor heat exchanger flow pipeline to ensure that the valve port is not throttled and that the minimum diameter of the valve port does not affect the operating efficiency of the entire machine.

[0008] Further, the valve port has oppositely arranged first and second flow-through ports. The first flow-through port is arranged close to the valve needle assembly. The diameter of the valve port gradually decreases from the first flow-through port to the second flow-through port. The end of the valve needle assembly facing the valve port forms a sealing end. The diameter of the first flow-through port is greater than that of the sealing end, and the diameter of the second flow-through port is less than or equal to that of the sealing end. The sealing end can move between the first and second flow-through ports to adjust the flow area of the valve port. Through the above arrangement, the electronic expansion valve can adjust the flow rate of the fluid.

[0009] Further, the valve needle assembly has an upper limit position and a lower limit position. When the valve needle assembly is in the upper limit position, the sealing end is located on the side of the first flow-through port away from the second flow-through port. When the valve needle assembly is in the lower limit position, the sealing end is located between the first and second flow-through ports. Through the above arrangement, the electronic expansion valve can have a certain flow rate in the full-closed state to realize the application of the electronic expansion valve as a dehumidification valve.

[0010] Further, when the electronic expansion valve is in a full-open mode, the flow coefficient Cv of the electronic expansion valve is ≥0.45, wherein, V is the maximum flow rate of the electronic expansion valve, G is the specific gravity of the flow medium in the electronic expansion valve, P1 is the pressure on the inflow side of the electronic expansion valve, and P2 is the pressure on the outflow side of the electronic expansion valve.

[0011] Further, the electronic expansion valve further comprises a sound attenuation assembly arranged in the valve body assembly, the sound attenuation assembly comprises a sound attenuation structure having a flow passage region and a bubble decomposition region, bubbles in the fluid flowing through the sound attenuation assembly can be decomposed through the bubble decomposition region. Through the above arrangement, the noise of the fluid flowing through the valve port can be reduced, and the fluid flowing through the electronic expansion valve will not be excessively throttled.

[0012] Further, the sound attenuation structure comprises a first sound attenuation block and a second sound attenuation block, the first sound attenuation block and the second sound attenuation block are arranged in a spaced manner along the flow direction of the fluid, the first sound attenuation block and the second sound attenuation block are both provided with the flow passage region and the bubble decomposition region, at least part of the flow passage region arranged on the first sound attenuation block is arranged in correspondence with the bubble decomposition region arranged on the second sound attenuation block, and at least part of the flow passage region arranged on the second sound attenuation block is arranged in correspondence with the bubble decomposition region arranged on the first sound attenuation block. Through the above arrangement, the area of the bubble decomposition region is increased, and the sound attenuation effect of the sound attenuation structure is improved.

[0013] Further, the first sound attenuation block and the second sound attenuation block are filter screen sintered blocks, the first sound attenuation block has at least one first through hole, and the second sound attenuation block has at least one second through hole, the first through hole forms the flow passage region on the first sound attenuation block, and the second through hole forms the flow passage region on the second sound attenuation block. Through the above arrangement, a hole with a larger diameter can be formed on the first sound attenuation block and the second sound attenuation block, so that impurities in the fluid cannot flow through the first sound attenuation block and the second sound attenuation block, and the filter screen sintered block is prevented from being clogged.

[0014] Further, the projection of the first through hole and the second through hole along the flow direction of the fluid has no overlapping part. Through the above arrangement, it can be ensured that as many bubbles as possible in the fluid can pass through the bubble decomposition region, and the sound attenuation effect of the sound attenuation structure is guaranteed.

[0015] Further, the total flow passage area of the first through hole and the plurality of second through holes is greater than or equal to 50% of the flow passage area of the valve port. Through the above arrangement, the sound attenuation structure can prevent excessive throttling of the fluid passing through, and the flow efficiency of the air conditioning system fluid is guaranteed.

[0016] Further, the pore size of the first sound attenuation block and the second sound attenuation block is 0.11-0.35mm. Through the above arrangement, the influence of the first sound attenuation block and the second sound attenuation block on the fluid flow can be reduced without affecting the decomposition effect of the first sound attenuation block and the second sound attenuation block.

[0017] Further, the porosity of the first sound attenuation block and the second sound attenuation block is 45%-95%. Through the above arrangement, the noise reduction effect of the sound attenuation structure can be improved while ensuring the smoothness of the fluid flow.

[0018] Further, the first sound attenuation block of the sound attenuation assembly is arranged close to the valve port, and a gap is formed between the valve port and the first sound attenuation block. A distance between the port of the valve port close to the first sound attenuation block and the first sound attenuation block is L1, and L1 is greater than or equal to 1 mm. Through the above arrangement, the influence of the sound attenuation assembly on the fluid flow can be reduced.

[0019] Further, the first sound attenuation block is arranged close to the valve port, and a flow area of the first through hole is 0.3 to 1 times of a flow area at the valve port. Through the above arrangement, the first sound attenuation block can prevent throttling of the refrigerant fluid, and the sound attenuation effect of the sound attenuation structure can be ensured.

[0020] Further, a flow area of the first through hole is S1, a diameter of the first through hole is R1, a distance between the first sound attenuation block and the second sound attenuation block is L2, and π*R1*L2 is greater than or equal to 1.2*S1. Through the above arrangement, the flow efficiency of the fluid can be improved.

[0021] Further, a diameter of the first sound attenuation block is more than 2 times of the flow area at the valve port. Through the above arrangement, the area of the decomposition region of the first sound attenuation block can be ensured, and the flow resistance of the fluid can be reduced.

[0022] Further, a support ring is arranged between the first sound attenuation block and the second sound attenuation block. The support ring is arranged at a peripheral edge of the second sound attenuation block, and the support ring avoids the flow area. Through the above arrangement, the support ring can prevent throttling of the fluid when the fluid flows through the sound attenuation structure.

[0023] Further, the support ring has a flow passage, an area of the flow passage is S2, a maximum projection area of the sound attenuation structure along the flow direction is S3, and S2 is greater than or equal to 0.8*S3. Through the above arrangement, the flow resistance of the fluid when flowing through the support ring can be reduced, and the smoothness of the fluid flow can be ensured while ensuring the supporting effect of the support ring on the first sound attenuation block.

[0024] Further, a support is arranged between the first sound attenuation block and the second sound attenuation block. The support has a mounting plate, the first sound attenuation block is arranged at one end of the mounting plate close to the valve port, the mounting plate is provided with a flow hole and a mounting ring, and the mounting ring is used to mount the second sound attenuation block. Through the above arrangement, the stability of the mounting of the first sound attenuation block and the second sound attenuation block can be ensured, and the flow performance of the fluid when flowing through the sound attenuation assembly can also be ensured.

[0025] Further, when the minimum diameter at the valve port is between 6-9 mm, and when the electronic expansion valve is in the full open mode, the flow coefficient Cv of the electronic expansion valve is greater than or equal to 0.6, wherein, V is the maximum flow of the electronic expansion valve, G is the specific gravity of the medium flowing in the electronic expansion valve, P1 is the pressure on the inflow side of the electronic expansion valve, and P2 is the pressure on the outflow side of the electronic expansion valve.

[0026] According to another aspect of the utility model, provide a kind of air conditioning system, air conditioning system includes compressor, indoor heat exchanger and outdoor heat exchanger being interconnected, indoor heat exchanger includes first heat exchanger and second heat exchanger, electronic expansion valve is arranged between first heat exchanger and second heat exchanger, and electronic expansion valve is above-mentioned electronic expansion valve.It is when air conditioning system is in refrigeration heating mode by above-mentioned arrangement, electronic expansion valve is full open state, valve port does not throttle refrigerant fluid, and first heat exchanger and second heat exchanger can be considered as one whole heat exchanger and heat is released or absorbed;When air conditioning system is in dehumidification mode, first heat exchanger is condenser, and refrigerant fluid is released heat by first heat exchanger, refrigerant fluid flows out first heat exchanger and enters electronic expansion valve, and electronic expansion valve can control the flow of refrigerant fluid, so that refrigerant fluid is throttled and depressurized by electronic expansion valve with small flow rate, second heat exchanger is evaporator and absorbs heat at this time, fan drives indoor humid air to pass through second heat exchanger and absorbs heat, so that water vapor condenses, and dehumidification effect is achieved, and indoor first heat exchanger is condenser, so that indoor air temperature rises, i.e. water vapor condensation and indoor condenser heat-released air are always circulated under the action of fan, so that the effect of dehumidification without temperature drop is achieved, and the use experience of user is improved.

[0027] Further, the first heat exchanger and the second heat exchanger are connected by a flow pipe, the electronic expansion valve is arranged on the flow pipe, a connecting pipe of the electronic expansion valve is connected with the flow pipe, and a diameter of a valve port of the electronic expansion valve is greater than an inner diameter of the flow pipe. Through the above arrangement, the pressure drop of the fluid when flowing through the electronic expansion valve between the first heat exchanger and the second heat exchanger can be avoided, and the flow efficiency of the refrigerant fluid when flowing through the electronic expansion valve is further ensured. BRIEF DESCRIPTION OF DRAWINGS

[0028] The drawings accompanying the specification of this application form a part thereof, serve to provide further understanding of the present application, and together with the description of the exemplary embodiments of the present application, serve to explain the present application. In the drawings:

[0029] Figure 1 Fig. 1 shows a structure schematic view of the electronic expansion valve provided by the utility model;

[0030] Figure 2 Fig. 2 shows a structure schematic view of the air conditioning system provided by the utility model; Figure 1 Fig. 3 shows a partial enlarged view of position A in Fig. 2;

[0031] Figure 3 Fig. 4 shows a structure schematic view of the sound-absorbing assembly provided by the utility model;

[0032] Figure 4 Fig. 5 shows a top view of the first sound-absorbing block provided by the utility model;

[0033] Figure 5A top view of the support ring is shown.

[0034] Figure 6 A top view of the second sound attenuation block is shown.

[0035] Figure 7 A top view of the support ring is shown. Figure 2 An enlarged view of the middle B is shown.

[0036] Figure 8 A structure schematic view of the bracket cooperating with the electronic expansion valve is shown.

[0037] Figure 9 A schematic view of the air conditioning system is shown.

[0038] Among them, the above-mentioned drawings include the following reference signs:

[0039] 10, first sound attenuation block; 11, first through hole;

[0040] 20, second sound attenuation block; 21, second through hole;

[0041] 30, support ring; 31, bracket; 311, blocking ring; 312, mounting plate; 313, mounting ring; 314, flow-through hole;

[0042] 40, valve body; 41, valve port; 411, straight line segment; 412, conical segment; 4121, first flow-through port; 4122, second flow-through port; 42, accommodating cavity;

[0043] 50, connecting pipeline;

[0044] 60, valve needle assembly;

[0045] 100, compressor; 200, indoor heat exchanger; 210, first heat exchanger; 220, second heat exchanger; 300, outdoor heat exchanger; 400, electronic expansion valve. DETAILED DESCRIPTION

[0046] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments. The description of the at least one exemplary embodiment is actually only illustrative, but not as any limitation on the present application and its application or use. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of the present application.

[0047] As Figure 1The utility model discloses an electronic expansion valve, electronic expansion valve includes valve body subassembly, valve needle subassembly 60 and connecting pipeline 50. Among them, valve body subassembly has accommodating chamber 42, is provided with valve port 41 and intercommunicating hole on valve body subassembly, and valve port 41 and intercommunicating hole communicate with accommodating chamber 42 respectively. Valve needle subassembly 60 sets up in accommodating chamber 42, and valve needle subassembly 60 sets up corresponding valve port 41, and valve needle subassembly 60 can move relative to valve port 41 to adjust the flow of valve port 41. Connecting pipeline 50 is connected with valve body subassembly, and connecting pipeline 50 communicates with accommodating chamber 42, when electronic expansion valve is in full close state, and there is gap between valve needle subassembly 60 and valve port, and the fluid in connecting pipeline 50 can communicate with accommodating chamber 42 through the gap. Among them, the minimum diameter at valve port 41 is between 4.5-9mm.

[0048] The utility model discloses an electronic expansion valve, electronic expansion valve includes valve body subassembly, valve needle subassembly 60 and connecting pipeline 50, valve needle subassembly 60 can adjust the flow of valve port 41, and when electronic expansion valve is in full close state, and there is gap between valve needle subassembly 60 and valve port 41, and the fluid in connecting pipeline 50 can flow to the connecting pipeline 50 of another side through the gap between valve needle subassembly 60 and valve port 41, that is, the electronic expansion valve can have certain flow capacity at this time, so the electronic expansion valve can be applied in air conditioning system as control valve, and the flow of refrigerant fluid is throttled to realize the dehumidification function of air conditioning system, and valve needle subassembly 60 can adjust the flow of valve port 41, and according to the actual air conditioning system needs, the flow through electronic expansion valve is adjusted to meet the needs of different refrigerating capacity air conditioner.

[0049] Specifically, in the prior art, the outer diameter of the flow pipeline between the indoor heat exchangers of the air conditioner needs to be considered according to the refrigerating capacity of the air conditioner. If the pipe diameter is too large, material will be wasted, and the refrigerating capacity of the air conditioner will not match, affecting the performance of the air conditioner. If the pipe diameter is too small, the pressure drop will be too large, also affecting the performance of the air conditioner. The refrigerating capacity of the mainstream air conditioner is between 1-3 tons, and the outer diameter of the flow pipeline between the indoor heat exchangers in this refrigerating capacity range is between 7mm-8mm, and the wall thickness is mainly 0.8mm. Therefore, the inner diameter of the flow pipeline between the indoor heat exchangers is mostly between 5.4mm-6.4mm. In this application, the minimum diameter of the valve port 41 is set to be between 4.5-9mm. When the minimum diameter of the valve port 41 is less than 4.5mm, the minimum diameter of the valve port 41 is too small, which is smaller than the inner diameter of the flow pipeline between the indoor heat exchangers of the mainstream household split air conditioner. Since the valve is fully open during normal air conditioner operation, if the minimum diameter of the valve port 41 is too small, throttling will be obvious, affecting the performance of the air conditioner. When the minimum diameter of the valve port 41 is greater than 9mm, the minimum diameter of the valve port 41 is too large, and the flow is too large when fully open, affecting the operating efficiency of the air conditioner. In this application, by setting the minimum diameter of the valve port 41 to be between 4.5-9mm, the minimum diameter of the valve port 41 is greater than the inner diameter of the flow pipeline between the indoor heat exchangers, which can meet the flow requirements of the flow pipeline between the indoor heat exchangers of the mainstream household split air conditioner, ensuring that there is no throttling and preventing the minimum diameter of the valve port 41 from being too large to affect the operating efficiency of the air conditioner. Through the above setting, the flow capacity of the electronic expansion valve in the fully open state can be ensured, the flow efficiency of the electronic expansion valve is ensured, and the electronic expansion valve is prevented from throttling the refrigerant fluid. Specifically, the minimum diameter of the valve port 41 can be set to 4.5mm, 5mm, 6mm, 6.5mm or 9mm.

[0050] In some embodiments of the present application, the valve body assembly includes a valve body 40, and the valve port and / or the communication hole can be integrally arranged with the valve body 40.

[0051] In some other embodiments of the present application, the valve body assembly includes a valve body 40 and a valve seat, and the valve body 40 and the valve seat are fixedly connected. The valve port and / or the communication hole can be arranged separately from the valve body 40.

[0052] Specifically, when the electronic expansion valve is in the fully open mode, the flow coefficient Cv≥0.45, wherein, V is the maximum flow of the electronic expansion valve, G is the specific gravity of the medium flowing in the electronic expansion valve, P1 is the pressure on the inflow side of the electronic expansion valve, and P2 is the pressure on the outflow side of the electronic expansion valve. The Cv value is the flow coefficient of the electronic expansion valve, which represents the flow capacity of the electronic expansion valve provided in the present application when fully open. When the Cv value is less than 0.45, the flow capacity of the fluid will be affected, that is, the electronic expansion valve will still throttle the fluid flowing through when fully open, which means that the flow capacity of the electronic expansion valve in the fully open state is not enough, affecting the fluid flow between the indoor heat exchangers and thus affecting the performance of the entire machine. In the present application, by setting Cv≥0.45, the flow capacity of the electronic expansion valve can be ensured to meet the performance requirements of the entire machine when used under normal operating conditions of the air conditioner.

[0053] Referring to Figure 2 As shown in FIG. 1, the valve port 41 has a first flow port 4121 and a second flow port 4122 arranged opposite to each other, the first flow port 4121 is arranged close to the valve needle assembly 60, the diameter of the valve port 41 between the first flow port 4121 and the second flow port 4122 gradually decreases from the first flow port 4121 to the second flow port 4122, the end of the valve needle assembly 60 towards the valve port 41 forms a sealing end, the diameter of the first flow port 4121 is greater than the diameter of the sealing end, the diameter of the second flow port 4122 is less than or equal to the diameter of the sealing end, and the sealing end can move between the first flow port 4121 and the second flow port 4122 to adjust the flow area at the valve port 41. Specifically, the valve port 41 of the electronic expansion valve has a straight section 411 and a tapered section 412 that are in communication with each other, the straight section 411 is arranged away from the valve needle assembly 60, and the tapered section 412 has the first flow port 4121 and the second flow port 4122. Through the above arrangement, the sealing end of the valve needle assembly 60 can enter the first flow port 4121 and move towards the second flow port 4122. Since the diameter of the valve port 41 between the first flow port 4121 and the second flow port 4122 gradually decreases from the first flow port 4121 to the second flow port 4122, that is, the inner diameter of the tapered section 412 gradually decreases away from the valve needle assembly 60, the distance between the outer diameter of the sealing end and the inner wall of the tapered section 412 will change with the movement of the valve needle assembly 60 in the tapered section 412, so that the flow area of the fluid at the valve port 41 can be adjusted, and the flow of the fluid can be adjusted.

[0054] In the traditional technical solution, the control valve is usually a dehumidification electromagnetic valve. The dehumidification electromagnetic valve has a valve needle and a valve port. The valve needle can open or block the valve port to control the on-off of the refrigerant fluid passing through the valve port. In order to realize the small flow circulation mode, the electromagnetic valve is provided with a valve piece having a throttling hole on the valve core to realize the circulation of small flow refrigerant fluid when the electromagnetic valve is in the full-closed mode. However, this setting mode causes the flow of the refrigerant fluid to be fixed at a certain value and cannot be adjusted, and the matching value of the dehumidification amount and the heating amount cannot be accurately controlled. When dehumidification is performed, the indoor temperature changes, the dehumidification effect is poor, and the size of the throttling hole may not be accurate due to the stamping formation, thereby easily causing the instability of the throttling effect of the dehumidification electromagnetic valve, causing the overheating degree to fluctuate, affecting the energy efficiency of the air conditioning dehumidification operation, and the electromagnetic valve also has obvious mechanical noise in the opening and closing process, affecting the user experience. In the present application, the valve port 41 of the electronic expansion valve can realize the flow regulation of the refrigerant fluid. Compared with the dehumidification electromagnetic valve used in the traditional technology, the valve needle assembly 60 and the valve port 41 cooperate to accurately control the flow of the refrigerant fluid in the full stroke of the valve needle assembly 60, and can be used for multiple specifications of valves. In the dehumidification working condition, that is, in the full-closed state, the flow can also be accurately controlled, so that the dehumidification amount and the heating amount can be accurately controlled to improve the dehumidification effect without temperature drop and improve the user experience. In addition, different refrigeration capacity air conditioning models can be covered by one dehumidification electronic expansion valve, which improves the standardization of key components and improves the applicability of the electronic expansion valve.

[0055] Specifically, in the present application, the valve needle assembly 60 has an upper limit position and a lower limit position. When the valve needle assembly 60 is in the upper limit position, the sealing end is located on the side away from the second flow port 4122 of the first flow port 4121. When the valve needle assembly 60 is in the lower limit position, the sealing end is located in the conical section 412, as shown in Figure 7 That is, the sealing end is located between the first flow port 4121 and the second flow port 4122, and there is a gap between the sealing end and the inner wall of the conical section 412. The fluid entering the containing cavity 42 through the connecting pipeline 50 can flow to the connecting pipeline 50 on the other side through the gap between the valve needle assembly 60 and the valve port 41. Through the above setting, when the valve needle assembly 60 is in the lower limit position, the electronic expansion valve can still have fluid flowing through the valve port 41 in the full-closed state, that is, the electronic expansion valve has a small flow function in the full-closed state. Compared with the traditional technical solution, by using the electronic expansion valve as the control valve, the present application can avoid the instability of the throttling effect of the throttling hole of the traditional dehumidification electromagnetic valve due to the manufacturing and installation process, avoid the overheating degree fluctuation of the air conditioning system due to the throttling hole, accurately control the flow, improve the throttling stability, and ensure the energy efficiency of the air conditioning dehumidification operation.

[0056] Specifically in the present application, since the electronic expansion valve provided by the present application is arranged on the indoor side, the noise reduction capability of the electronic expansion valve has certain requirements, otherwise the noise of the electronic expansion valve during operation is too large to easily affect the user experience; therefore, the electronic expansion valve with dehumidification function of the present application further comprises a sound attenuation assembly, the sound attenuation assembly is arranged in the valve body 40, the sound attenuation assembly comprises a sound attenuation structure, the sound attenuation structure has a flow-through region and a decomposition region, the bubbles in the fluid flowing through the sound attenuation assembly can be decomposed through the decomposition region. Through the above arrangement, the larger bubbles in the two-phase fluid flowing through the decomposition region will be decomposed into smaller bubbles in the decomposition region, so that the size of the bubbles in the fluid becomes uniform, thereby reducing the abnormal noise generated by the unstable and discontinuous large bubbles during flow, and the impurities in the fluid cannot pass through the decomposition region, which is easy to cause the dirty blockage of the decomposition region, by setting the flow-through region, the impurities can flow through the sound attenuation assembly through the flow-through region, preventing the sound attenuation assembly from being blocked, and also reducing the influence of the sound attenuation assembly on the throttling of the refrigerant fluid, ensuring the flow-through performance of the fluid.

[0057] Referring to Figures 3 to 6 As shown in the figure, the sound attenuation structure comprises a first sound attenuation block 10 and a second sound attenuation block 20, the first sound attenuation block 10 and the second sound attenuation block 20 are arranged in a spaced manner along the flow direction of the fluid, the first sound attenuation block 10 and the second sound attenuation block 20 are both provided with a flow-through region and a decomposition region, the flow-through region arranged at least partially on the first sound attenuation block 10 is arranged in a corresponding manner with the decomposition region arranged on the second sound attenuation block 20, and the flow-through region arranged at least partially on the second sound attenuation block 20 is arranged in a corresponding manner with the decomposition region arranged on the first sound attenuation block 10. Through the above arrangement, the bubbles in the fluid mixed with impurities will still flow through the decomposition region on the first sound attenuation block 10 or the second sound attenuation block 20 after flowing through the flow-through region on the first sound attenuation block 10 or the second sound attenuation block 20, thereby improving the decomposition effect of the sound attenuation assembly and further improving the noise reduction capability of the sound attenuation assembly.

[0058] Further, the first sound attenuation block 10 and the second sound attenuation block 20 are filter sintered blocks, the first sound attenuation block 10 is provided with at least one first through hole 11, the first through hole 11 can be one or multiple, the second sound attenuation block 20 is provided with at least one second through hole, the second through hole can be one or multiple. The first through hole 11 forms a flow-through area on the first sound attenuation block 10, and the second through hole 21 forms a flow-through area on the second sound attenuation block 20. The filter sintered block is woven by metal wires or alloy wires, and then the metal wires or alloy wires are sintered with each other to form a uniform block-shaped filter material with high strength and stability, which can effectively play a filtering effect. By providing the first through hole 11 on the first sound attenuation block 10 and the second through hole 21 on the second sound attenuation block 20, a hole with a larger diameter can be formed on the filter sintered block, so that the impurities in the fluid cannot flow through the first sound attenuation block 10 and the second sound attenuation block 20, preventing the first sound attenuation block 10 and the second sound attenuation block 20 from being dirty and blocked.

[0059] Preferably, the minimum diameter at the valve port 41 can be set to 6-9mm, when the electronic expansion valve is in full open mode, the flow coefficient Cv of the electronic expansion valve ≥0.6, so as to further improve the use performance of the electronic expansion valve.

[0060] Specifically in the present application, the projection of the first through hole 11 and the second through hole 21 along the fluid flow direction has no overlapping part. Through the above setting, the fluid flowing through the first through hole 11 can pass through the second sound attenuation block 20 except the part of the second through hole 21, and the fluid flowing through the second through hole 21 can pass through the first sound attenuation block 10 except the part of the first through hole 11, preventing the fluid from directly passing through the first through hole 11 and the second through hole 21 without filtering, ensuring that the fluid can pass through the decomposition area for filtering, and improving the noise reduction effect of the sound attenuation structure.

[0061] Specifically, the total flow area of the first through hole 11 and the plurality of second through holes 21 is greater than the minimum aperture flow area of the filter screen on the system pipeline, and the total flow area of the first through hole 11 and the plurality of second through holes 21 is greater than or equal to 50% of the flow area of the valve port 41. That is, the total flow area of the first through hole 11 is greater than or equal to the flow area of the valve port 41, and the total flow area of the second through hole 21 is greater than or equal to the flow area of the valve port 41. When the total flow area of the first through hole 11 and the plurality of second through holes 21 is less than 50% of the flow area of the valve port 41, the first sound attenuation block 10 and the second sound attenuation block 20 will cause greater flow resistance to the fluid flowing through the valve port 41, affecting the flow of the fluid. By setting the total flow area of the first through hole 11 and the plurality of second through holes 21 to be greater than or equal to 50% of the flow area of the valve port 41, it can be prevented that the sound attenuation structure causes too much throttling to the passing fluid, and the flow efficiency of the air conditioning system fluid can be ensured. Specifically, the total flow area of the first through hole 11 and the second through hole 21 can be set to 50%, 55%, 60% or 100% of the flow area of the valve port 41, and the flow capacity of the electronic expansion valve can be further improved. The total flow area of the first through hole 11 and the second through hole 21 is set to be greater than the flow area of the valve port 41.

[0062] In different embodiments, the Cv values of the valve port 41 with different diameters are as follows:

[0063] Example 1

[0064] The minimum diameter at the valve port 41 is 4.5 mm, the total flow area of the first through hole 11 on the first sound attenuation block 10 is equal to the flow area of the valve port 41, the total flow area of the second through hole 21 on the second sound attenuation block 20 is equal to the flow area of the valve port 41, and the flow direction of the refrigerant is first through the containing cavity 42 and then through the valve port 41. The experiment shows that Cv=0.45; when the flow direction of the refrigerant is first through the valve port 41 and then through the containing cavity 42, the experiment shows that Cv=0.46;

[0065] Example 2

[0066] The minimum diameter at the valve port 41 is 6 mm, the total flow area of the first through hole 11 on the first sound attenuation block 10 is equal to the flow area of the valve port 41, the total flow area of the second through hole 21 on the second sound attenuation block 20 is equal to the flow area of the valve port 41, and the flow direction of the refrigerant is first through the containing cavity 42 and then through the valve port 41. The experiment shows that Cv=0.6; when the flow direction of the refrigerant is first through the valve port 41 and then through the containing cavity 42, the experiment shows that Cv=0.6;

[0067] Example 3

[0068] The minimum diameter at the valve port 41 is 6.35 mm, the total flow area of the first through hole 11 on the first sound attenuation block 10 is equal to the flow area of the valve port 41, the total flow area of the second through hole 21 on the second sound attenuation block 20 is equal to the flow area of the valve port 41, the flow direction of the refrigerant is first through the containing cavity 42 and then through the valve port 41, and the experiment shows that Cv=0.65; when the flow direction of the refrigerant is first through the valve port 41 and then through the containing cavity 42, the experiment shows that Cv=0.66.

[0069] Embodiment 4

[0070] The minimum diameter at the valve port 41 is 8 mm, the total flow area of the first through hole 11 on the first sound attenuation block 10 is equal to the flow area of the valve port 41, the total flow area of the second through hole 21 on the second sound attenuation block 20 is equal to the flow area of the valve port 41, the flow direction of the refrigerant is first through the containing cavity 42 and then through the valve port 41, and the experiment shows that Cv=0.81; when the flow direction of the refrigerant is first through the valve port 41 and then through the containing cavity 42, the experiment shows that Cv=0.82.

[0071] It can be known from the above embodiments that when the diameter of the valve port 41 is selected to be between 4.5-9 mm, and the total flow area of the first through hole 11 on the first sound attenuation block 10 is equal to the flow area of the valve port 41, and the total flow area of the second through hole 21 on the second sound attenuation block 20 is equal to the flow area of the valve port 41, Cv≥0.45 can be achieved. In the above embodiments, under the same other conditions, if the total flow area of the first through hole 11 on the first sound attenuation block 10 and / or the total flow area of the second through hole 21 on the second sound attenuation block 20 is further increased and is greater than the flow area of the valve port 41, the Cv value will be further increased accordingly. When the minimum diameter at the valve port 41 is ≥6, Cv≥0.6, which ensures the flow capacity of the electronic expansion valve. When the electronic expansion valve provided in the application is used under normal working conditions of the air conditioner, the flow capacity of the electronic expansion valve can meet the performance requirements of the whole machine.

[0072] Specifically, the pore size of the first sound attenuation block 10 and the second sound attenuation block 20 is 0.11-0.35 mm. When the pore size of the first sound attenuation block 10 and the second sound attenuation block 20 is less than 0.11 mm, the pore size of the first sound attenuation block 10 and the second sound attenuation block 20 is too small, the spacing of the holes on the first sound attenuation block 10 and the second sound attenuation block 20 is too small, so that the first sound attenuation block 10 and the second sound attenuation block 20 will form greater resistance to the flow of fluid, affecting the flow of fluid; when the pore size of the first sound attenuation block 10 and the second sound attenuation block 20 is greater than 0.35 mm, the pore size of the first sound attenuation block 10 and the second sound attenuation block 20 is too large, the spacing of the holes on the first sound attenuation block 10 and the second sound attenuation block 20 is too large, the effect of decomposing large bubbles is poor, in the present application, by setting the pore size of the first sound attenuation block 10 and the second sound attenuation block 20 to 0.11-0.35 mm, the influence of the first sound attenuation block 10 and the second sound attenuation block 20 on the fluid flow can be reduced without affecting the decomposition effect of the first sound attenuation block 10 and the second sound attenuation block 20, preventing the first sound attenuation block 10 and the second sound attenuation block 20 from causing excessive throttling to the passing fluid, affecting the flow efficiency of the air conditioning system fluid. Specifically, the pore size of the first sound attenuation block 10 and the second sound attenuation block 20 can be set to 0.11 mm, 0.2 mm, 0.25 mm, 0.28 mm or 0.35 mm.

[0073] Specifically, the porosity of the first sound attenuation block 10 and the second sound attenuation block 20 is 45%-95%. The porosity refers to the ratio of the volume of the pores in the material to the total volume. When the porosity of the first sound attenuation block 10 and the second sound attenuation block 20 is less than 45%, the ratio of the volume of the pores in the first sound attenuation block 10 and the second sound attenuation block 20 to the total volume is too small, the decomposition efficiency of the sound attenuation assembly for bubbles is poor, and the flow resistance of the fluid is increased, affecting the flow of the fluid; when the porosity of the first sound attenuation block 10 and the second sound attenuation block 20 is greater than 95%, the ratio of the volume of the pores in the first sound attenuation block 10 and the second sound attenuation block 20 to the total volume is too large, the effect of the first sound attenuation block 10 and the second sound attenuation block 20 on the refinement of the bubbles is poor, in the present application, by setting the porosity of the first sound attenuation block 10 and the second sound attenuation block 20 to 45%-95%, the flow smoothness of the fluid can be ensured while the noise reduction effect of the sound attenuation structure is improved. Specifically, the porosity of the first sound attenuation block 10 and the second sound attenuation block 20 can be set to 45%, 50%, 80% or 95%.

[0074] In the present application, the first sound attenuation block 10 of the sound attenuation assembly is arranged close to the valve port 41, and the valve port 41 has a spacing with the first sound attenuation block 10. The distance between the port of the valve port 41 close to the first sound attenuation block 10 and the first sound attenuation block 10 is L1, and L1≥1mm. When the distance between the port of the valve port 41 close to the first sound attenuation block 10 and the first sound attenuation block 10 is less than 1mm, the distance between the port of the valve port 41 close to the first sound attenuation block 10 and the first sound attenuation block 10 is too small, which is not conducive to the flow of fluid in the valve port 41 and the sound attenuation assembly, and the fluid will be subjected to a large flow resistance. In the present application, by setting L1≥1mm, the influence of the sound attenuation assembly on the fluid flow can be reduced. Specifically, L1 can be set to 1mm, 1.5mm, 2mm or 3mm.

[0075] Further, the first sound attenuation block 10 is arranged close to the valve port 41, and the flow area of the first through hole 11 is 0.3 to 1 times the flow area at the valve port 41. When the flow area of the first through hole 11 is less than 0.3 times the flow area at the valve port 41, the first sound attenuation block 10 can excessively throttle the fluid, affecting the flow of the fluid; when the flow area of the first through hole 11 is greater than 1 times the flow area at the valve port 41, the fluid can not pass through the decomposition area on the first sound attenuation block 10 after passing through the valve port 41, affecting the sound attenuation effect of the sound attenuation structure. In the present application, by setting the flow area of the first through hole 11 to be 0.3 to 1 times the flow area at the valve port 41, the first sound attenuation block 10 can be prevented from throttling the refrigerant fluid, and the sound attenuation effect of the sound attenuation structure can be ensured.

[0076] Specifically, the flow area of the first through hole 11 is S1, the diameter of the first through hole 11 is R1, and the distance between the first sound attenuation block 10 and the second sound attenuation block 20 is L2, and π*R1*L2≥1.2*S1. π*R1*L2 is the flow area of the first through hole 11 between the first sound attenuation block 10 and the second sound attenuation block 20. When the flow area of the first through hole 11 between the first sound attenuation block 10 and the second sound attenuation block 20 is less than 1.2 times the flow area of the first through hole 11, the fluid will be subjected to a large flow resistance when flowing through the sound attenuation assembly. In the present application, by setting π*R1*L2≥1.2*S1, the flow efficiency of the fluid can be improved.

[0077] Specifically, the diameter of the first sound attenuation block 10 is more than 2 times the area of the valve port 41. When the diameter of the first sound attenuation block 10 is less than the area of the valve port 41, the diameter of the first sound attenuation block 10 is too small. When the fluid passes through the first sound attenuation block 10 for bubble decomposition, the diameter of the first sound attenuation block 10 is small and cannot match the flow of the fluid at the valve port 41, which will generate a large flow resistance to the fluid and reduce the flow efficiency of the fluid. In the present application, by setting the diameter of the first sound attenuation block 10 to be more than 2 times the area of the valve port 41, the area of the decomposition area of the first sound attenuation block 10 can be ensured, and the flow resistance of the fluid can be reduced.

[0078] In one specific embodiment of this application, a support ring 30 is provided between the first muffler block 10 and the second muffler block 20. The support ring 30 is located around the periphery of the second muffler block 20 and is positioned to avoid the flow area. By providing the support ring 30, the relative displacement of the first muffler block 10 and the second muffler block 20 can be restricted, preventing displacement of either the first muffler block 10 or the second muffler block 20 under the impact of fluid, thus ensuring the stability of the first muffler block 10 and the second muffler block 20. Furthermore, by positioning the support ring 30 to avoid the flow area, it can prevent the support ring 30 from throttling the fluid as it flows through the muffler structure.

[0079] Specifically, the support ring 30 has a flow channel with an area of ​​S2, and the maximum projected area of ​​the silencing structure along the flow direction is S3, where S2 ≥ 0.8 * S3. When the area of ​​the flow channel S2 is less than 0.8 * S3, the flow area of ​​the support ring 30 is small, and the fluid will experience greater flow resistance when passing through the support ring 30, affecting the flow of the fluid and reducing the flow rate of the fluid passing through the first silencing block 10, the second silencing block 20, and the support ring 30. In this application, by setting S2 ≥ 0.8 * S3, the flow resistance experienced by the fluid when flowing through the support ring 30 can be reduced while ensuring the supporting effect of the support ring 30 on the first silencing block 10, thus ensuring smooth fluid flow.

[0080] The size setting of the above-mentioned silencing structure can reduce the impact of the silencing structure on fluid flow caused by the silencing structure in the valve body 40 of the electronic expansion valve provided in this application, and avoid excessive throttling; at the same time, it can also reduce the noise generated by the indoor electronic expansion valve during operation.

[0081] like Figure 8 As shown, in another embodiment of this application, a bracket 31 is provided between the first muffler block 10 and the second muffler block 20. The bracket 31 has a mounting plate 312. The first muffler block 10 is disposed at one end of the mounting plate 312 near the valve port 41. The mounting plate 312 is provided with a flow hole 314 and a mounting ring 313. The mounting ring 313 is used to install the second muffler block 20. The bracket 31 also has a retaining ring 311 that is connected to the mounting plate 312. The first muffler block 10 and the second muffler block 20 are separated by the retaining ring 311. The mounting ring 313 has a mounting hole in which the second muffler block 20 is disposed. This can prevent the second muffler block 20 from displacing under the impact of the fluid, further improving the stability of the muffler assembly installation. In addition, the flow hole 314 provided on the mounting plate 312 can also provide for the flow of impurities, preventing the muffler assembly from being blocked and ensuring the fluid flow performance.

[0082] This application also provides an air conditioning system, wherein the dehumidifying electronic expansion valve provided in this application is used in…Figure 9 The air conditioning system shown in the figure, the air conditioning system comprises a compressor 100, an indoor heat exchanger 200 and an outdoor heat exchanger 300 which are communicated with each other, the indoor heat exchanger 200 comprises a first heat exchanger 210 and a second heat exchanger 220, an electronic expansion valve 400 is arranged between the first heat exchanger 210 and the second heat exchanger 220, and the electronic expansion valve 400 is the electronic expansion valve described above. Through the above arrangement, when the air conditioning system is in a cooling and heating mode, the electronic expansion valve 400 is in a full open state, the valve port 41 does not throttle the refrigerant fluid, and the first heat exchanger 210 and the second heat exchanger 220 can be regarded as an integral heat exchanger to release heat or absorb heat; when the air conditioning system is in a dehumidification mode, the second heat exchanger 220 is a condenser, the refrigerant fluid releases heat through the second heat exchanger 220, and the refrigerant fluid flows out of the second heat exchanger 220 and enters the electronic expansion valve 400. The electronic expansion valve 400 can control the flow of the refrigerant fluid, so that the refrigerant fluid throttles and depressurizes through the electronic expansion valve 400 at a small flow rate. At this time, the first heat exchanger 210 acts as an evaporator to absorb heat, and the fan drives the indoor humid air to pass through the heat-absorbing first heat exchanger 210 to make the water vapor condense, thereby achieving the dehumidification effect. At the same time, the indoor second heat exchanger 220 acts as a condenser to make the indoor air temperature rise, that is, the air passes through the first heat exchanger 210 for dew condensation and dehumidification, passes through the second heat exchanger 220 for temperature rise, and circulates under the action of the fan, thereby achieving the effect of dehumidification without temperature drop and improving the user experience.

[0083] Specifically, the first heat exchanger 210 and the second heat exchanger 220 are connected through a flow pipe, and the electronic expansion valve 400 is arranged on the flow pipe. The connecting pipe 50 of the electronic expansion valve 400 is connected with the flow pipe, and the minimum diameter at the valve port 41 is greater than the inner diameter of the flow pipe, so that the flow of the fluid through the valve port 41 can not be obviously throttled, and the normal flow of the fluid between the first heat exchanger 210 and the second heat exchanger 220 is ensured.

[0084] Specifically, in the present application, the inner diameter of the connecting pipe 50 is greater than the inner diameter of the flow pipe. Through the above arrangement, when the connecting pipe 50 is connected with the flow pipe, the fluid flowing through the connecting pipe 50 and the electronic expansion valve 400 provided in the present application can avoid pressure drop, thereby further ensuring the flow efficiency of the refrigerant fluid flowing through the electronic expansion valve 400.

[0085] The use of the electronic expansion valve provided in the present application can meet the requirements of the indoor electronic expansion valve when the air conditioning system is in a cooling, heating and dehumidification mode. Compared with the traditional scheme, the electronic expansion valve provided in the present application has the following advantages:

[0086] 1. By setting the minimum diameter at the valve port 41 to be greater than the inner diameter of the flow pipe, the flow of the fluid through the electronic expansion valve can be prevented from being throttled, and the flow capacity of the fluid in the air conditioning system is ensured.

[0087] 2, The flow of the dehumidification electromagnetic valve cannot be adjusted when it is running in the dehumidification mode, which cannot accurately match the dehumidification amount and the condensation heat release amount, resulting in a significant reduction in the effect of dehumidification without temperature drop. The throttling opening of the dehumidification electronic expansion valve can be accurately adjusted according to the control logic of the whole machine manufacturer, thereby improving the effect of dehumidification without temperature drop and improving the user experience.

[0088] 3, The dehumidification electromagnetic valve has a small flow in the full-closed mode, which needs to be realized by the size of the throttling small hole on the internal throttling piece. The throttling small hole is mostly stamped, with poor size precision. When running in the dehumidification mode, the unstable throttling of the dehumidification electromagnetic valve causes the fluctuation of the superheat degree, affecting the dehumidification operation efficiency. The use of the dehumidification electronic expansion valve can accurately control the flow, with high machining and matching precision of the internal related parts and high throttling stability.

[0089] 4, Since it is used on the indoor side, the noise of the dehumidification electromagnetic valve when turning on and off is relatively obvious. The use of the electronic expansion valve can effectively reduce mechanical noise, and by setting the sound attenuation structure in the electronic expansion valve, it can further reduce the noise caused by bubbles when the refrigerant fluid flows through the electronic expansion valve, ensuring the user experience.

[0090] 5, The flow of the electronic expansion valve in the full-open and small-opening flow modes can be accurately controlled according to the requirements of the air conditioning machine, which can be used for multiple specifications of valves, and one dehumidification electronic expansion valve can cover different refrigerating capacity models, improving the standardization of key components and the applicability of the electronic expansion valve.

[0091] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments consistent with the present application. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms "comprises" and / or "comprising," when used in this specification, specify the presence of stated features, steps, operations, elements, components, and / or groups thereof, but do not preclude the presence or addition of one or more other features, steps, operations, elements, components, and / or groups thereof.

[0092] The foregoing description, for purposes of explanation, sets forth specific values and arrangements of components and steps that are subject to many variations in the light of specific circumstances and / or material or workpiece shapes. Such examples, while indicating preferred embodiments, are not intended to limit or restrict the various concepts taught herein. It will be appreciated that the dimensions of the parts shown in the drawings are not necessarily to scale, and have been shown as such for illustrative purposes only. Techniques, methods, and apparatus known to those of ordinary skill in the art can not be discussed in detail, but are contemplated as being part of the specification, where appropriate. In all examples shown and discussed herein, any specific values are to be interpreted as merely illustrative of the examples, and not as a limitation thereon. Thus, other examples of the exemplary embodiments can have different values. It is noted that like numbers and letters on the figures identify like parts throughout the disclosure, and thus, once an item is defined in one figure, it is not necessary to discuss it further in connection with other figures where it is shown and / or discussed.

[0093] In the description of the present application, it needs to be understood that the orientation words such as "front, back, up, down, left, right", "horizontal, vertical, perpendicular, horizontal" and "top, bottom" and the like indicated orientation or position relationship are usually based on the orientation or position relationship shown in the drawings, only for the convenience of describing the present application and simplifying the description, without making the opposite statement, these orientation words do not indicate and imply that the indicated device or element must have a specific orientation or be constructed and operated in a specific orientation, therefore, it cannot be understood as a limitation on the protection scope of the present application; the orientation words "inner, outer" refer to the inner and outer of the contour of each component itself.

[0094] For the convenience of description, spatial relative terms such as "above", "upper", "on", "top", "bottom", etc. can be used herein to describe the spatial relationship of one device or feature to other devices or features as shown in the drawings. It should be understood that the spatial relative terms are intended to include different orientations in use or operation in addition to the orientation of the device described in the drawings. For example, if the device in the drawing is inverted, the device described as "above" or "on" other devices or structures will be positioned "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below" orientations. The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein are interpreted accordingly.

[0095] In addition, it needs to be explained that the use of "first", "second" and the like to limit parts is only for the convenience of distinguishing the corresponding parts, and the above words have no special meaning unless otherwise stated, therefore, it cannot be understood as a limitation on the protection scope of the present application.

[0096] The above merely describes preferred embodiments of the present application and is not intended to limit the present application. For those skilled in the art, the present application can have various modifications and changes. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1. An electronic expansion valve characterized by, The electronic expansion valve comprises: a valve body assembly having a receiving cavity (42), the valve body assembly being provided with a valve port (41) and a communication hole, the valve port and the communication hole being in communication with the receiving cavity (42) respectively; a valve needle assembly (60) arranged in the receiving cavity (42), the valve needle assembly (60) being arranged corresponding to the valve port (41), the valve needle assembly (60) being movable relative to the valve port (41) to adjust the flow at the valve port (41); a connecting pipeline (50) connected with the valve body assembly, the connecting pipeline (50) being in communication with the receiving cavity (42), when the electronic expansion valve is in a full-closed state, there is a gap between the valve needle assembly (60) and the valve port, and the fluid in the connecting pipeline (50) can communicate with the receiving cavity (42) through the gap; wherein the minimum diameter of the valve port (41) is between 4.5-9mm.

2. The electronic expansion valve according to claim 1, characterized in that The valve port (41) has oppositely arranged first and second flow-through ports (4121, 4122), the first flow-through port (4121) is arranged close to the valve needle assembly (60), the diameter of the valve port (41) between the first and second flow-through ports (4121, 4122) gradually decreases from the first flow-through port (4121) to the second flow-through port (4122), one end of the valve needle assembly (60) towards the valve port (41) forms a sealing end, the diameter of the first flow-through port (4121) is greater than that of the sealing end, the diameter of the second flow-through port (4122) is less than or equal to that of the sealing end, and the sealing end can move between the first and second flow-through ports (4121, 4122) to adjust the flow area of the valve port (41).

3. The electronic expansion valve according to claim 2, characterized in that The valve needle assembly (60) has an upper limit position and a lower limit position, when the valve needle assembly (60) is in the upper limit position, the sealing end is located on the side of the first flow-through port (4121) away from the second flow-through port (4122), and when the valve needle assembly (60) is in the lower limit position, the sealing end is located between the first and second flow-through ports (4121, 4122).

4. The electronic expansion valve according to claim 1, wherein When the electronic expansion valve is in a full-open mode, the flow coefficient Cv of the electronic expansion valve is ≥0.45, wherein, V is the maximum flow rate of the electronic expansion valve, G is the specific gravity of the medium flowing in the electronic expansion valve, P1 is the pressure on the inflow side of the electronic expansion valve, and P2 is the pressure on the outflow side of the electronic expansion valve.

5. The electronic expansion valve according to claim 1, wherein The electronic expansion valve further comprises a sound attenuation assembly arranged in the valve body assembly, the sound attenuation assembly comprising a sound attenuation structure having a flow-through area and a decomposition area, bubbles in the fluid flowing through the sound attenuation assembly can be decomposed through the decomposition area.

6. The electronic expansion valve according to claim 5, wherein The sound attenuation structure comprises a first sound attenuation block (10) and a second sound attenuation block (20), the first sound attenuation block (10) and the second sound attenuation block (20) are arranged in a flow direction of fluid, the first sound attenuation block (10) and the second sound attenuation block (20) are provided with the flow area and the decomposition area, the flow area arranged on the first sound attenuation block (10) corresponds to the decomposition area arranged on the second sound attenuation block (20), and the flow area arranged on the second sound attenuation block (20) corresponds to the decomposition area arranged on the first sound attenuation block (10).

7. The electronic expansion valve according to claim 6, characterized in that The first sound attenuation block (10) and the second sound attenuation block (20) are filter screen sintered blocks, the first sound attenuation block (10) is provided with at least one first through hole (11), and the second sound attenuation block (20) is provided with at least one second through hole (21), the first through hole (11) forms the flow area on the first sound attenuation block (10), and the second through hole (21) forms the flow area on the second sound attenuation block (20).

8. The electronic expansion valve according to claim 7, characterized in that The first through hole (11) and the second through hole (21) do not have an overlapping part in the projection along the fluid flow direction.

9. The electronic expansion valve according to claim 7, wherein The total flow area of the first through hole (11) and the plurality of second through holes (21) is greater than or equal to 50% of the flow area of the valve port (41).

10. The electronic expansion valve according to claim 7, wherein The pore size of the first sound attenuation block (10) and the second sound attenuation block (20) is 0.11-0.35mm.

11. The electronic expansion valve according to claim 7, wherein The porosity of the first sound attenuation block (10) and the second sound attenuation block (20) is 45%-95%.

12. The electronic expansion valve according to claim 7, wherein The first sound attenuation block (10) of the sound attenuation assembly is arranged close to the valve port (41), and the valve port (41) and the first sound attenuation block (10) have a spacing, the distance between the port of the valve port (41) close to the first sound attenuation block (10) and the first sound attenuation block (10) is L1, and L1 is greater than or equal to 1mm.

13. The electronic expansion valve according to claim 7, wherein The first sound attenuation block (10) is arranged close to the valve port (41), and the flow area of the first through hole (11) is 0.3 times to 1 times of the flow area at the valve port (41).

14. The electronic expansion valve of claim 7, wherein, The flow area of the first through hole (11) is S1, the diameter of the first through hole (11) is R1, the distance between the first sound attenuation block (10) and the second sound attenuation block (20) is L2, and π*R1*L2 is greater than or equal to 1.2*S1.

15. The electronic expansion valve of claim 7, wherein, The diameter of the first sound attenuation block (10) is more than 2 times of the flow area at the valve port (41).

16. The electronic expansion valve according to claim 6, wherein The support ring (30) is arranged between the first sound attenuation block (10) and the second sound attenuation block (20), the support ring (30) is arranged on the periphery of the second sound attenuation block (20), and the support ring (30) avoids the flow area.

17. The electronic expansion valve according to claim 16, wherein The support ring (30) has a flow channel, the area of the flow channel is S2, the maximum projection area of the sound attenuation structure along the flow direction is S3, and S2 is greater than or equal to 0.8*S3.

18. The electronic expansion valve of claim 6, wherein, The first sound attenuation block (10) and the second sound attenuation block (20) are provided with a bracket (31), the bracket (31) has a mounting plate (312), the first sound attenuation block (10) is arranged on one end of the mounting plate (312) close to the valve port (41), and the mounting plate (312) is provided with a flow-through hole (314) and a mounting ring (313), and the mounting ring (313) is used for mounting the second sound attenuation block (20).

19. The electronic expansion valve according to any one of claims 5 to 18, characterized in that When the minimum diameter at the valve port (41) is between 6-9mm, the flow coefficient Cv of the electronic expansion valve is greater than or equal to 0.6 when the electronic expansion valve is in full open mode, wherein, V is the maximum flow rate of the electronic expansion valve, G is the specific gravity of the medium flowing in the electronic expansion valve, P1 is the pressure on the inflow side of the electronic expansion valve, and P2 is the pressure on the outflow side of the electronic expansion valve.

20. An air conditioning system comprising: The air conditioning system comprises a compressor (100), an indoor heat exchanger (200) and an outdoor heat exchanger (300) which are communicated with each other, the indoor heat exchanger (200) comprises a first heat exchanger (210) and a second heat exchanger (220), and an electronic expansion valve (400) is arranged between the first heat exchanger (210) and the second heat exchanger (220), wherein the electronic expansion valve (400) is the electronic expansion valve according to any one of claims 1 to 19.

21. The air conditioning system of claim 20, wherein, The first heat exchanger (210) and the second heat exchanger (220) are connected through a flow-through pipeline, the electronic expansion valve (400) is arranged on the flow-through pipeline, a connecting pipeline (50) of the electronic expansion valve (400) is connected with the flow-through pipeline, and the caliber of a valve port (41) of the electronic expansion valve is greater than the inner diameter of the flow-through pipeline.

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