Electronic expansion valve and air conditioning system having same

Abstract

The present application provides an electronic expansion valve and an air conditioning system having same. The electronic expansion valve comprises: a valve body assembly, having an accommodating cavity, a valve port and a communication hole being provided on a valve body, and the valve port and the communication hole each being in communication with the accommodating cavity; a valve needle assembly, disposed in the accommodating cavity, the valve needle assembly being disposed corresponding to the valve port, and the valve needle assembly being movable relative to the valve port, so as to adjust the flow at the valve port; and a connection tube, connected to the valve body assembly, the connection tube being in communication with the accommodating cavity, such that when the electronic expansion valve is in a fully closed state, a gap exists between the valve needle assembly and the valve port, so that a fluid in the connection tube can communicate with the accommodating cavity by means of the gap, a minimum diameter at the valve port ranging between 4.5-9 mm. By means of the technical solution of the present application, the problem in the existing technology that a control valve throttles a refrigerant fluid can be solved.

Description

Electronic expansion valve and air conditioning system having the same

[0001] The present application claims priority to the patent application No. 2024207377262, filed on April 10, 2024, with the China National Intellectual Property Office and titled "Electronic expansion valve and air conditioning system having the same"; the patent application No. 202410431789X, filed on April 10, 2024, with the China National Intellectual Property Office and titled "Electronic expansion valve and air conditioning system having the same"; the patent application No. 2025101120583, filed on January 23, 2025, with the China National Intellectual Property Office and titled "Electronic expansion valve and air conditioning system having the same"; and the patent application No. 2025201645854, filed on January 23, 2025, with the China National Intellectual Property Office and titled "Electronic expansion valve and air conditioning system having the same". TECHNICAL FIELD

[0002] The present application relates to the technical field of air conditioners, in particular to an electronic expansion valve and an air conditioning system having the same. BACKGROUND

[0003] At present, in an 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 cooling and heating mode and a dehumidification mode, when the air conditioning system is in the cooling and heating mode, the control valve is in a fully 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, and then flows into the control valve, the control valve can control the flow of the refrigerant fluid, so that the refrigerant fluid flows 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 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 throttling effect on the fluid, affecting the circulation of the refrigerant fluid. SUMMARY

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

[0006] According to an aspect of the present application, an electronic expansion valve is provided, comprising: a valve body assembly having a receiving cavity, a valve port and a communication hole being arranged on the valve body assembly and being communicated with the receiving cavity respectively; a valve needle assembly arranged in the receiving cavity, the valve needle assembly being arranged corresponding to the valve port and being movable 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 being 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 be communicated with the receiving cavity through the gap; wherein the minimum diameter of the valve port is between 4.5-9mm.

[0007] By applying the technical solution of the present application, the electronic expansion valve comprises the valve body assembly, the valve needle assembly and the connecting pipeline, the valve needle assembly can adjust the flow rate at the valve port, and when the electronic expansion valve is in a full-closed state, there is a gap between the valve needle assembly and the valve port, the fluid entering the receiving cavity through the connecting pipeline can flow to the connecting pipeline on the other side 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, so that the electronic expansion valve can be applied as a control valve in the air conditioning system to throttle the refrigerant fluid to realize the dehumidification function of the air conditioning system, and the valve needle assembly can adjust the flow rate at the valve port, and according to the actual needs of the air conditioning system, the flow rate through the electronic expansion valve can be adjusted to meet the needs of air conditioners with different refrigerating capacities. By setting the minimum diameter of the valve port to be between 4.5-9mm, it can be applied to the flow requirements of the mainstream household split indoor heat exchanger flow pipeline, ensuring that it does not throttle while also preventing the minimum diameter of the valve port from being too large to 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 between the first and second flow-through ports 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 the diameter of the sealing end, the diameter of the second flow-through port is less than or equal to the diameter of the sealing end, and the sealing end can move between the first and second flow-through ports to adjust the flow area at the valve port. By 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, and when the valve needle assembly is in the lower limit position, the sealing end is located between the first and second flow-through ports. By the above arrangement, the electronic expansion valve can have a certain flow rate in a 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 the full open mode, the flow coefficient Cv of the electronic expansion valve is ≥ 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.

[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, the sound attenuation structure has a flow-through area and a decomposition area, and bubbles in the fluid flowing through the sound attenuation assembly can be decomposed through the decomposition area. 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 flow direction of the fluid, the first sound attenuation block and the second sound attenuation block are provided with the flow-through area and the decomposition area, at least part of the flow-through area arranged on the first sound attenuation block is correspondingly arranged with the decomposition area arranged on the second sound attenuation block, and at least part of the flow-through area arranged on the second sound attenuation block is correspondingly arranged with the decomposition area arranged on the first sound attenuation block. Through the above arrangement, the area of the decomposition area 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-through area on the first sound attenuation block, and the second through hole forms the flow-through area 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 in the fluid flow direction 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 decomposition area, and the sound attenuation effect of the sound attenuation structure is guaranteed.

[0015] Further, the total flow-through area of the first through hole and the plurality of second through holes is greater than or equal to 50% of the flow-through area of the valve port. Through the above arrangement, it can be prevented that the sound attenuation structure causes excessive throttling to the fluid passing through, and the flow efficiency of the fluid in the air conditioning system 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 while the decomposition effect of the first sound attenuation block and the second sound attenuation block is not affected.

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

[0018] Further, the first sound attenuation block of the sound attenuation assembly is arranged close to the valve port, and the valve port has a spacing with the first sound attenuation block. The 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≥1mm. Through the above setting, the influence of the sound attenuation assembly on fluid flow can be reduced.

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

[0020] Further, the flow area of the first through hole is S1, the diameter of the first through hole is R1, the distance between the first sound attenuation block and the second sound attenuation block is L2, and π*R1*L2≥1.2*S1. Through the above setting, the flow efficiency of the fluid can be improved.

[0021] Further, the diameter of the first sound attenuation block is more than 2 times the flow area at the valve port. Through the above setting, 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 the circumference of the second sound attenuation block, and the support ring avoids the flow area. Through the above setting, the support ring can prevent the throttling of the fluid when the fluid flows through the sound attenuation structure.

[0023] Further, the support ring 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≥0.8*S3. Through the above setting, the flow resistance of the fluid when flowing through the support ring can be reduced while ensuring the supporting effect of the support ring on the first sound attenuation block, and the smoothness of the fluid flow can be ensured.

[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, and the mounting plate is provided with a flow hole and a mounting ring. The mounting ring is used to mount the second sound attenuation block. Through the above setting, the stability of the installation 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 6-9mm, the flow coefficient Cv of the electronic expansion valve is ≥0.6 when the electronic expansion valve is in full open mode, 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 present application, an air conditioning system is provided, which comprises a compressor, an indoor heat exchanger and an outdoor heat exchanger in communication with each other, the indoor heat exchanger comprises a first heat exchanger and a second heat exchanger, and an electronic expansion valve is arranged between the first heat exchanger and the second heat exchanger, the electronic expansion valve 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 is in a fully open state, the valve port does not throttle the refrigerant fluid, 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 a dehumidification mode, the first heat exchanger is a condenser, the refrigerant fluid releases heat through the first heat exchanger, and the refrigerant fluid flows out of the first heat exchanger and enters the electronic expansion valve, the electronic expansion valve can control the flow of the refrigerant fluid, so that the refrigerant fluid throttles and depressurizes through the electronic expansion valve at a small flow rate, at this time the second heat exchanger acts as an evaporator to absorb heat, and the fan drives the indoor humid air to pass through the heat-absorbing second heat exchanger to make the water vapor condense, thereby achieving the dehumidification effect, and at the same time the indoor first heat exchanger acts as a condenser to make the indoor air temperature rise, that is, the condensed water vapor and the air released by the condenser in the indoor are in circulation under the action of the fan, thereby achieving the effect of dehumidification without temperature drop and improving the user experience.

[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 the diameter of the valve port of the electronic expansion valve is greater than the inner diameter of the flow pipe. Through the above arrangement, the pressure drop of the fluid flowing through the electronic expansion valve between the first heat exchanger and the second heat exchanger can be avoided, thereby further ensuring the flow efficiency of the refrigerant fluid flowing through the electronic expansion valve. BRIEF DESCRIPTION OF DRAWINGS

[0028] The drawings constituting a part of the specification of the present application are used to provide further understanding of the present application, the illustrative embodiments of the present application and the description thereof are used to explain the present application, and do not constitute improper limitations on the present application. In the drawings:

[0029] Fig. 1 shows a structural schematic diagram of the electronic expansion valve provided by the present application;

[0030] Fig. 2 shows a partial enlarged view of A in Fig. 1;

[0031] Fig. 3 shows a structural schematic diagram of the sound attenuation assembly provided by the present application;

[0032] Fig. 4 shows a top view of the first sound attenuation block provided by the present application;

[0033] Fig. 5 shows a top view of the support ring provided by the present application;

[0034] Fig. 6 shows a top view of the second sound-absorbing block provided by the present application;

[0035] Fig. 7 shows an enlarged view of part B in Fig. 2;

[0036] Fig. 8 shows a structural schematic view of the bracket cooperating with the electronic expansion valve provided by the present application;

[0037] Fig. 9 shows a schematic view of the air conditioning system provided by the present application.

[0038] In the above drawings, the following reference signs are used: 10, first sound-absorbing block; 11, first through hole; 20, second sound-absorbing block; 21, second through hole; 30, support ring; 31, bracket; 311, blocking ring; 312, mounting plate; 313, mounting ring; 314, flow-through hole; 40, valve body; 41, valve port; 411, straight section; 412, tapered section; 4121, first flow-through port; 4122, second flow-through port; 42, accommodating cavity; 50, connecting pipeline; 60, valve needle assembly; 100, compressor; 200, indoor heat exchanger; 210, first heat exchanger; 220, second heat exchanger; 300, outdoor heat exchanger; 400, electronic expansion valve. DETAILED DESCRIPTION

[0039] 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 of the present application. The following description of at least one exemplary embodiment is merely illustrative in nature and in no way limits any application or use of the present application. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative work fall within the scope of protection of the present application.

[0040] As shown in Fig. 1, the present application provides an electronic expansion valve, which comprises a valve body assembly, a valve needle assembly 60 and a connecting pipeline 50. The valve body assembly has an accommodating cavity 42, and the valve body assembly is provided with a valve port 41 and a communication hole, which respectively communicate with the accommodating cavity 42. The valve needle assembly 60 is arranged in the accommodating cavity 42, and the valve needle assembly 60 is arranged corresponding to the valve port 41. The valve needle assembly 60 can move relative to the valve port 41 to adjust the flow rate at the valve port 41. The connecting pipeline 50 is connected with the valve body assembly, and the connecting pipeline 50 communicates with the accommodating 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 accommodating cavity 42 through the gap. The minimum diameter at the valve port 41 is between 4.5-9 mm.

[0041] According to the technical solution of the present application, the electronic expansion valve comprises a valve body assembly, a valve needle assembly 60 and a connecting pipeline 50. The valve needle assembly 60 can adjust the flow rate at the valve port 41. When the electronic expansion valve is in a fully closed state, there is a gap between the valve needle assembly 60 and the valve port 41. The fluid entering the accommodation cavity 42 through the connecting pipeline 50 can flow to the other side of the connecting pipeline 50 through the gap between the valve needle assembly 60 and the valve port 41, that is, the electronic expansion valve can have a certain flow capacity at this time. Therefore, the electronic expansion valve can be used as a control valve in an air conditioning system to throttle the refrigerant fluid to achieve the dehumidification function of the air conditioning system. In addition, the valve needle assembly 60 can adjust the flow rate at the valve port 41 to adjust the flow rate through the electronic expansion valve according to the actual needs of the air conditioning system to meet the needs of air conditioners with different refrigerating capacities.

[0042] 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 selected pipe diameter is too large, it will waste materials and not match the refrigerating capacity of the whole machine, affecting the performance of the whole machine. If the selected pipe diameter is too small, the pressure drop will be too large, also affecting the performance of the whole machine. The main stream of the current air conditioner refrigerating capacity is between 1-3 tons. The outer diameter of the flow pipeline between the indoor heat exchangers of the air conditioner 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 the present 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 current mainstream household split indoor heat exchanger flow pipeline. Since the valve is fully open during normal air conditioning operation, if the minimum diameter of the valve port 41 is too small, it will be throttled significantly, affecting the performance of the whole machine. 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 rate is too large when fully open, affecting the operating efficiency of the whole machine. In the present 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 indoor heat exchanger flow pipeline, which can meet the flow requirements of the current mainstream household split indoor heat exchanger flow pipeline, ensuring that there is no throttling while preventing the minimum diameter of the valve port 41 from being too large to affect the operating efficiency of the whole machine. Through the above setting, the flow capacity of the electronic expansion valve in the fully open state can be ensured, which can ensure the flow efficiency of the electronic expansion valve while preventing the electronic expansion valve 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.

[0043] In some embodiments of the present application, the valve body assembly comprises a valve body 40, and the valve port and / or the communication hole can be integrally arranged with the valve body 40.

[0044] In some other embodiments of the present application, the valve body assembly comprises a valve body 40 and a valve seat, and the valve body 40 and the valve seat are fixedly connected, and the valve port and / or the communication hole can be arranged separately from the valve body 40.

[0045] Specifically, when the electronic expansion valve is in the full 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 in the full open state. When the Cv value is less than 0.45, the flow capacity of the fluid will be throttled when the electronic expansion valve is fully open, that is, the flow capacity of the electronic expansion valve in the full open state is not enough, which affects the flow between the indoor side heat exchangers and the overall performance. 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 overall machine when the valve is used in normal working conditions of the air conditioner.

[0046] Referring to FIG. 2, the valve port 41 has a first flow port 4121 and a second flow port 4122 arranged oppositely, 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, and the diameter of the second flow port 4122 is less than or equal to the diameter of the sealing end. 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 segment 411 and a tapered segment 412 which are in communication with each other, the straight segment 411 is arranged away from the valve needle assembly 60, and the tapered segment 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 segment 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 segment 412 will change with the movement of the valve needle assembly 60 in the tapered segment 412. Thus, the flow area of the fluid at the valve port 41 can be adjusted, and the flow of the fluid can be adjusted.

[0047] In the conventional technical solution, the control valve is usually a dehumidification electromagnetic valve, which 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, so that the electromagnetic valve can flow through a small flow of refrigerant fluid in the full-closed mode. However, this setting mode will cause the flow of 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 will change, the dehumidification effect is poor, and the size of the throttling hole may not be accurate due to the stamping formation, which may cause the instability of the dehumidification electromagnetic valve throttling effect, causing the overheating degree to fluctuate, affecting the energy efficiency of the air conditioning dehumidification operation, and the electromagnetic valve will also have 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 conventional 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, which can be used for multiple specifications of the valve, and can accurately control the flow in the dehumidification working condition, that is, in the full-closed state, so as to accurately control the dehumidification amount and the heating amount, improve the dehumidification effect without temperature drop, improve the user experience, and different air conditioning models can use one dehumidification electronic expansion valve, which improves the standardization of key components and improves the applicability of the electronic expansion valve.

[0048] 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. Specifically, as shown in FIG. 7, 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 conventional 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 conventional 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.

[0049] 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 area and a decomposition area, the bubbles in the fluid flowing through the sound attenuation assembly can be decomposed through the decomposition area. Through the above arrangement, the larger bubbles in the two-phase fluid flowing through the decomposition area will be decomposed into smaller bubbles in the decomposition area, 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 area, which is easy to cause the dirty blockage of the decomposition area, by setting the flow-through area, the impurities can flow through the sound attenuation assembly through the flow-through area, 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.

[0050] Referring to FIGS. 3 to 6, 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 area and a decomposition area, at least part of the flow-through area arranged on the first sound attenuation block 10 is arranged in correspondence with the decomposition area arranged on the second sound attenuation block 20, and at least part of the flow-through area arranged on the second sound attenuation block 20 is arranged in correspondence with the decomposition area 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 area on the first sound attenuation block 10 or the second sound attenuation block 20 after flowing through the flow-through area 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 improving the noise reduction capability of the sound attenuation assembly.

[0051] 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.

[0052] 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.

[0053] 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.

[0054] 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.

[0055] In different embodiments, the Cv values of the valve port 41 with different diameters are as follows:

[0056] Example 1

[0057] 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;

[0058] Example 2

[0059] 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;

[0060] Example 3

[0061] 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.

[0062] Embodiment 4

[0063] 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.

[0064] 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.

[0065] 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.

[0066] 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%.

[0067] 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.

[0068] 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.

[0069] 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.

[0070] 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.

[0071] In a specific embodiment of the present application, a 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 at the periphery of the second sound attenuation block 20, and the support ring 30 avoids the flow passage area. By arranging the support ring 30, the relative displacement of the first sound attenuation block 10 and the second sound attenuation block 20 can be limited by the support ring 30, preventing the first sound attenuation block 10 or the second sound attenuation block 20 from being displaced under the impact of the fluid, ensuring the stability of the first sound attenuation block 10 and the second sound attenuation block 20, and by arranging the support ring 30 to avoid the flow passage area, the support ring 30 can prevent the fluid from being throttled when the fluid flows through the sound attenuation structure.

[0072] Specifically, the support ring 30 has a flow passage with an area S2, and the sound attenuation structure has a maximum projected area S3 along the flow direction, and S2≥0.8*S3. When the area S2 of the flow passage is less than 0.8*S3, the flow passage of the support ring 30 has a smaller flow area, and the fluid will experience a larger 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 sound attenuation block 10, the second sound attenuation block 20, and the support ring 30. In the present 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 sound attenuation block 10, thereby ensuring the smoothness of the fluid flow.

[0073] The size of the above-mentioned sound attenuation structure can reduce the impact on the fluid flow caused by arranging the sound attenuation structure in the valve body 40 of the electronic expansion valve provided in the present application, and can avoid excessive throttling; at the same time, it can also reduce the noise generated by the indoor electronic expansion valve during operation.

[0074] As shown in FIG. 8, in another embodiment of the present application, a support 31 is arranged between the first sound attenuation block 10 and the second sound attenuation block 20, the support 31 has a mounting plate 312, the first sound attenuation block 10 is arranged at one end of the mounting plate 312 close to the valve port 41, the mounting plate 312 is provided with a flow hole 314 and a mounting ring 313, and the mounting ring 313 is used to mount the second sound attenuation block 20. The support 31 also has a blocking ring 311 connected to the mounting plate 312, the first sound attenuation block 10 and the second sound attenuation block 20 are separated by the blocking ring 311, the mounting ring 313 has a mounting hole, and the second sound attenuation block 20 is arranged in the mounting hole. In this way, the displacement of the second sound attenuation block 20 under the impact of the fluid can be prevented, and the stability of the sound attenuation assembly installation can be further improved. Furthermore, the flow hole 314 arranged on the mounting plate 312 can also serve as a flow passage for impurities, preventing the sound attenuation assembly from being blocked and ensuring the flow performance of the fluid.

[0075] The application also provides an air conditioning system. The electronic expansion valve is applied to the air conditioning system shown in FIG. 9. The air conditioning system comprises a compressor 100, an indoor heat exchanger 200 and an outdoor heat exchanger 300 which are in communication 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. 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 fully 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 for heat release or heat absorption. 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.

[0076] 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 of 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 will 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.

[0077] Specifically, in the 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 pressure drop of the fluid flowing through the connecting pipe 50 and the electronic expansion valve 400 provided in the application is avoided, and the flow efficiency of the refrigerant fluid flowing through the electronic expansion valve 400 is further ensured.

[0078] The electronic expansion valve provided in the 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 application has the following advantages:

[0079] 1. By setting the minimum diameter at the valve port 41 to be larger than the inner diameter of the flow passage, throttling of the fluid when passing through the electronic expansion valve is prevented, and the flow capacity of the fluid in the air conditioning system is ensured.

[0080] 2. When the dehumidification electromagnetic valve is operating in a dehumidification mode, the flow rate is fixed at a certain flow rate and cannot be adjusted, 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.

[0081] 3. When the dehumidification electromagnetic valve is in a full-off mode, a small flow rate is required to be achieved by the size of the throttling small hole on the internal throttling piece. The throttling small hole is mostly stamped, and the size precision is poor. When operating in a dehumidification mode, the dehumidification electromagnetic valve throttling is unstable, resulting in fluctuations in superheat, affecting the dehumidification operation efficiency. The use of a dehumidification electronic expansion valve can accurately control the flow rate, and the internal related parts have high machining and matching precision, and the throttling stability is high.

[0082] 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 an electronic expansion valve can effectively reduce mechanical noise, and by setting a sound attenuation structure in the electronic expansion valve, the noise caused by bubbles when the refrigerant fluid passes through the electronic expansion valve can be further reduced, ensuring the user experience.

[0083] 5. The flow rate of the electronic expansion valve when fully open and in a small opening flow mode can be accurately controlled according to the requirements of the air conditioning unit. One valve can be used for multiple specifications of machine models. One dehumidification electronic expansion valve can be used for different refrigeration capacity models, improving the standardization of key components and improving the applicability of the electronic expansion valve.

[0084] 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 according to 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, and / or components, but do not preclude the presence or addition of one or more other features, steps, operations, elements, components, and / or groups thereof.

[0085] The foregoing is considered as illustrative only of the principles of the application. Other variations and modifications are possible in light of the above teachings. Therefore, the scope of the application is not intended to be limited to the particular embodiments described, but is to be accorded the broadest scope consistent with the scope of the claims. Without intent to limit the scope of the application, exemplary embodiments of the application are set forth below. It is, however, contemplated that other embodiments might fall within the scope of the application. To the extent that they are inconsistent, the reference in this specification to singular comprise a reference to the plural or vice versa and male and female referents include both male and female unless explicitly stated otherwise. Furthermore, to the extent that "comprising", "including", containing", listed

[0086] In the description of the present application, it is to be understood that the orientation or positional relationships indicated by terms such as "front", "back", "up", "down", "left", "right", "lateral", "vertical", "horizontal", "top", "bottom", and the like are generally based on the orientation or positional relationships shown in the drawings, and are merely intended to facilitate the description of the present application and simplify the description, and do not indicate or imply that the devices or elements referred to must have a particular orientation or be constructed and operated in a particular orientation, and therefore should not be construed as limiting the scope of protection of the present application. The orientation terms "inner", "outer" refer to the inner and outer relative to the contour of the components themselves.

[0087] For the convenience of description, spatial relative terms such as "above", "upper", "top", "up", "lower", "bottom", and the like can be used herein to describe the spatial relationship of one device or feature to another device or feature as shown in the drawings. It should be understood that the spatial relative terms are intended to include different orientations of the devices in use or operation in addition to the orientation of the devices described in the drawings. For example, if the devices in the drawings are turned over, the device described as "above" or "above" the other device or structure will be positioned "below" or "below" the other device or structure. 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.

[0088] In addition, it should be noted that the use of "first", "second", and the like words to qualify elements does not have a special meaning, and therefore should not be construed as limiting the scope of protection of the present application, unless otherwise stated.

[0089] The above descriptions are only the preferred embodiments of the present application, and are not intended to limit the present application. The present application can have various modifications and changes for those skilled in the art. Any modifications, equivalent replacements, improvements, 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 in that: The electronic expansion valve comprises: A valve body assembly having an accommodating cavity (42), wherein a valve port (41) and a communicating hole are provided on the valve body assembly, wherein the valve port and the communicating hole are respectively communicated with the accommodating cavity (42); A valve needle assembly (60) is disposed in the accommodating cavity (42), the valve needle assembly (60) being disposed corresponding to the valve port (41), and the valve needle assembly (60) being movable relative to the valve port (41) to adjust the flow rate at the valve port (41); a connecting pipeline (50) connected to the valve body assembly, the connecting pipeline (50) being in communication with the accommodating chamber (42); when the electronic expansion valve is in a fully closed state, a gap is provided between the valve needle assembly (60) and the valve port, and the fluid in the connecting pipeline (50) can be in communication with the accommodating chamber (42) through the gap; The minimum diameter of the valve port (41) is between 4.5 and 9 mm.

2. The electronic expansion valve according to claim 1, characterized in that: The valve port (41) has a first flow port (4121) and a second flow port (4122) that are relatively arranged. 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 valve needle assembly (60) forms a sealing end toward one end of the valve port (41). The diameter of the first flow port (4121) is greater than the diameter of the sealing end, and the diameter of the second flow port (4122) is less than or equal to the diameter of the sealing end. 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).

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 at the upper limit position, the sealing end is located on the side of the first flow port (4121) away from the second flow port (4122). When the valve needle assembly (60) is at the lower limit position, the sealing end is located between the first flow port (4121) and the second flow port (4122).

4. The electronic expansion valve according to claim 1, characterized in that: When the electronic expansion valve is in the fully open mode, the flow coefficient Cv of the electronic expansion valve is ≥ 0.

45. in, 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 inlet side of the electronic expansion valve, and P2 is the pressure on the outlet side of the electronic expansion valve.

5. The electronic expansion valve according to claim 1, characterized in that: The electronic expansion valve also includes a silencer component, which is arranged in the valve body component. The silencer component includes a silencer structure, which has a circulation area and a decomposition area. Bubbles in the fluid flowing through the silencer component can be decomposed through the decomposition area.

6. The electronic expansion valve according to claim 5, characterized in that: The muffler structure comprises a first muffler block (10) and a second muffler block (20); the first muffler block (10) and the second muffler block (20) are arranged at intervals along the flow direction of the fluid; the first muffler block (10) and the second muffler block (20) are both provided with the flow area and the decomposition area; the flow area at least partially provided on the first muffler block (10) is provided correspondingly to the decomposition area provided on the second muffler block (20); and the flow area at least partially provided on the second muffler block (20) is provided correspondingly to the decomposition area provided on the first muffler block (10).

7. The electronic expansion valve according to claim 6, characterized in that: The first muffler block (10) and the second muffler block (20) are filter mesh sintered blocks. The first muffler block (10) has at least one first through hole (11), and the second muffler block (20) has at least one second through hole (21). The first through hole (11) forms a flow area on the first muffler block (10), and the second through hole (21) forms a flow area on the second muffler block (20).

8. The electronic expansion valve according to claim 7, characterized in that: The projections of the first through hole (11) and the second through hole (21) along the fluid flow direction have no overlapping parts.

9. The electronic expansion valve according to claim 7, characterized in that: 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, characterized in that: The pore size of the first muffler block (10) and the second muffler block (20) is 0.11-0.35 mm.

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

12. The electronic expansion valve according to claim 7, characterized in that: The first muffler block (10) of the muffler assembly is arranged close to the valve port (41), and there is a gap between the valve port (41) and the first muffler block (10). The distance between the port of the valve port (41) close to the first muffler block (10) and the first muffler block (10) is L1, and L1 is ≥ 1 mm.

13. The electronic expansion valve according to claim 7, characterized in that: The first muffler 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).

14. The electronic expansion valve according to claim 7, characterized in that: 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 silencer block (10) and the second silencer block (20) is L2, and π*R1*L2≥1.2*S1.

15. The electronic expansion valve according to claim 7, characterized in that: The diameter of the first muffler block (10) is more than twice the flow area at the valve port (41).

16. The electronic expansion valve according to claim 6, characterized in that A support ring (30) is provided between the first silencer block (10) and the second silencer block (20); the support ring (30) is provided on the periphery of the second silencer block (20), and the support ring (30) is provided to avoid the circulation area.

17. The electronic expansion valve according to claim 16, characterized in that: The support ring (30) has a circulation channel, the area of ​​the circulation channel is S2, the maximum projection area of ​​the silencer structure along the circulation direction is S3, and S2≥0.8*S3.

18. The electronic expansion valve according to claim 6, characterized in that A bracket (31) is provided between the first silencer block (10) and the second silencer block (20), the bracket (31) having a mounting plate (312), the first silencer block (10) being provided at one end of the mounting plate (312) close to the valve port (41), the mounting plate (312) being provided with a flow hole (314) and a mounting ring (313), the mounting ring (313) being used for mounting the second silencer 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 and 9 mm, and when the electronic expansion valve is in a fully open mode, the flow coefficient Cv of the electronic expansion valve is ≥ 0.6, in, 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 inlet side of the electronic expansion valve, and P2 is the pressure on the outlet side of the electronic expansion valve.

20. An air conditioning system, characterized in that: The air-conditioning system includes a compressor (100), an indoor heat exchanger (200), and an outdoor heat exchanger (300) that are interconnected. The indoor heat exchanger (200) includes a first heat exchanger (210) and a second heat exchanger (220). An electronic expansion valve (400) is provided between the first heat exchanger (210) and the second heat exchanger (220). The electronic expansion valve (400) is the electronic expansion valve according to any one of claims 1 to 19.

21. The air conditioning system according to claim 20, characterized in that The first heat exchanger (210) and the second heat exchanger (220) are connected via a circulation pipeline, the electronic expansion valve (400) is arranged on the circulation pipeline, the connecting pipeline (50) of the electronic expansion valve (400) is connected to the circulation pipeline, and the diameter of the valve port (41) of the electronic expansion valve is larger than the inner diameter of the circulation pipeline.

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