One-way reverse-opening passive expansion valve

Abstract

The invention relates to a one-way reverse-open passive expansion valve applied to the field of air conditioner valves, a valve needle, a large spring and a small spring are arranged on one side of a sliding core, the control effect of forward throttling and reverse full-open of a refrigerant is achieved, an air conditioner condenser and an evaporator are connected with two different expansion valves respectively, and in the refrigerating or heating process, the two expansion valves are connected with one another in a one-way reverse-open mode. When a refrigerant passes through the first expansion valve in the forward direction, throttling control over the refrigerant is achieved through deformation of the large spring and the small spring, then after the refrigerant passes through the power device and is cooled, the refrigerant passes through the other expansion valve in the reverse direction, the valve needle and the sliding core form a full-open state, and the refrigerant rapidly passes through and enters a condenser or an evaporator; an auxiliary flow controller is further arranged in the expansion valve, when the elastic performance of the large spring and the small spring is reduced, deformation of the large spring and the small spring is corrected, and the control precision of the refrigerant flow is effectively kept.

Description

Technical Field

[0001] The invention relates to an expansion valve, in particular to a one-way reverse opening passive expansion valve used in the field of air conditioning valves. Background Art

[0002] In variable frequency air conditioning systems, existing refrigeration expansion valve technologies mainly include two categories: electronic expansion valves and thermal expansion valves. Electronic expansion valves are composed of a stepper motor and an action execution structure composed of a coil and magnetic materials. They have a complex structure and high material and processing costs. During use, they are prone to operating failures due to unstable electronic equipment or stuck structures that do not rotate, affecting the performance of the expansion valve. The working principle of the thermal expansion valve is to control the valve opening by sensing external temperature changes. They have a complex structure, low control accuracy, and slow response speed.

[0003] To solve the above problems, the specification of Chinese patent CN202410034015.3 discloses a passive adaptive cooling and heating bidirectional air-conditioning expansion valve, which utilizes the pressure of the refrigerant to compress the small spring and the main spring in sequence, open the gap between the valve needle and the center hole of the sliding core, allow the refrigerant to pass, and rely on the main spring to generate a rebound force to offset the refrigerant pressure and automatically reach a new balance point, so that the refrigerant maintains the flow rate of this balance point to flow. At the same time, the setting of the small spring can effectively control the flow change under a smaller pressure, so that the conversion between large and small flow rates is smooth and smooth. Compared with the existing electronic expansion valve, this application reduces the electronic control failure point and extends the service life. The opening of the gap between the valve needle and the center hole of the sliding core can respond in real time according to the change of the refrigerant pressure, reducing the pressure shock to the refrigeration system caused by the sudden change of the compressor speed.

[0004] However, the above-mentioned air-conditioning expansion valve mainly relies on the elastic force of the spring to control the flow rate of the refrigerant. However, no matter it is the small spring or the main spring, their elastic properties will decrease after multiple deformations. After long-term use, it is easy to cause the flow rate of the refrigerant in the later period to become larger than that in the earlier period under the same pressure difference of the refrigerant, and the control accuracy of the expansion valve on the refrigerant will decrease. Summary of the invention

[0005] In view of the above-mentioned prior art, the technical problem to be solved by the present invention is that the existing air-conditioning expansion valve is prone to reduce the refrigerant control accuracy due to the degradation of spring performance after long-term use.

[0006] In order to solve the above problems, the present invention provides a one-way reverse opening passive expansion valve, comprising a conduit and a pair of end heads, wherein both ends of the conduit are fixedly connected to the pair of end heads through valve seats, and ends of the pair of end heads that are away from each other are fixedly connected to a delivery pipe, and a sliding core is slidably connected inside the conduit, and an outer rotor core, an inner rotor core, a valve needle, a large spring and a small spring are arranged inside one of the end heads;

[0007] An auxiliary throttle is also provided inside the end with an outer rotor core, and the auxiliary throttle includes an electrical box, an outer flow tube, an inner flow tube, an inner correction frame and an outer correction frame. One end of the outer correction frame movably penetrates the inner rotor core and extends into its inner cavity. The inner correction frame is movably connected between the other end of the outer correction frame and the outer flow tube. The electrical box is provided on the outside of the end. One end of both the outer flow tube and the inner flow tube are fixedly penetrated through the electrical box and connected to the electrically controlled three-way valve inside the electrical box. The electrically controlled three-way valve is also fixedly connected to the liquid storage bag through a hose. The large spring abuts between the inner rotor core and the inner correction frame, and the small spring abuts between the valve needle and the outer correction frame.

[0008] As a further supplement to the present application, the inner rotor core is slidably connected to the interior of the outer rotor core, a small spring is arranged in the inner cavity of the inner rotor core, one end of the valve needle is located in the inner cavity of the inner rotor core, and the other end thereof moves through the inner rotor core and the outer rotor core and extends to the inside of the conduit.

[0009] As a further supplement to the present application, the outer flow tube is sleeved on the outside of the inner flow tube, and the two do not contact each other. The inner correction frame includes a pressure ring, a sliding sleeve and a plurality of support rods fixedly connected between the two. One end of the sliding sleeve is slidably connected between the outer flow tube and the inner flow tube, and the three are in a sliding sealing state. One end of the large spring abuts against the pressure ring.

[0010] As a further supplement to the present application, a slide groove is provided on the inner wall of the outer flow tube, and a slider is fixedly connected to the end of the sliding sleeve. The slider is slidably connected to the inside of the slide groove. In the initial state, the slider is close to the slide groove and away from the inner wall of the inner correction frame.

[0011] As a further supplement to the present application, the external correction frame includes a pressure plate, a piston and a sliding rod, and the piston is fixedly connected between the pressure plate and the sliding rod, one end of the sliding rod is slidably connected to the inside of the sliding sleeve, and the two are in a sliding sealed state, the pressure plate is located in the inner cavity of the inner rotor core, the piston moves through the inner rotor core and is slidably connected to the inside of it, the small spring abuts between the valve needle and the pressure plate, and in the initial state, the large spring and the small spring are at their original length.

[0012] As a further supplement to the present application, the outer end of the piston is fixedly connected to a limiting ring, and the limiting ring is located on the outer side of the inner rotor core.

[0013] As a further supplement to the present application, the electrically controlled three-way valve is respectively fixedly connected with an inlet, outlet one and outlet two, the outer flow pipe and the inner flow pipe are fixedly passed through the delivery pipe and extend to the inside of the electrical box, the end of the inner flow pipe is fixedly passed through the end of the outer flow pipe and is fixedly connected with outlet one, and a connecting pipe is fixedly connected between the outer flow pipe and outlet two.

[0014] As a further supplement to the present application, a pump body is fixedly connected to the interior of the electrical box, the feed end of the pump body is fixedly connected to a liquid storage bag via a hose, the liquid storage bag is fixedly connected to the interior of the electrical box, and the discharge end of the pump body is fixedly connected to the inlet via a feed pipe.

[0015] As a further supplement to the present application, a flow sensor is fixedly connected to the inside of the delivery pipe near the large spring, a controller is fixedly connected to the inside of the electrical box, and the flow sensor, the electrically controlled three-way valve and the pump body are all electrically connected to the controller.

[0016] In summary, the present application achieves the control effect of forward throttling and reverse full opening of the refrigerant by arranging a valve needle, a large spring and a small spring on one side of the sliding core. The air conditioning condenser and evaporator are respectively connected to two different expansion valves of the present invention. During the cooling or heating process, when the refrigerant passes through the first expansion valve in the forward direction, the throttling control of the refrigerant is achieved through the deformation of the large spring and the small spring. Then the refrigerant passes through the power device to cool it down, and then passes through another expansion valve in the reverse direction. The valve needle and the sliding core form a fully open state, allowing the refrigerant to pass quickly into the condenser or evaporator. In addition, an auxiliary throttler is also provided in the present expansion valve. When the elastic performance of the large spring and the small spring decreases, the deformation of the large spring and the small spring is corrected, so that the control accuracy of the refrigerant flow is effectively maintained. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 This is the installation diagram of the first and second implementation modes of this application;

[0018] Figure 2 It is a stereogram of the first and second embodiments of the present application;

[0019] Figure 3 It is a three-dimensional cross-sectional view of the first and second embodiments of the present application;

[0020] Figure 4 A three-dimensional diagram of the outer rotor core of the first and second embodiments of the present application;

[0021] Figure 5 This is a partial front structure diagram of the first and second embodiments of the present application when used. Figure 1 ;

[0022] Figure 6 This is a partial front structure diagram of the first and second embodiments of the present application when used. Figure 2 ;

[0023] Figure 7 It is a partial three-dimensional cross-sectional view of the second embodiment of the present application;

[0024] Figure 8 A three-dimensional cross-sectional view of an auxiliary throttle according to a second embodiment of the present application;

[0025] Fig. 9 This is a front structural diagram of an electrical box and its internal structure according to the second embodiment of the present application;

[0026] Fig.10 This is a partial front structural schematic diagram of the second implementation mode of the present application;

[0027] Fig.11 This is a partial front structure diagram of the second embodiment of the present application when used. Figure 1 ;

[0028] Fig.12 This is a partial front structure diagram of the second embodiment of the present application when used. Figure 2 .

[0029] Description of the numbers in the figure:

[0030] 1 catheter, 2 end, 3 delivery pipe, 4 valve seat, 5 sliding core, 6 outer rotor core, 601 guide groove, 7 inner rotor core, 8 valve needle, 9 large spring, 10 small spring, 11 electrical box, 12 outer flow pipe, 1201 slide groove, 13 inner flow pipe, 14 inner correction frame, 1401 pressure ring, 1402 support rod, 1403 sliding sleeve, 15 outer correction frame, 1501 pressure plate, 1502 piston, 1503 sliding rod, 16 limiting ring, 17 slider, 18 electric three-way valve, 1801 inlet, 1802 outlet one, 1803 outlet two, 19 liquid storage capsule, 20 connecting pipe, 21 pump body. DETAILED DESCRIPTION

[0031] The following describes two implementation modes of the present application in detail with reference to the accompanying drawings.

[0032] The first implementation method:

[0033] The present invention provides a one-way reverse opening passive expansion valve, please refer to Figure 2 and Figure 3 , comprising a conduit 1 and a pair of end heads 2, both ends of the conduit 1 are fixedly connected to the pair of end heads 2 through a valve seat 4, the ends of the pair of end heads 2 that are away from each other are fixedly connected to a delivery pipe 3, the interior of the conduit 1 is slidably connected to a sliding core 5, one of the end heads 2 is provided with an outer rotor core 6, an inner rotor core 7, a valve needle 8, a large spring 9 and a small spring 10, the outer rotor core 6 is slidably connected to the interior of the end head 2, the inner rotor core 7 is slidably connected to the interior of the outer rotor core 6, the small spring 10 is arranged in the inner cavity of the inner rotor core 7, one end of the valve needle 8 is located in the inner cavity of the inner rotor core 7, and the other end thereof movably passes through the inner rotor core 7 and the outer rotor core 6 and extends to the inner side of the conduit 1, the small spring 10 abuts between the inner cavity wall of the inner rotor core 7 and the valve needle 8, and the large spring 9 abuts between the inner wall of the end head 2 and the inner rotor core 7.

[0034] See also Figure 4The outer end of the outer rotor core 6 is provided with a plurality of evenly distributed guide grooves 601. The end of the valve needle 8 close to the conduit 1 is a cone structure, and its maximum outer diameter is larger than the center hole diameter of the valve needle 8, so that the center hole of the valve needle 8 can be closed. At the same time, when necessary, a gap can be formed between the two to facilitate the circulation of refrigerant.

[0035] When the refrigerant passes through the expansion valve in the forward direction, Figure 5 As shown, in the first stage: the refrigerant enters the conduit 1, pushing the sliding core 5 toward the valve needle 8, so that the tapered end of the valve needle 8 is inserted into the center hole of the sliding core 5, and the sliding core 5 is blocked by the valve seat 4 when moving to the end of the conduit 1. At this time, the valve needle 8 effectively closes the center hole and is difficult to move further; in the second stage: as the refrigerant pressure increases, the pressure on the valve needle 8 will cause the small spring 10 to be compressed first, and the valve needle 8 moves slightly into the inner cavity of the inner rotor core 7, so that the gap between the valve needle 8 and the center hole of the sliding core 5 is slightly opened, and the refrigerant passes through at a small flow rate, and then passes through the valve seat. 4 and the gap between the outer rotor core 6 and the guide groove 601 enter into the delivery pipe 3, thereby realizing the flow of refrigerant under relatively small pressure, and effectively realizing the throttling effect; the third stage: when the refrigerant pressure is relatively large, the excessive refrigerant pressure pushes the valve needle 8, the outer rotor core 6 and the inner rotor core 7 to move together, compressing the large spring 9, so that the gap between the valve needle 8 and the sliding core 5 is further opened, increasing the flow rate of the refrigerant, and realizing the flow of refrigerant under relatively large pressure. At the same time, the large spring 9 generates a rebound force to offset the thrust of the refrigerant, and its compression degree is stabilized at a certain equilibrium point, which also realizes the throttling effect.

[0036] When the refrigerant passes through the expansion valve in reverse direction, Figure 6 As shown, after the refrigerant enters the end 2 from the delivery pipe 3, it enters the conduit 1 through the guide groove 601 and the gap between the outer rotor core 6 and the valve seat 4 in turn. The refrigerant pressure pushes the sliding core 5 away from the valve needle 8 until it hits the valve seat 4. At this time, the valve needle 8 is completely separated from the center hole in the sliding core 5, and the sliding core 5 is in a fully open state. The refrigerant can pass through the expansion valve smoothly and quickly.

[0037] In practical application, Figure 1 As shown, the condenser and the evaporator are respectively connected to two different expansion valves, namely valve A and valve B. During cooling, the refrigerant flowing out of the condenser flows forward through valve A for throttling transmission. During heating, the refrigerant flowing out of the evaporator flows forward through valve B for throttling transmission. When the refrigerant in the cooling process flows through valve B, and when the refrigerant in the cooling process flows through valve A, valve A and valve B are both in a fully open state, so that it is not easy to affect the refrigerant from entering the corresponding evaporator and condenser. During the cooling and heating processes, the refrigerant will flow through the power device to cool it down.

[0038] Second implementation method:

[0039] This implementation mode adds the following contents based on implementation mode 1: Figure 3 and Figure 7 An auxiliary throttle is also provided inside the end head 2 with an outer rotor core 6. The auxiliary throttle includes an electrical box 11, an outer flow tube 12, an inner flow tube 13, an inner correction frame 14 and an outer correction frame 15. One end of the outer correction frame 15 movably penetrates the inner rotor core 7 and extends into its inner cavity. The inner correction frame 14 is movably connected between the other end of the outer correction frame 15 and the outer flow tube 12. The electrical box 11 is arranged on the outside of the end head 2. One end of both the outer flow tube 12 and the inner flow tube 13 are fixedly penetrated by the electrical box 11 and communicated with the electric control three-way valve 18 inside the electrical box. The electric control three-way valve 18 is also fixedly connected with the liquid storage capsule 19 through a hose. Fluid is stored in the liquid storage capsule 19. The fluid can be water or gas, or the same refrigerant material as that inside the expansion valve. Technical personnel in this field can choose it at their own discretion. The large spring 9 abuts between the inner rotor core 7 and the inner correction frame 14, and the small spring 10 abuts between the valve needle 8 and the outer correction frame 15.

[0040] See also Figure 8 The outer flow tube 12 is sleeved on the outer side of the inner flow tube 13, and the two do not contact each other. The gap between the two has the function of transmitting fluid. The inner correction frame 14 includes a pressure ring 1401, a sliding sleeve 1403 and a plurality of support rods 1402 fixedly connected therebetween. One end of the sliding sleeve 1403 is slidably connected between the outer flow tube 12 and the inner flow tube 13, and the three are in a sliding sealing state. One end of the large spring 9 abuts against the pressure ring 1401. A sliding groove 1201 is provided on the inner wall of the outer flow tube 12. A slider 17 is fixedly connected to the end of the sliding sleeve 1403. The slider 17 is slidably connected to the inside of the sliding groove 1201. In the initial state, the slider 17 is close to the sliding groove 1201 and away from the inner wall of the inner correction frame 14. The slider 17 limits the movement of the sliding sleeve 1403, making it difficult for it to completely detach from the sliding groove 1201.

[0041] The outer correction frame 15 includes a pressing plate 1501, a piston 1502 and a sliding rod 1503, wherein the piston 1502 is fixedly connected between the pressing plate 1501 and the sliding rod 1503, and one end of the sliding rod 1503 is slidably connected to the inside of the sliding sleeve 1403, and the two are in a sliding sealing state, and the combination Figure 7 , Figure 8 and Fig.10As shown, the pressure plate 1501 is located in the inner cavity of the inner rotor core 7, the piston 1502 moves through the inner rotor core 7 and is slidably connected to the inside thereof, the small spring 10 abuts between the valve needle 8 and the pressure plate 1501, and in the initial state, the large spring 9 and the small spring 10 are both at their original lengths, the outer end of the piston 1502 is fixedly connected to a limiting ring 16, and the limiting ring 16 is located on the outer side of the inner rotor core 7. The limiting ring 16 limits the movement of the outer correction frame 15, and when the outer correction frame 15 moves a certain distance into the inner cavity of the inner rotor core 7, the limiting ring 16 will abut against the outer end of the inner rotor core 7, thereby making it difficult for the sliding rod 1503 to completely detach from the sliding sleeve 1403.

[0042] See also Fig. 9 The electric-controlled three-way valve 18 is respectively fixedly connected with an inlet 1801, an outlet 1802 and an outlet 2 1803. The outer flow tube 12 and the inner flow tube 13 are fixedly penetrated through the delivery tube 3 and extend to the inside of the electrical box 11. The end of the inner flow tube 13 is fixedly penetrated through the end of the outer flow tube 12 and is fixedly connected with the outlet 1 1802. A connecting tube 20 is fixedly connected between the outer flow tube 12 and the outlet 2 1803. A pump body 21 is fixedly connected to the inside of the electrical box 11. The pump body 21 can adopt a circulating pump to convey fluid. The feed end of the pump body 21 is fixedly connected to the liquid storage capsule 19 through a hose. The liquid storage capsule 19 is fixedly connected to the inside of the electrical box 11. The discharge end of the pump body 21 is fixedly connected to the inlet 1801 through the delivery pipe.

[0043] A flow sensor (not shown) is fixedly connected to the inside of the delivery pipe 3 near the large spring 9, and a controller is fixedly connected to the inside of the electrical box 11. The flow sensor, the electrically controlled three-way valve 18 and the pump body 21 are all electrically connected to the controller.

[0044] In actual use of the expansion valve, due to the long-term elastic deformation of the large spring 9 and the small spring 10, the elastic performance of the two is prone to decrease, and the accuracy of the control of the refrigerant flow rate is reduced. Therefore, in view of the above practical problems, this embodiment adds an auxiliary throttle and a flow sensor. When the elastic performance of the large spring 9 and the small spring 10 decreases, the auxiliary throttling effect on the refrigerant can be achieved. The specific process is as follows:

[0045] Step 1, data setting: When the refrigerant is transmitted in the forward direction in the expansion valve, it enters the delivery pipe 3 after passing through the throttling effect of the slide core 5, valve needle 8, large spring 9 and small spring 10. The flow sensor can monitor the refrigerant flow through the delivery pipe 3. When the refrigerant pressure is small, the small spring 10 is deformed, and the large spring 9 is not deformed. The refrigerant flow in the delivery pipe 3 is also small, so the following settings can be made:

[0046] Assume that when the large spring 9 is about to be deformed, the refrigerant flow rate in the delivery pipe 3 is Q1, and the refrigerant pressure difference is F1. Therefore, when the refrigerant pressure difference is less than F1, the refrigerant flow rate in the delivery pipe 3 will be less than Q1, and only the small spring 10 will be deformed. When the refrigerant pressure difference is greater than F1, the refrigerant flow rate in the delivery pipe 3 is greater than Q1, and the large spring 9 and the small spring 10 will be deformed at the same time.

[0047] Step 2: Monitoring the elastic properties of the large spring 9 and the small spring 10: The flow sensor measures the refrigerant flow Q flowing through the delivery pipe 3 in real time. 实际 After receiving the data, the controller compares it with the refrigerant standard flow rate q under the same preset refrigerant pressure difference. 实际 When it is greater than the standard flow rate q of the refrigerant and the difference between the two exceeds the preset difference range, it indicates that the flow rate of the refrigerant through the expansion valve has increased significantly under the same pressure difference, and the elastic performance of the large spring 9 or the small spring 10 or both of them has decreased. At this time, on the one hand, the controller warns the external control terminal that the control accuracy of the expansion valve is insufficient, and on the other hand, the following judgment operations and auxiliary throttling operations are performed:

[0048] 1. The refrigerant pressure difference is less than F1, indicating that only the small spring 10 undergoes elastic deformation at this time, and it is inferred that the elastic performance of the small spring 10 may be reduced. At this time, the small spring 10 is effectively corrected to achieve auxiliary throttling, as follows: the controller first starts the electric three-way valve 18 to connect the inlet 1801 with the outlet 1 1802, and the inlet 1801 with the outlet 2 1803 is not connected, and then starts the pump body 21 to absorb the fluid in the liquid storage capsule 19, so that it is slowly transported to the inner flow tube 13 through the electric three-way valve 18, as shown in FIG. Fig.11 As shown, the fluid passes through the inner flow tube 13 and gathers between the inner flow tube 13 and the slide bar 1503, gradually pushing the slide bar 1503 outward, so that the pressure plate 1501 squeezes the small spring 10, increasing the rebound force of the small spring 10 on the valve needle 8, reducing the gap between the valve needle 8 and the slide core 5, and correcting the throttling effect on the refrigerant. At this time, the actual refrigerant flow Q monitored by the flow sensor is 实际 It also gradually decreases. When the difference between it and the refrigerant standard flow rate q is within the preset difference range, it indicates that through the above-mentioned auxiliary throttling operation, the throttling effect of the expansion valve is close to the normal state when the small spring 10 is intact. At this time, the pump body 21 stops conveying the fluid, the external correction frame 15 stops moving, and the pressure plate 1501 maintains the squeezing effect on the small spring 10 in this state, maintaining the correction state, that is, maintaining the control accuracy of the refrigerant flow;

[0049] 2. The refrigerant pressure difference is greater than F1, indicating that both the large spring 9 and the small spring 10 are elastically deformed. Since the rebound force of the large spring 9 plays the main throttling effect at this time, the probability of the elastic performance of the large spring 9 decreasing is relatively high. The large spring 9 is corrected as follows to achieve auxiliary throttling: the controller starts the electric three-way valve 18 to connect the inlet 1801 with the outlet 2 1803, and the inlet 1801 with the outlet 1 1802 is not connected, and then starts the pump body 21 to absorb the fluid in the liquid storage capsule 19 and slowly transport it to the outflow pipe 12 through the electric three-way valve 18. Fig.12 As shown, the fluid flows along the gap between the outer flow tube 12 and the inner flow tube 13, and finally gathers in the slide groove 1201. The fluid pressure acts on the slider 17, pushing the sleeve 1403 outward, so that the pressure ring 1401 squeezes the large spring 9, increasing the rebound force of the large spring 9 on the valve needle 8, and reducing the gap between the valve needle 8 and the slide core 5, correcting the throttling effect on the refrigerant. When the actual refrigerant flow Q monitored by the flow sensor 实际 When the difference with the standard refrigerant flow q is within the preset difference range, it indicates that through the above-mentioned auxiliary throttling operation, the throttling effect of the expansion valve is close to the normal state when the large spring 9 is intact. At this time, the pump body 21 stops conveying the fluid, the internal correction frame 14 stops moving, and the pressure ring 1401 maintains the squeezing effect on the small spring 10 in this state, maintaining the correction state, that is, maintaining the control accuracy of the refrigerant flow.

[0050] In view of current practical needs, the above-mentioned implementation mode adopted in this application is not limited to the scope of protection. Various changes made within the knowledge scope of technical personnel in this field without departing from the concept of this application still fall within the scope of protection of the present invention.

Claims

1. A one-way reverse opening passive expansion valve, comprising a conduit (1) and a pair of end caps (2), wherein both ends of the conduit (1) are fixedly connected to the pair of end caps (2) via valve seats (4), and ends of the pair of end caps (2) that are away from each other are fixedly connected to a delivery pipe (3), and a sliding core (5) is slidably connected inside the conduit (1), characterized in that: An outer rotor core (6), an inner rotor core (7), a valve needle (8), a large spring (9) and a small spring (10) are arranged inside one of the end heads (2); An auxiliary throttle is also provided inside the end head (2) provided with the outer rotor core (6), and the auxiliary throttle comprises an electrical box (11), an outer flow tube (12), an inner flow tube (13), an inner correction frame (14) and an outer correction frame (15), one end of the outer correction frame (15) movably penetrates the inner rotor core (7) and extends into the inner cavity thereof, the inner correction frame (14) is movably connected between the other end of the outer correction frame (15) and the outer flow tube (12), and the electrical box (11) is provided with an auxiliary throttle. The box (11) is arranged on the outside of the end (2), and one end of the outer flow tube (12) and the inner flow tube (13) are fixedly passed through the electrical box (11) and communicated with the electric control three-way valve (18) inside the electrical box. The electric control three-way valve (18) is also fixedly communicated with the liquid storage bag (19) through a hose. The large spring (9) abuts between the inner rotor core (7) and the inner correction frame (14), and the small spring (10) abuts between the valve needle (8) and the outer correction frame (15).

2. The one-way reverse opening passive expansion valve according to claim 1, characterized in that: The inner rotor core (7) is slidably connected to the interior of the outer rotor core (6), the small spring (10) is arranged in the inner cavity of the inner rotor core (7), one end of the valve needle (8) is located in the inner cavity of the inner rotor core (7), and the other end thereof movably passes through the inner rotor core (7) and the outer rotor core (6) and extends to the inner side of the conduit (1).

3. The one-way reverse opening passive expansion valve according to claim 1, characterized in that: The outer flow tube (12) is sleeved on the outer side of the inner flow tube (13), and the two do not contact each other. The inner correction frame (14) includes a pressure ring (1401), a sliding sleeve (1403) and a plurality of support rods (1402) fixedly connected between the two. One end of the sliding sleeve (1403) is slidably connected between the outer flow tube (12) and the inner flow tube (13), and the three are in a sliding sealing state. One end of the large spring (9) abuts against the pressure ring (1401).

4. The one-way reverse opening passive expansion valve according to claim 3, characterized in that: A slide groove (1201) is provided on the inner wall of the outer flow tube (12), and a slider (17) is fixedly connected to the end of the sliding sleeve (1403). The slider (17) is slidably connected to the inside of the slide groove (1201). In the initial state, the slider (17) is close to the slide groove (1201) and away from the inner wall of the inner correction frame (14).

5. The one-way reverse opening passive expansion valve according to claim 3, characterized in that: The outer correction frame (15) includes a pressure plate (1501), a piston (1502) and a sliding rod (1503), and the piston (1502) is fixedly connected between the pressure plate (1501) and the sliding rod (1503), one end of the sliding rod (1503) is slidably connected to the inside of the sliding sleeve (1403), and the two are in a sliding sealing state, the pressure plate (1501) is located in the inner cavity of the inner rotor core (7), the piston (1502) moves through the inner rotor core (7) and is slidably connected to the inside thereof, the small spring (10) abuts between the valve needle (8) and the pressure plate (1501), and in the initial state, the large spring (9) and the small spring (10) are both at their original lengths.

6. The one-way reverse opening passive expansion valve according to claim 5, characterized in that: The outer end of the piston (1502) is fixedly connected to a limit ring (16), and the limit ring (16) is located on the outer side of the inner rotor core (7).

7. The one-way reverse opening passive expansion valve according to claim 1, characterized in that: The electric-controlled three-way valve (18) is fixedly connected with an inlet (1801), an outlet 1 (1802) and an outlet 2 (1803), respectively; the outer flow pipe (12) and the inner flow pipe (13) are fixedly passed through the delivery pipe (3) and extend into the interior of the electrical box (11); the end of the inner flow pipe (13) is fixedly passed through the end of the outer flow pipe (12) and is fixedly connected with the outlet 1 (1802); a connecting pipe (20) is fixedly connected between the outer flow pipe (12) and the outlet 2 (1803).

8. The one-way reverse opening passive expansion valve according to claim 7, characterized in that: A pump body (21) is fixedly connected to the interior of the electrical box (11); a feed end of the pump body (21) is fixedly connected to a liquid storage bag (19) via a hose; the liquid storage bag (19) is fixedly connected to the interior of the electrical box (11); and a discharge end of the pump body (21) is fixedly connected to an inlet (1801) via a feed pipe.

9. The one-way reverse opening passive expansion valve according to claim 8, characterized in that: A flow sensor is fixedly connected to the interior of the delivery pipe (3) near the large spring (9), a controller is fixedly connected to the interior of the electrical box (11), and the flow sensor, the electrically controlled three-way valve (18) and the pump body (21) are all electrically connected to the controller.

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