Fluid distributor of air conditioner heat exchanger
By using a retractable constant temperature cavity and a multi-dimensional temperature regulation structure, the problem of insufficient refrigerant temperature regulation in air conditioning heat exchangers under extreme temperature differences is solved, achieving uniform distribution and stable flow of refrigerant and improving air conditioning operating efficiency.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2026-01-12
- Publication Date
- 2026-03-31
AI Technical Summary
Traditional air conditioner heat exchangers' fluid distributors struggle to effectively regulate refrigerant temperature under extreme temperature differences, leading to capillary blockage or expansion, which affects refrigerant distribution and air conditioner operating efficiency.
It adopts a retractable constant temperature chamber structure, combined with the coordinated control of electric cylinder and temperature sensor to dynamically adjust the chamber volume. It is equipped with a porous flow plate, cooling and heating shells to ensure uniform refrigerant temperature, and eliminates pressure fluctuations through a pressure stabilizing chamber. It also uses a polyurethane insulation shell for heat insulation.
Under extreme temperature differences, ensure precise regulation of refrigerant temperature, avoid capillary blockage or expansion, maintain uniform refrigerant distribution, and improve heat exchanger operating efficiency.
Smart Images
Figure CN121761533A_ABST
Abstract
Description
Technical Field
[0001] This invention relates to the field of fluid distributor technology, and more specifically to a fluid distributor for an air conditioning heat exchanger. Background Technology
[0002] Generally speaking, the fluid distributor is a core component of the air conditioner heat exchanger. It is used to evenly distribute the refrigerant into each heat exchange tube of the heat exchanger to achieve efficient heat exchange between the refrigerant and the heat medium. During the operation of the air conditioner, the fluid distributor is needed to ensure that the refrigerant is evenly distributed in order to avoid uneven heat exchange and increased system energy consumption caused by refrigerant misflow. At the same time, it can also prevent compressor failure caused by excessive or insufficient refrigerant in some branches.
[0003] In practical applications, the core premise for achieving uniform distribution of refrigerant through a fluid distributor is that the refrigerant must pass through a constant temperature chamber before passing through the distributor's distributing capillary tube to make its temperature uniform. This is to eliminate the temperature gradient of the refrigerant itself and avoid uneven density and viscosity of the refrigerant due to local temperature differences, which would lead to deviations in branch flow. On the other hand, it is to adjust the refrigerant temperature to a preset temperature suitable for the capillary tube to avoid thermal expansion and contraction of the capillary tube due to temperature changes, which would change its inner diameter and flow resistance and destroy the basis for uniform distribution with equal resistance and equal flow. However, in actual use, the refrigerant temperature of air conditioners differs greatly between heating in winter and cooling in summer. In winter, the outside temperature is low, and the refrigerant temperature can be as low as -15°C before entering the distributor. In summer, the outside temperature is high, and the refrigerant temperature can be as high as 55°C before entering the distributor. Under such extreme temperature difference conditions, the traditional fixed-structure constant temperature chamber is difficult to meet the refrigerant temperature regulation requirements. When the outside temperature is very low, the time required for the refrigerant to heat up is insufficient to fully eliminate the temperature gradient and reach the preset temperature. This can easily lead to increased resistance in the capillary tube due to low temperature contraction, and blockage in some branches. Conversely, in summer when the temperature is too high, the time required for the refrigerant to cool down is insufficient to quickly reach the preset temperature. This can cause the capillary tube to expand due to high temperature and reduce resistance. Ultimately, both of these conditions will lead to the failure of the refrigerant distribution effect. Based on this, the present invention aims to provide a fluid distributor for an air conditioner heat exchanger that can adapt to extreme temperature difference environments and optimize the refrigerant temperature regulation effect. Summary of the Invention
[0004] The purpose of this invention is to address the shortcomings of the prior art by providing a fluid distributor for an air conditioning heat exchanger, thereby solving the technical problems in the prior art.
[0005] The objective of this invention can be achieved through the following technical solutions: A fluid distributor for an air conditioning heat exchanger includes: a distribution chamber, capillary tubes, drain pipes, a constant temperature chamber, a pressure stabilizing chamber, a main inlet pipe, a housing, a telescopic tube, and a porous flow buffer. The pressure stabilizing chamber is located at one end of the housing, and its inlet is connected to the main inlet pipe. The outlet of the pressure stabilizing chamber is connected to the constant temperature chamber. The constant temperature chamber is equipped with a porous flow buffer. The constant temperature chamber is connected to the distribution chamber via a telescopic tube, a connector tube, and a connecting tube. The distribution chamber is located at the other end of the housing. The telescopic tube is moved by an electric cylinder fixedly installed on the distribution chamber to adjust the volume of the cavity formed by the constant temperature chamber and the distribution chamber. Multiple capillary tubes are provided in the distribution chamber, and each capillary tube is connected to a connecting tube. Multiple drain pipes are fixedly installed on the distribution chamber, and each drain pipe is connected to a capillary tube. The drain pipes are connected to the inlet of the heat exchanger.
[0006] As a further aspect of the present invention: the end of the constant temperature chamber near the telescopic tube is fixedly and sealed to the telescopic tube, the end of the telescopic tube away from the constant temperature chamber is fixedly and sealed to the insertion tube, one end of the connecting tube is fixedly and sealed to the distribution chamber, and the other end forms an open structure, the end of the insertion tube away from the telescopic tube is slidably inserted into the opening of the connecting tube, and the contact surface of the two is provided with a sealing element.
[0007] As a further aspect of the present invention: a plurality of first temperature equalization plates are fixedly installed on the inner wall of the constant temperature cavity and are evenly arranged in a circular pattern. The first temperature equalization plates are arranged radially. A plurality of second temperature equalization plates are correspondingly arranged in a circular pattern inside the telescopic tube. One end of each second temperature equalization plate is fixedly connected to the end of the insertion tube facing the telescopic tube, and the plurality of second temperature equalization plates are staggered with the plurality of first temperature equalization plates.
[0008] As a further aspect of the present invention: a temperature sensor is provided at the inlet end of the constant temperature cavity, the temperature probe of the temperature sensor extends to the center of the constant temperature cavity, a cooling shell and a heating shell are fitted on the outer circular surface of the constant temperature cavity, the cooling shell and the heating shell are symmetrically arranged about the constant temperature cavity, and the temperature sensor is electrically connected to the cooling shell and the heating shell respectively.
[0009] As a further aspect of the present invention: a liquid storage chamber is fixedly installed inside the cooling sleeve, the liquid storage chamber is attached to the outer circular surface of the constant temperature cavity, a condenser is fixedly installed on the cooling sleeve, the bottom of the condenser is connected to the bottom of the liquid storage chamber through a low temperature liquid inlet pipe, and the top of the condenser is connected to the top of the liquid storage cavity through a heat exchange liquid outlet pipe. Multiple heat-conducting plates are fixedly installed inside the heating sleeve, one end of the heat-conducting plates extends into the cavity of the constant temperature cavity, and a heating assembly is also provided inside the heating sleeve, the heating assembly being fixedly connected to the heat-conducting plates.
[0010] As a further aspect of the present invention: an insulation shell is fitted onto the outside of the distribution cavity, the insulation shell is fixedly connected to the outer shell, and both the insulation shell and the outer shell are made of polyurethane material.
[0011] As a further aspect of the present invention: the pressure stabilizing chamber is provided with a flow guide cone and a flow turbulence rib, the flow guide cone is located on the side of the pressure stabilizing chamber near the main liquid inlet pipe, and the flow turbulence rib is located upstream of the flow guide cone.
[0012] As a further aspect of the present invention: the electric cylinder is equipped with a stroke sensor, which is connected to a temperature sensor.
[0013] The beneficial effects of this invention are: 1. In this invention, the telescopic tube is driven to extend and retract by an electric cylinder. Combined with the coordinated control of the stroke sensor and the temperature sensor, the volume of the cavity composed of the constant temperature chamber and the telescopic tube is dynamically adjusted to adapt to extreme temperature difference conditions in winter and summer. In winter, the refrigerant residence time is extended to ensure sufficient heating, and in summer, the cooling cycle is optimized. This effectively avoids the problems of capillary contraction and blockage due to insufficient heating in traditional fixed constant temperature chambers and capillary expansion caused by untimely cooling. It maintains the stability of the capillary inner diameter and flow resistance, and ensures the equal distribution of refrigerant with equal resistance and flow. 2. In this invention, the constant temperature cavity is provided with staggered first and second temperature equalization plates, which, together with the circulating cooling structure of the cooling shell and the heat-conducting heating structure of the heating shell, form a multi-dimensional temperature regulation and equalization system. This system can quickly eliminate the temperature gradient of the refrigerant itself and can also accurately adjust the refrigerant to the preset temperature through active temperature control. This avoids the problems of low adjustment accuracy and poor heat exchange efficiency of traditional constant temperature structures, ensuring that the density and viscosity of the refrigerant are uniform and consistent, and improving the flow stability. 3. In this invention, the pressure stabilizing chamber eliminates refrigerant pressure fluctuations through the synergistic effect of the turbulence ribs and the flow guide cone. The outer side of the distribution chamber is provided with a polyurethane insulation shell to prevent secondary temperature changes of the refrigerant. At the same time, the expandable sealing structure ensures the sealing performance during volume adjustment. This avoids the problem of the traditional distributor failing to achieve the desired distribution effect due to pressure fluctuations and secondary temperature changes. It is suitable for complex air conditioning operating conditions and improves the overall operating efficiency of the heat exchanger. Attached Figure Description
[0014] The invention will now be further described with reference to the accompanying drawings.
[0015] Figure 1 This is a schematic diagram of the overall structure of the present invention; Figure 2 This is a schematic diagram of the internal structure of the outer shell in this invention; Figure 3 This is a schematic diagram of the overall cross-section of the structure in this invention; Figure 4 This is a schematic diagram of the internal structure of the telescopic tube in this invention; Figure 5 This is a schematic diagram of the structure of the constant temperature cavity in this invention; Figure 6 This is a cross-sectional structural schematic diagram of the cooling jacket in this invention.
[0016] In the diagram: 1. Insulation shell; 101. Distribution chamber; 102. Capillary tube; 2. Drain pipe; 3. Constant temperature chamber; 4. Pressure stabilizing chamber; 5. Main inlet pipe; 6. Outer shell; 7. Telescopic pipe; 8. Insert pipe; 9. Connecting pipe; 10. Electric cylinder; 11. Cooling shell; 12. Heating shell; 13. Temperature sensor; 14. First heat spreader; 15. Second heat spreader; 16. Heat-conducting plate; 17. Condenser; 18. Liquid storage chamber; 19. Low-temperature liquid inlet pipe; 20. Heat exchange outlet pipe; 21. Temperature probe; 22. Porous flow buffer; 23. Flow bleed rib; 24. Flow guide cone. Detailed Implementation
[0017] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.
[0018] Please see Figures 1-6 As shown, the present invention is a fluid distributor for an air conditioning heat exchanger, comprising: The system comprises a distribution chamber 101, a capillary tube 102, a drain pipe 2, a constant temperature chamber 3, a pressure stabilizing chamber 4, a main inlet pipe 5, an outer shell 6, a telescopic pipe 7, and a porous flow buffer 22. The pressure stabilizing chamber 4 is located at one end of the outer shell 6. The inlet of the pressure stabilizing chamber 4 is connected to the main inlet pipe 5, and the outlet of the pressure stabilizing chamber 4 is connected to the constant temperature chamber 3. The constant temperature chamber 3 is equipped with a porous flow buffer 22 inside. The constant temperature chamber 3 is connected to the distribution chamber 101 in sequence through the telescopic pipe 7, the insertion pipe 8, and the connecting pipe 9. The distribution chamber 101 is located on the outer shell. At the other end of the shell 6, the telescopic tube 7 is driven to move by an electric cylinder 10 fixedly installed on the distribution chamber 101, which is used to adjust the volume of the cavity formed by the constant temperature chamber 3 and the distribution chamber 101. Multiple capillary tubes 102 are opened in the distribution chamber 101, and each capillary tube 102 is connected to the connecting tube 9. Multiple drain pipes 2 are fixedly installed on the distribution chamber 101, and each drain pipe 2 is connected to a capillary tube 102. The drain pipe 2 is connected to the heat exchanger inlet.
[0019] The working principle of this invention is as follows: Under normal operating conditions, the refrigerant enters the pressure stabilizing chamber 4 through the main liquid inlet pipe 5. First, the internal structure performs flow stabilization treatment to eliminate pressure fluctuations during refrigerant delivery, preventing uneven pressure from causing deviations in subsequent temperature regulation and flow distribution. After flow stabilization, the refrigerant enters the constant temperature chamber 3. Passing through the porous flow buffer 22, it is dispersed into multiple fine streams. The flow rate decreases while increasing the contact area with the inner wall of the constant temperature chamber 3 and the temperature equalization structure, providing sufficient reaction time for temperature regulation. The temperature sensor 13 monitors the core temperature of the refrigerant in the constant temperature chamber 3 in real time. Combined with the feedback signal from the air conditioning operation, it synchronously controls the operation of the heating jacket 12 and the cooling jacket 11, adjusting the refrigerant temperature to the preset value adapted to the capillary tube 102, eliminating the refrigerant's own temperature gradient, and ensuring uniform refrigerant density and viscosity. To address the issue of extreme temperature differences between winter and summer, the electric cylinder 10 drives the telescopic tube 7 to extend and retract based on the coordinated signals from the temperature sensor 13 and the stroke sensor, thereby adjusting the total volume of the cavity composed of the constant temperature chamber 3 and the telescopic tube 7. In winter, the initial temperature of the refrigerant decreases, requiring a longer heating time. The electric cylinder 10 pulls the telescopic tube 7 to extend, causing the insertion tube 8 to slide into the connecting tube 9, increasing the cavity volume. This extends the residence time of the refrigerant in the constant temperature chamber 3, allowing it to fully absorb heat and complete the heating process, eliminating the temperature gradient and reaching the preset temperature. In summer, the initial temperature of the refrigerant is high, similarly requiring a longer time to cool down. After being treated with constant temperature and pressure, the refrigerant enters the distribution chamber 101 through the connecting pipe 9, is evenly distributed through multiple capillary tubes 102, and is then transported to the heat exchanger through the drain pipe 2. Throughout the process, the adjustable-volume constant temperature structure adapts to extreme temperature differences, avoiding the problems of insufficient refrigerant heating at low temperatures leading to capillary contraction and liquid blockage, and untimely cooling at high temperatures leading to capillary expansion, which are common in traditional fixed constant temperature chambers. This maintains the stability of the capillary inner diameter and flow resistance, ensuring the basis for equal flow and resistance of the refrigerant, avoiding branch flow deviations, and ensuring the uniform distribution effect of the refrigerant.
[0020] like Figures 1-3 As shown, in a preferred embodiment of the present invention, the end of the constant temperature chamber 3 near the telescopic tube 7 is fixedly and sealed to the telescopic tube 7, the end of the telescopic tube 7 away from the constant temperature chamber 3 is fixedly and sealed to the insertion tube 8, one end of the connecting tube 9 is fixedly and sealed to the distribution chamber 101, and the other end forms an open structure, the end of the insertion tube 8 away from the telescopic tube 7 is slidably inserted into the opening of the connecting tube 9, and the contact surface of the two is provided with a sealing element.
[0021] In practical application, the electric cylinder 10 drives the telescopic tube 7 to perform axial telescopic movement, which in turn drives the insertion tube 8 to slide back and forth along the opening end of the connecting tube 9, thereby achieving stepless adjustment of the cavity volume. This adapts to the residence time required for refrigerant temperature adjustment under different temperature differences. The sealing element on the contact surface can effectively prevent refrigerant leakage at the sliding connection, ensuring sealing performance. Compared with the traditional fixed cavity structure, this telescopic sealing structure achieves dynamic volume adjustment, solving the problem of insufficient or excessive refrigerant temperature adjustment time under extreme temperature differences, and balancing temperature adjustment effect and fluid delivery efficiency.
[0022] like Figures 1-5 As shown, in a preferred embodiment of the present invention, a plurality of circumferentially uniformly arranged first temperature equalization plates 14 are fixedly installed on the inner wall of the constant temperature cavity 3. The first temperature equalization plates 14 are arranged radially. A plurality of circumferentially arranged second temperature equalization plates 15 are correspondingly provided in the telescopic tube 7. One end of each second temperature equalization plate 15 is fixedly connected to the end of the insertion tube 8 facing the telescopic tube 7, and the plurality of second temperature equalization plates 15 and the plurality of first temperature equalization plates 14 are staggered.
[0023] In practical application, after the refrigerant enters the constant temperature cavity 3, the first temperature equalization plate 14 divides the cavity into multiple radial channels, making the refrigerant evenly distributed and avoiding local accumulation that could lead to uneven temperature regulation. At the same time, the first temperature equalization plate 14 can quickly conduct the regulated temperature of the constant temperature cavity 3, accelerating the refrigerant temperature to become uniform. When the telescopic tube 7 moves the insertion tube 8, the second temperature equalization plate 15 moves synchronously with the insertion tube 8. Due to its staggered arrangement with the first temperature equalization plate 14, it can continuously disrupt the refrigerant flow trajectory while the cavity volume changes. Furthermore, when the telescopic tube 7 extends, the second temperature equalization plate 15 also moves synchronously, extending the contact path between the refrigerant and the temperature equalization plate, further improving the temperature homogenization effect.
[0024] like Figures 1-6 As shown, in a preferred embodiment of the present invention, a temperature sensor 13 is provided at the inlet end of the constant temperature cavity 3. The temperature probe 21 of the temperature sensor 13 extends to the center of the constant temperature cavity 3. A cooling shell 11 and a heating shell 12 are fitted on the outer circular surface of the constant temperature cavity 3. The cooling shell 11 and the heating shell 12 are symmetrically arranged about the constant temperature cavity 3. The temperature sensor 13 is electrically connected to the cooling shell 11 and the heating shell 12 respectively.
[0025] In practical application, the temperature probe 21 is positioned deep within the center of the constant temperature cavity 3, enabling precise monitoring of the refrigerant core temperature and avoiding temperature regulation errors caused by monitoring position deviations. The temperature sensor 13 converts the real-time temperature signal into an electrical signal, which is then fed back to the control system. When the refrigerant temperature is higher than the preset value, such as in summer conditions, the control system activates the cooling sleeve 11 and closes the heating sleeve 12, rapidly reducing the temperature of the inner wall of the constant temperature cavity 3 to cool the refrigerant. When the refrigerant temperature is lower than the preset value, such as in winter conditions, the heating sleeve 12 is activated and the cooling sleeve 11 is closed, providing heat to the refrigerant to complete the heating process. When the temperature reaches the preset value, both sleeves are in standby mode, maintaining the temperature of the constant temperature cavity 3 stable. In this way, active temperature regulation ensures that the refrigerant temperature of the constant temperature cavity 3 remains stable at the preset temperature.
[0026] like Figures 1-6 As shown, in a preferred embodiment of the present invention, a liquid storage chamber 18 is fixedly installed inside the cooling sleeve 11, and the liquid storage chamber 18 is attached to the outer circular surface of the constant temperature chamber 3. A condenser 17 is fixedly installed on the cooling sleeve 11. The bottom of the condenser 17 is connected to the bottom of the liquid storage chamber 18 through a low-temperature liquid inlet pipe 19, and the top of the condenser 17 is connected to the top of the liquid storage chamber 18 through a heat exchange liquid outlet pipe 20. A plurality of heat-conducting plates 16 are fixedly installed inside the heating sleeve 12. One end of the heat-conducting plate 16 extends into the cavity of the constant temperature chamber 3. A heating assembly is also provided inside the heating sleeve 12, and the heating assembly is fixedly connected to the heat-conducting plate 16.
[0027] In practical application, during summer cooling conditions, the condenser 17 prepares a low-temperature coolant, which is then transported to the storage chamber 18 via the low-temperature inlet pipe 19. The storage chamber 18 is attached to the outer surface of the constant temperature chamber 3, and the coolant carries away heat from the refrigerant through heat conduction. The cooled liquid, after absorbing heat, flows back to the condenser 17 for cooling circulation via the heat exchange outlet pipe 20, achieving continuous cooling and ensuring that the high-temperature refrigerant is quickly reduced to the preset temperature, thus preventing the capillary tube from experiencing a decrease in resistance due to high-temperature expansion. During winter heating conditions, the heating component is activated to generate heat, which is transferred to the interior of the constant temperature chamber 3 through the heat-conducting plate 16. The heat-conducting plate 16 extends deep into the chamber and can directly contact the refrigerant, improving heat conduction efficiency and enabling the low-temperature refrigerant to heat up rapidly, eliminating temperature gradients and preventing the capillary tube from developing liquid plugs due to low-temperature contraction.
[0028] like Figures 1-3 As shown, in a preferred embodiment of the present invention, a heat insulation shell 1 is sleeved on the outside of the distribution cavity 101, the heat insulation shell 1 is fixedly connected to the outer shell 6, and both the heat insulation shell 1 and the outer shell 6 are made of polyurethane material.
[0029] In practical applications, because polyurethane material has excellent thermal insulation properties, the insulation shell 1 can effectively isolate the influence of the external ambient temperature on the refrigerant in the distribution cavity 101, and avoid the refrigerant from fluctuating in density and viscosity due to secondary temperature changes during the distribution process, thus disrupting the established uniform temperature state. Meanwhile, the outer shell 6 protects the internal constant temperature cavity 3 and other components, reduces the temperature loss in the constant temperature cavity 3, and lowers the energy consumption of the heating shell 12 and the cooling shell 11.
[0030] like Figures 1-3 As shown, in a preferred embodiment of the present invention, the pressure stabilizing chamber 4 is provided with a flow guide cone 24 and a flow turbulence rib 23. The flow guide cone 24 is located on the side of the pressure stabilizing chamber 4 near the main liquid inlet pipe 5, and the flow turbulence rib 23 is located upstream of the flow guide cone 24.
[0031] In practical application, after the refrigerant enters the pressure stabilizing chamber 4 through the main inlet pipe 5, its flow trajectory is first disrupted by the turbulence ribs 23, breaking up the eddies in the refrigerant and initially eliminating pressure fluctuations. Subsequently, the refrigerant flows to the guide cone 24, which has a conical structure that can disperse the concentrated refrigerant inflow circumferentially, allowing the refrigerant to flow evenly against the inner wall of the pressure stabilizing chamber 4, further balancing the pressure inside the chamber. Through the synergistic effect of turbulence and guidance, the refrigerant enters the constant temperature chamber 3 with a stable flow rate and pressure, avoiding the problem of uneven refrigerant flow and inconsistent temperature regulation in the constant temperature chamber 3 caused by pressure fluctuations.
[0032] like Figures 1-3 As shown, in a preferred embodiment of the present invention, the electric cylinder 10 is provided with a stroke sensor, which is connected to the temperature sensor 13.
[0033] In practical applications, the stroke sensor can monitor the extension and retraction stroke of the electric cylinder 10 in real time, thereby providing feedback on the adjustment amount of the telescopic tube 7 and the change in cavity volume. It also works in synergy with the temperature signal from the temperature sensor 13 to form a coordinated control mechanism. When the temperature sensor 13 detects a large deviation in refrigerant temperature, the stroke sensor adjusts the stroke of the electric cylinder 10 to increase the adjustment range of cavity volume and extend or shorten the refrigerant residence time. When the temperature approaches the preset value, the adjustment range is reduced to precisely control the volume and stabilize the refrigerant temperature within the preset range. This allows for precise adjustment of the volume of the constant temperature cavity 3 and the telescopic tube 7 according to specific temperature conditions.
[0034] The foregoing has provided a detailed description of one embodiment of the present invention, but this description is merely a preferred embodiment and should not be construed as limiting the scope of the invention. All equivalent variations and modifications made within the scope of the claims of this invention should still fall within the patent coverage of this invention.
Claims
1. A fluid distributor for an air conditioning heat exchanger, comprising: The distribution cavity (101), the capillary channel (102), the liquid discharge pipe (2), the constant temperature cavity (3), the constant pressure cavity (4), the total liquid inlet pipe (5), the shell (6), the telescopic pipe (7) and the porous slow flow plate (22) are characterized in that: the constant pressure cavity (4) is arranged at one end of the shell (6), the inlet end of the constant pressure cavity (4) is communicated with the total liquid inlet pipe (5), the outlet end of the constant pressure cavity (4) is connected with the constant temperature cavity (3), the constant temperature cavity (3) is internally provided with the porous slow flow plate (22), the constant temperature cavity (3) is communicated with the distribution cavity (101) through the telescopic pipe (7), the plug-in pipe (8) and the connecting pipe (9) in sequence, the distribution cavity (101) is located at the other end of the shell (6), the telescopic pipe (7) is driven to move by the electric cylinder (10) fixedly installed on the distribution cavity (101), for adjusting the cavity volume composed of the constant temperature cavity (3) and the distribution cavity (101), a plurality of capillary channels (102) are arranged in the distribution cavity (101), each capillary channel (102) is communicated with the connecting pipe (9), a plurality of liquid discharge pipes (2) are fixedly installed on the distribution cavity (101), and each liquid discharge pipe (2) is communicated with one capillary channel (102), and the liquid discharge pipe (2) is connected with the inlet of the heat exchanger.
2. A fluid distributor for an air conditioning heat exchanger according to claim 1, wherein The one end of the constant temperature cavity (3) close to the telescopic pipe (7) is fixedly and sealingly connected with the telescopic pipe (7), the other end of the telescopic pipe (7) away from the constant temperature cavity (3) is fixedly connected with the plug-in pipe (8), one end of the connecting pipe (9) is fixedly and sealingly connected with the distribution cavity (101), and the other end is formed as an open structure, the other end of the plug-in pipe (8) away from the telescopic pipe (7) is slidingly inserted into the opening of the connecting pipe (9), and a sealing element is arranged on the contact surface of the two.
3. A fluid distributor for an air conditioning heat exchanger according to claim 2, wherein A plurality of first uniform temperature plates (14) are fixedly installed on the inner wall of the constant temperature cavity (3) and are uniformly arranged in a circle, the first uniform temperature plates (14) are arranged in a radial direction, a plurality of second uniform temperature plates (15) are correspondingly arranged in the telescopic pipe (7) and are arranged in a circle, one end of each second uniform temperature plate (15) is fixedly connected with the one end of the plug-in pipe (8) facing the telescopic pipe (7), and the plurality of second uniform temperature plates (15) are arranged in a staggered manner with the plurality of first uniform temperature plates (14).
4. The fluid distributor for an air conditioning heat exchanger of claim 1 wherein, A temperature sensor (13) is arranged at the inlet end of the constant temperature cavity (3), the temperature sensing head (21) of the temperature sensor (13) extends to the center position of the cavity of the constant temperature cavity (3), the constant temperature cavity (3) is sleeved with a cooling sleeve (11) and a heating sleeve (12) on the outer circular surface, the cooling sleeve (11) and the heating sleeve (12) are symmetrically arranged about the constant temperature cavity (3), and the temperature sensor (13) is electrically connected with the cooling sleeve (11) and the heating sleeve (12) respectively.
5. A fluid distributor for an air conditioning heat exchanger according to claim 4, wherein The temperature reducing sleeve shell (11) is fixedly provided with a liquid storage cavity (18) which is attached to the outer circular surface of the constant temperature cavity (3), the temperature reducing sleeve shell (11) is fixedly provided with a condenser (17), the bottom of the condenser (17) is communicated with the bottom of the liquid storage cavity (18) through a low temperature liquid inlet pipe (19), the top of the condenser (17) is communicated with the top of the liquid storage cavity (18) through a heat exchange liquid outlet pipe (20), the temperature increasing sleeve shell (12) is fixedly provided with a plurality of heat conducting fins (16), one end of the heat conducting fins (16) extends into the cavity of the constant temperature cavity (3), and the temperature increasing sleeve shell (12) is further provided with a heating assembly which is fixedly connected with the heat conducting fins (16).
6. A fluid distributor for an air conditioning heat exchanger according to claim 1, wherein The distribution cavity (101) is sleeved with a heat preservation shell (1) on the outside, the heat preservation shell (1) is fixedly connected with the outer shell (6), and the heat preservation shell (1) and the outer shell (6) are both made of polyurethane material.
7. A fluid distributor for an air conditioning heat exchanger according to claim 1, wherein The steady pressure cavity (4) is internally provided with a flow guide cone (24) and a flow disturbing rib (23), the flow guide cone (24) is arranged on one side of the steady pressure cavity (4) close to the total liquid inlet pipe (5), and the flow disturbing rib (23) is arranged on the upstream of the flow guide cone (24).
8. A fluid distributor for an air conditioning heat exchanger according to claim 1, wherein The electric cylinder (10) is provided with a stroke sensor, and the stroke sensor is connected with the temperature sensor (13).