Air conditioner evaporator with current sharing distribution structure

Abstract

This invention relates to the field of air conditioning evaporator technology, and discloses an air conditioning evaporator with a uniform flow distribution structure, including multiple evaporation branches, multiple distributors, a basic liquid distribution pipe, a liquid phase compensation pipe, and a vapor-liquid separator. The vapor-liquid separator separates the throttled gas-liquid two-phase refrigerant into a gas-liquid mixed refrigerant and a liquid-enriched refrigerant, which are then respectively delivered to the basic liquid distribution pipe and the liquid phase compensation pipe. Each distributor is located at the input end of an evaporation branch and contains a flow distribution chamber, a liquid replenishment chamber, and a valve core assembly. The valve core rod has a basic throttling orifice and a liquid replenishment channel. The basic throttling orifice connects the flow distribution chamber and the evaporation branch, forming a throttling pressure difference. Under the action of the throttling pressure difference, the valve core rod overcomes the slippage of the elastic reset element, thereby changing the flow area of ​​the liquid replenishment channel, allowing the liquid-enriched refrigerant in the liquid replenishment chamber to be supplied in parallel with the basic throttling orifice into the corresponding evaporation branch. Liquid phase compensation is performed according to the liquid supply status of each evaporation branch to improve the uniformity of refrigerant distribution.

Description

Technical Field

[0001] This invention relates to the field of air conditioner evaporator technology, and more particularly to an air conditioner evaporator with a uniform flow distribution structure. Background Technology

[0002] The evaporator in an air conditioner is a crucial heat exchange component in a refrigeration system, typically comprising multiple parallel or segmented evaporation branches. After being condensed in the condenser, the high-pressure liquid refrigerant passes through expansion valves, capillary tubes, or electronic expansion valves, forming a low-temperature, low-pressure two-phase gas-liquid refrigerant, which then enters the evaporator. Inside the evaporator, the refrigerant absorbs heat from the air side and gradually evaporates, thus achieving refrigeration and heat exchange.

[0003] Existing air conditioning evaporators typically distribute the throttled refrigerant to multiple evaporation branches via a distributor, distribution pipe, or fixed orifice. To ensure similar refrigerant flow rates in each evaporation branch, current structures generally achieve basic flow equalization by using distribution orifices of the same diameter, distribution pipes of the same length, or capillary tubes of the same specifications. However, the refrigerant entering the evaporator is usually in a two-phase state of gas and liquid. The gas and liquid phases differ significantly in density, inertia, flow velocity, and flow resistance, which can easily lead to gas-liquid stratification, inlet flow deviation, and localized impinging flow within the distributor, manifold, or distribution pipe. This results in inconsistent gas-liquid ratios and mass flow rates in each evaporation branch.

[0004] Meanwhile, differences may exist between different evaporator branches in terms of pipe length, number of bends, installation height, processing errors, welding deformation, oil film deposition inside the pipes, and localized impurity adhesion, resulting in varying flow resistance in each evaporator branch. During evaporator operation, uneven airflow distribution on the air side, localized dust accumulation on the fins, localized frost formation, or changes in heat exchange load will further alter the evaporation and pressure states of the refrigerant in each evaporator branch. The combined effect of these factors can easily lead to insufficient refrigerant supply in some evaporator branches, while excessive refrigerant supply can occur in others.

[0005] When the liquid refrigerant supply to certain evaporation branches is insufficient, there is not enough liquid refrigerant to effectively participate in evaporation and heat absorption within those branches. This leads to a decrease in the heat exchange capacity of the corresponding area, uneven temperature distribution on the evaporator surface, and affects the overall refrigeration efficiency. Conversely, when the liquid refrigerant supply to certain evaporation branches is excessive, the liquid refrigerant may not be able to evaporate fully within those branches. This can easily cause excessively low temperatures in those areas, exacerbate localized frost formation, and the frost layer can block the fin channels and increase airflow resistance, thereby reducing the effective heat exchange area and heat exchange efficiency. In severe cases, it may also increase ineffective refrigerant circulation and even pose a risk of liquid refrigerant flowing back into the compressor.

[0006] Existing fixed liquid distribution structures mainly rely on preset orifice diameters or pipeline parameters for distribution. The distribution ratio is basically fixed during operation, making it difficult to dynamically compensate based on the real-time throttling pressure difference, liquid supply status, or evaporation status of individual evaporation branches. Even when using ordinary bypass structures or pressure regulating structures, the adjustment is usually based on the main pipeline pressure or total flow rate. It is difficult to add refrigerant with a higher liquid content to an evaporation branch with insufficient liquid supply, and it is also difficult to automatically reduce the amount of refrigerant added based on the pressure recovery of that branch after replenishment.

[0007] Therefore, there is an urgent need for an air conditioning evaporator flow distribution structure that can separate the basic liquid supply from the liquid phase compensation liquid supply and can independently adjust the liquid replenishment according to the throttling pressure difference of each evaporation branch, so as to improve the problem of uneven refrigerant mass flow rate and liquid phase distribution among multiple evaporation branches and improve the overall heat exchange uniformity and operational stability of the evaporator. Summary of the Invention

[0008] The purpose of this invention is to provide an air conditioner evaporator with a uniform flow distribution structure, in order to solve the problems of existing air conditioner evaporators with multi-branch liquid distribution structures that mainly rely on fixed orifice diameters or fixed pipeline resistance for preset distribution, making it difficult to dynamically compensate according to the liquid supply status of individual evaporation branches, which easily leads to uneven refrigerant distribution, uneven heat exchange, and increased local frost in each evaporation branch.

[0009] To achieve the above objectives, the present invention adopts the following technical solution: an air conditioning evaporator with a uniform flow distribution structure, comprising: Multiple evaporation branches; Multiple distributors are installed at the input end of each of the evaporation branches, and each distributor is provided with a flow distribution chamber, a liquid replenishment chamber and a valve core assembly. The basic liquid distribution pipes are respectively connected to the distribution chambers of the multiple distributors; Liquid phase compensation pipes are respectively connected to the replenishment chambers of the multiple distributors; A vapor-liquid separator has an input end, a first output end, and a second output end. The first output end is connected to the basic liquid distribution pipeline and is used to output a vapor-liquid mixed refrigerant to the basic liquid distribution pipeline. The second output end is connected to the liquid phase compensation pipeline and is used to output a liquid phase enriched refrigerant to the liquid phase compensation pipeline. Each of the distributors includes a slidable valve core rod and an elastic reset member. The valve core rod is provided with a basic throttling orifice and a liquid replenishment channel. The basic throttling orifice connects the distribution chamber with the corresponding evaporation branch, so that the gas-liquid mixed refrigerant in the distribution chamber enters the corresponding evaporation branch through the basic throttling orifice, and a throttling pressure difference is formed on both sides of the basic throttling orifice. The valve core rod overcomes the slippage of the elastic reset member under the action of the throttling pressure difference, thereby changing the flow area of ​​the liquid replenishment channel, so that the liquid-enriched refrigerant in the liquid replenishment chamber is replenished into the corresponding evaporation branch in parallel with the basic throttling orifice through the liquid replenishment channel.

[0010] Preferably, the flow areas of the basic throttling orifices in the plurality of distributors are equal, the effective pressure-bearing areas of the plurality of valve core rods are equal, and the preload of the plurality of elastic reset members is equal.

[0011] Preferably, a pull rod is provided at the end of the valve core rod, a spring seat is slidably mounted on the surface of the pull rod, the elastic reset member is a spring sleeved on the pull rod, the two ends of the spring respectively abut against the valve core rod and the spring seat, and a limiting step is provided in the distributor to limit the position of the spring seat.

[0012] Preferably, the valve core rod has a stepped structure, and a first sealing ring and a second sealing ring are provided on the surface of the valve core rod. The first sealing ring slides in contact with the inner wall of the diversion cavity, and the second sealing ring slides in contact with the inner wall of the replenishment cavity.

[0013] Preferably, the valve core rod is provided with a first pressure-bearing end face and a second pressure-bearing end face, the basic throttling orifice is provided through the valve core rod along the axial direction, the two ends of the basic throttling orifice are respectively provided on the first pressure-bearing end face and the second pressure-bearing end face, the inlet end of the basic throttling orifice faces the flow distribution chamber, the outlet end of the basic throttling orifice faces the corresponding evaporation branch, and an effective pressure-bearing surface is formed between the first pressure-bearing end face and the second pressure-bearing end face.

[0014] Preferably, the liquid-phase enriched refrigerant is added to the corresponding evaporation branch, thereby increasing the downstream pressure of the basic throttling orifice of the corresponding evaporation branch and reducing the corresponding throttling pressure difference.

[0015] Preferably, the interior of the vapor-liquid separator is a liquid phase deposition chamber, the input end is located in the top, side or upper region of the liquid phase deposition chamber, the first output end is located in the middle or upper region of the liquid phase deposition chamber, and the second output end is located in the bottom region of the liquid phase deposition chamber.

[0016] Preferably, the replenishment channel is an annular groove provided on the outer periphery of the valve core rod, a fixing sleeve is fixedly installed inside the distributor, and the end of the valve core rod with the replenishment channel is slidably inserted into the fixing sleeve; When the valve core rod is in the initial position, the fixed sleeve blocks the liquid replenishment channel, so that the liquid replenishment chamber is cut off from the corresponding evaporation branch, and the liquid replenishment chamber temporarily stores the liquid-enriched refrigerant from the liquid phase compensation pipe. When the valve core rod slides toward the direction of the corresponding evaporation branch, the liquid replenishment channel passes over the blocking edge of the fixed sleeve and connects with the corresponding evaporation branch, so that the liquid-phase enriched refrigerant temporarily stored in the liquid replenishment chamber is replenished into the corresponding evaporation branch through the liquid replenishment channel.

[0017] Preferably, the annular groove includes a slow-opening section and a compensation section arranged sequentially along the sliding direction of the valve core rod. The flow area of ​​the slow-opening section is smaller than that of the compensation section, and the slow-opening section is gradually changing so that the opening area of ​​the liquid replenishment channel gradually increases when the valve core rod slides.

[0018] The present invention has the following beneficial effects: 1. This invention separates the basic liquid supply and makeup liquid supply of the evaporation branch by using a vapor-liquid separator to output a gas-liquid mixed refrigerant to the basic liquid distribution pipe and a liquid-enriched refrigerant to the liquid phase compensation pipe. Compared with the existing structure that supplies liquid to each branch only through a single liquid distribution pipe or a fixed liquid distribution hole, this invention can replenish the evaporation branch with a refrigerant with a higher liquid phase content when the liquid supply to the branch is insufficient, thereby improving the effective evaporation and heat absorption capacity of the makeup liquid.

[0019] 2. This invention includes a distributor at the input end of each evaporation branch. The valve core rod within the distributor slides under the throttling pressure difference on both sides of the basic throttling orifice, thereby changing the flow area of ​​the replenishment channel. Therefore, when the throttling pressure difference increases in a certain evaporation branch due to uneven distribution, resistance changes, or insufficient liquid supply, only the replenishment channel corresponding to that evaporation branch opens or increases its opening, achieving directional replenishment to the abnormal branch. This differs from existing fixed-aperture liquid distribution structures, which cannot compensate for changes in the state of individual branches.

[0020] 3. In this invention, the replenishment channel and the basic throttling orifice are connected in parallel to replenish the same evaporation branch with liquid-phase enriched refrigerant. When the replenishment channel is opened, the downstream pressure of the basic throttling orifice of the corresponding evaporation branch increases, reducing the throttling pressure difference of that branch. The valve core rod then retracts under the action of the elastic reset element, thereby reducing or closing the replenishment channel. This forms a mechanical negative feedback process of "pressure difference increase - replenishment opening - pressure difference decrease - replenishment reduction", avoiding excessive liquid supply to the corresponding evaporation branch caused by the replenishment channel being open for a long time, reducing energy waste caused by insufficient evaporation of liquid refrigerant, increased local frost, and ineffective refrigerant circulation.

[0021] 4. This invention controls the opening and closing of the liquid replenishment channel by using a fixed sleeve to block the annular groove on the outer periphery of the valve core rod. The annular groove can be configured as a slow-opening section and a compensation section, allowing the opening area of ​​the liquid replenishment channel to gradually increase as the valve core rod slides. Compared to a conventional sudden-opening bypass hole structure, this method reduces pressure fluctuations and valve core vibrations caused by a large amount of liquid-enriched refrigerant instantaneously entering the evaporation branch, thus improving the stability of refrigerant distribution regulation across multiple branches. Attached Figure Description

[0022] Figure 1 This is a three-dimensional structural diagram of an air conditioner evaporator with a uniform flow distribution structure proposed in this invention; Figure 2 This is an exploded structural diagram of an air conditioner evaporator with a uniform flow distribution structure proposed in this invention; Figure 3 This is an exploded view of the dispenser proposed in this invention; Figure 4 This is a cross-sectional three-dimensional structural diagram of the dispenser proposed in this invention; Figure 5 This is a cross-sectional three-dimensional structural diagram of the valve core rod proposed in this invention; Figure 6 This is a schematic diagram of the front section of the vapor-liquid separator proposed in this invention; Figure 7 This is a cross-sectional view of the dispenser proposed in this invention with the replenishment channel cut off. Figure 8 This is a cross-sectional view of the dispenser proposed in this invention when the replenishment channel is connected.

[0023] In the picture: 100. Evaporation branch; 200. Distributor; 201. Diversion chamber; 202. Liquid replenishment chamber; 203. Valve core rod; 204. Elastic reset element; 205. Basic throttling orifice; 206. Liquid replenishment channel; 207. Pull rod; 208. Spring seat; 209. First sealing ring; 210. Second sealing ring; 211. First pressure-bearing end face; 212. Second pressure-bearing end face; 213. Fixing sleeve; 300. Basic liquid distribution pipe; 400. Liquid phase compensation pipe; 500. Vapor-liquid separator; 600. Output main fitting. Detailed Implementation

[0024] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments.

[0025] In the description of this invention, it should be understood that the terms "upper", "lower", "front", "rear", "left", "right", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention. Example 1

[0026] like Figures 1 to 8As shown, this embodiment provides an air conditioning evaporator with a uniform flow distribution structure, including multiple evaporation branches 100, multiple distributors 200, a basic liquid distribution pipe 300, a liquid phase compensation pipe 400, and a vapor-liquid separator 500.

[0027] Multiple evaporator branches 100 are used for refrigerant to flow through and exchange heat with the outside air. Each evaporator branch 100 can be a heat exchange pipeline arranged in parallel, or it can be a heat exchange channel in different areas of the evaporator core. Multiple distributors 200 are installed at the input end of each evaporator branch 100 to distribute and compensate the refrigerant entering each evaporator branch 100. The output ends of the multiple evaporator branches 100 are connected to the output main pipe 600, which is used to collect the refrigerant after heat exchange in the multiple evaporator branches 100 and output the collected refrigerant to the compressor suction side or subsequent refrigeration circuit.

[0028] like Figure 4 As shown, each distributor 200 is equipped with a flow distribution chamber 201, a liquid replenishment chamber 202, and a valve core assembly. The flow distribution chamber 201 is connected to the basic liquid distribution pipe 300, and the liquid replenishment chamber 202 is connected to the liquid phase compensation pipe 400. The basic liquid distribution pipe 300 is connected to the flow distribution chambers 201 of multiple distributors 200 respectively, and is used to supply gas-liquid mixed refrigerant to each distributor 200. The liquid phase compensation pipe 400 is connected to the liquid replenishment chambers 202 of multiple distributors 200 respectively, and is used to supply liquid-enriched refrigerant to each distributor 200.

[0029] like Figure 4 As shown, the vapor-liquid separator 500 has an input end, a first output end, and a second output end. The input end of the vapor-liquid separator 500 is used to receive the two-phase refrigerant (gas and liquid) after throttling by the throttling device. The first output end is connected to the basic liquid distribution pipe 300 and is used to output the gas-liquid mixed refrigerant to the basic liquid distribution pipe 300. The second output end is connected to the liquid phase compensation pipe 400 and is used to output the liquid phase enriched refrigerant to the liquid phase compensation pipe 400. It should be noted that the liquid phase enriched refrigerant mentioned in this embodiment is not required to be a completely pure liquid refrigerant without any gas phase, but rather refers to a refrigerant fluid whose liquid phase content is higher than that of the gas-liquid mixed refrigerant in the basic liquid distribution pipe 300.

[0030] like Figures 3 to 5 As shown, each distributor 200's valve core assembly includes a slidable valve core rod 203 and a resilient reset member 204. The valve core rod 203 can slide along the axial direction of the distributor 200 or a preset sliding direction. The valve core rod 203 is provided with a basic throttling orifice 205 and a liquid replenishment channel 206.

[0031] Preferably, the flow areas of the basic throttling orifices 205 in the multiple distributors 200 are equal, the effective pressure-bearing areas of the multiple valve core rods 203 are equal, and the preload of the multiple elastic reset members 204 is equal. Thus, the valve core assemblies corresponding to each evaporation branch 100 have the same or similar opening pressure differential and reset characteristics. When the throttling pressure differential of a certain evaporation branch 100 is too large, its corresponding replenishment channel 206 opens preferentially; when the throttling pressure differential drops after replenishment, the replenishment channel 206 gradually decreases or closes, thereby helping to make the throttling pressure differentials of the multiple evaporation branches 100 tend to be consistent.

[0032] like Figure 5 and Figure 7 As shown, a pull rod 207 is provided at the end of the valve core rod 203. A spring seat 208 is slidably mounted on the surface of the pull rod 207. The elastic reset member 204 is a spring sleeved on the pull rod 207. One end of the spring abuts against the valve core rod 203, and the other end abuts against the spring seat 208. A limiting step is provided inside the distributor 200 to limit the position of the spring seat 208. By limiting the position of the spring seat 208 by the limiting step, the elastic reset member 204 can be kept at a preset compression amount, thereby providing a stable reset force for the valve core rod 203.

[0033] like Figure 4 and Figure 5 As shown, the valve core rod 203 can have a stepped structure. A first sealing ring 209 and a second sealing ring 210 are provided on the surface of the valve core rod 203. The first sealing ring 209 slides in contact with the inner wall of the flow divider chamber 201 to reduce unintended cross-flow between the flow divider chamber 201 and other chambers. The second sealing ring 210 slides in contact with the inner wall of the replenishment chamber 202 to reduce unintended cross-flow between the replenishment chamber 202 and other chambers. The first sealing ring 209 and the second sealing ring 210 are made of an elastic sealing material resistant to refrigerant and refrigeration oil.

[0034] Furthermore, such as Figure 5 As shown, the valve core rod 203 has a first pressure-bearing end face 211 and a second pressure-bearing end face 212. A basic throttling orifice 205 is axially extending through the valve core rod 203, with its two ends respectively located on the first pressure-bearing end face 211 and the second pressure-bearing end face 212. The inlet end of the basic throttling orifice 205 faces the flow distribution chamber 201, and the outlet end of the basic throttling orifice 205 faces the corresponding evaporation branch 100. An effective pressure-bearing surface is formed between the first pressure-bearing end face 211 and the second pressure-bearing end face 212.

[0035] Specifically, the pressure within the diversion chamber 201 acts on the first pressure-bearing end face 211, and the pressure at the inlet side of the evaporation branch 100 or the outlet side of the basic throttling orifice 205 acts on the second pressure-bearing end face 212. The pressure difference between the two acts on the effective pressure-bearing area of ​​the valve core rod 203, thereby forming an axial hydraulic pressure that pushes the valve core rod 203 to slide towards the evaporation branch 100. The elastic reset member 204 applies a reset force in the opposite direction to the valve core rod 203. When the axial hydraulic pressure is greater than the reset force of the elastic reset member 204, the valve core rod 203 slides. By setting the first pressure-bearing end face 211, the second pressure-bearing end face 212, and the effective pressure-bearing surface, the throttling pressure difference on both sides of the basic throttling orifice 205 can be reliably converted into the sliding action of the valve core rod 203.

[0036] like Figure 7 As shown, the basic throttling orifice 205 connects the flow distribution chamber 201 with the corresponding evaporation branch 100, allowing the gas-liquid mixed refrigerant in the flow distribution chamber 201 to enter the corresponding evaporation branch 100 through the basic throttling orifice 205. Because the basic throttling orifice 205 throttles the refrigerant flow, a throttling pressure difference is formed on both sides of the basic throttling orifice 205. This throttling pressure difference acts on the valve core rod 203, causing the valve core rod 203 to slide against the elastic reset member 204.

[0037] Under normal operating conditions, such as Figure 7 As shown, the liquid supply status of each evaporation branch 100 is basically the same, and the throttling pressure difference formed on both sides of the basic throttling orifice 205 is within the preset range. At this time, the valve core rod 203 is held in the initial position under the action of the elastic reset member 204, the liquid replenishment channel 206 is in the closed state, and the liquid-enriched refrigerant in the liquid replenishment chamber 202 will not enter the evaporation branch 100 in large quantities. Each evaporation branch 100 mainly obtains the gas-liquid mixed refrigerant from the basic liquid distribution pipe 300 through the basic throttling orifice 205.

[0038] like Figure 8 As shown, when a certain evaporation branch 100 experiences insufficient liquid supply due to uneven gas-liquid distribution, changes in branch resistance, localized frosting, differences in heat exchange load, or other reasons, the downstream pressure of the corresponding basic throttling orifice 205 in the evaporation branch 100 decreases, increasing the throttling pressure difference across the basic throttling orifice 205. Under the action of this throttling pressure difference, the valve core rod 203 overcomes the slippage of the elastic reset element 204, thereby changing the flow area of ​​the liquid replenishment channel 206. This allows the liquid-enriched refrigerant in the liquid replenishment chamber 202 to be replenished into the corresponding evaporation branch 100 in parallel with the basic throttling orifice 205 via the liquid replenishment channel 206.

[0039] After the liquid-phase enriched refrigerant is added to the evaporation branch 100, the amount of liquid refrigerant participating in evaporation and heat absorption in the evaporation branch 100 increases, the downstream pressure of the basic throttling orifice 205 increases, and the corresponding throttling pressure difference decreases. After the throttling pressure difference decreases, the driving force on the valve core rod 203 decreases, and the elastic reset member 204 pushes the valve core rod 203 to move in the reset direction, thereby reducing or closing the flow area of ​​the liquid replenishment channel 206. Figure 7 As shown, this embodiment forms a mechanical negative feedback process of "increased throttling pressure difference - sliding of valve core rod 203 - opening of liquid replenishment channel 206 - liquid phase enrichment of refrigerant replenishment - decreased throttling pressure difference - valve core rod 203 retraction".

[0040] Through the above structure, this embodiment can independently adjust the liquid phase compensation amount of each evaporation branch 100 according to the actual throttling pressure difference state. Compared with the existing fixed orifice liquid distribution structure, this embodiment can not only achieve basic liquid supply, but also perform directional liquid phase compensation for some evaporation branches 100 when the liquid supply to some evaporation branches 100 is insufficient, thereby improving the problem of uneven refrigerant mass flow rate and liquid phase distribution among multiple evaporation branches 100. Example 2

[0041] like Figure 6 As shown, this embodiment further defines the liquid phase pre-storage structure between the vapor-liquid separator 500, the liquid phase compensation pipe 400, and the liquid replenishment chamber 202 based on embodiment 1.

[0042] The interior of the vapor-liquid separator 500 is a liquid phase deposition chamber. The input end of the vapor-liquid separator 500 is located in the top, side or upper region of the liquid phase deposition chamber, the first output end is located in the middle or upper region of the liquid phase deposition chamber, and the second output end is located in the bottom region of the liquid phase deposition chamber.

[0043] After being throttled by the throttling device, the gas-liquid two-phase refrigerant enters the liquid phase deposition chamber from the inlet of the gas-liquid separator 500. Because the liquid phase deposition chamber has a certain expansion capacity relative to the inlet channel, the flow velocity of the gas-liquid two-phase refrigerant decreases upon entry. Refrigerant with a higher liquid content is more likely to accumulate in the bottom region of the liquid phase deposition chamber under the combined effects of gravity, inertia, and the reduced flow velocity. The main gas-liquid mixture can then enter the basic liquid distribution pipe 300 from the first outlet located in the middle or upper region.

[0044] The second output end is located at the bottom region of the liquid phase deposition chamber and is connected to the liquid phase compensation pipe 400. Therefore, the liquid-enriched refrigerant in the bottom region of the liquid phase deposition chamber can enter the liquid phase compensation pipe 400 under the action of refrigerant pressure, liquid column static pressure, and gravity in the vapor-liquid separator 500. The liquid phase compensation pipe 400 is connected to the replenishment chambers 202 of multiple distributors 200, allowing the liquid-enriched refrigerant to further enter each replenishment chamber 202.

[0045] When the liquid replenishment channel 206 is closed, the liquid replenishment path between each liquid replenishment chamber 202 and the corresponding evaporation branch 100 is cut off, and the liquid-enriched refrigerant cannot enter the evaporation branch 100 through the liquid replenishment channel 206. At this time, the liquid phase compensation pipe 400 and each liquid replenishment chamber 202 can temporarily store the liquid-enriched refrigerant from the bottom area of ​​the vapor-liquid separator 500, thereby forming a liquid phase compensation reserve to be released; the upper end of the liquid phase compensation pipe 400 faces the vapor-liquid separator 500 so that the air bubbles mixed in the liquid phase compensation pipe 400 can flow back to the vapor-liquid separator 500.

[0046] When the replenishment channel 206 corresponding to a certain evaporation branch 100 opens after the valve core rod 203 slides, the liquid-enriched refrigerant temporarily stored in the replenishment chamber 202 corresponding to that evaporation branch 100 can be replenished into the corresponding evaporation branch 100 in a timely manner through the replenishment channel 206 under the action of the pressure in the liquid phase compensation pipeline 400, the refrigerant pressure in the vapor-liquid separator 500, and the static pressure of the liquid column. After the replenishment channel 206 is closed, the liquid-enriched refrigerant in the liquid phase compensation pipeline 400 is replenished into the corresponding replenishment chamber 202 again, so that the replenishment chamber 202 is re-formed with a liquid phase compensation reserve to be released.

[0047] Through the coordination of the liquid phase deposition chamber, liquid phase compensation pipe 400, and liquid replenishment chamber 202 in this embodiment, the present invention can pre-form a temporary storage of liquid-enriched refrigerant when each liquid replenishment channel 206 is closed; when any evaporation branch 100 needs liquid replenishment, the liquid-enriched refrigerant temporarily stored in the corresponding liquid replenishment chamber 202 can be replenished into the evaporation branch 100 in a timely manner. Thus, the present invention does not simply replenish liquid temporarily through a bypass from the main flow, but forms a liquid phase pre-storage compensation structure through the liquid phase compensation pipe 400 and the liquid replenishment chamber 202, thereby improving the liquid replenishment response speed and liquid phase compensation effect for evaporation branches 100 with insufficient liquid supply.

[0048] It should be noted that when compensating for insufficient liquid supply in the evaporation branch 100, this invention prioritizes adding liquid-phase enriched refrigerant rather than simply adding gaseous refrigerant. This is because the heat exchange of the evaporator mainly relies on the heat absorption and evaporation of the liquid-phase refrigerant within the evaporation branch 100. When the liquid supply to a certain evaporation branch 100 is insufficient, there is usually a low proportion of liquid-phase refrigerant and insufficient effective evaporation heat-absorbing medium within that branch. If only gaseous refrigerant is added to that evaporation branch 100, although it may increase the local pressure in that branch, the gaseous refrigerant cannot provide the latent heat absorption capacity required for the evaporation of the liquid-phase refrigerant, and may also occupy the flow space within the evaporation branch 100, reducing the proportion of liquid-phase refrigerant entering that branch. Therefore, in this embodiment, a compensation path for liquid-enriched refrigerant is formed by the liquid-phase deposition chamber, the liquid-phase compensation pipe 400 and the liquid replenishment chamber 202, so that when the liquid replenishment channel 206 is opened, refrigerant with a higher liquid content is preferentially replenished to the evaporation branch 100 with insufficient liquid supply, thereby improving the effective evaporation heat absorption capacity of the evaporation branch 100. Example 3

[0049] In Example 2, the liquid replenishment chamber 202 can temporarily store the liquid-enriched refrigerant from the liquid phase compensation pipe 400; this example further illustrates how the liquid replenishment channel 206 releases the liquid-enriched refrigerant when the valve core rod 203 slides.

[0050] like Figure 7 As shown, the replenishment channel 206 is an annular groove located on the outer periphery of the valve core rod 203. A fixing sleeve 213 is fixedly installed inside the distributor 200. One end of the valve core rod 203 with the replenishment channel 206 is slidably inserted into the fixing sleeve 213. The fixing sleeve 213 remains fixed relative to the distributor 200, and the valve core rod 203 can slide relative to the fixing sleeve 213 in a preset direction.

[0051] like Figure 7 As shown, when the valve core rod 203 is in the initial position, the fixing sleeve 213 blocks the liquid replenishment channel 206, causing the liquid replenishment chamber 202 to be cut off from the corresponding evaporation branch 100. At this time, although the liquid phase compensation pipe 400 is connected to the liquid replenishment chamber 202, the liquid-enriched refrigerant in the liquid replenishment chamber 202 cannot enter the evaporation branch 100 in large quantities through the liquid replenishment channel 206. The evaporation branch 100 mainly obtains the gas-liquid mixed refrigerant through the basic throttling orifice 205.

[0052] like Figure 8As shown, when the throttling pressure difference across the basic throttling orifice 205 increases due to insufficient liquid supply in the corresponding evaporation branch 100, the valve core rod 203 slides towards the corresponding evaporation branch 100 under the action of this throttling pressure difference, overcoming the elastic reset member 204. After the valve core rod 203 slides, the liquid replenishment channel 206 crosses the blocking edge of the fixed sleeve 213 and connects with the corresponding evaporation branch 100. At this time, the liquid-enriched refrigerant in the liquid replenishment chamber 202 can be replenished into the corresponding evaporation branch 100 through the liquid replenishment channel 206.

[0053] As the sliding amount of valve core rod 203 increases, the area of ​​liquid replenishment channel 206 blocked by fixed sleeve 213 gradually decreases, and its exposed flow area gradually increases, thus causing the amount of liquid-enriched refrigerant replenished to change with the sliding amount of valve core rod 203. In this way, the opening degree of liquid replenishment channel 206 can be correlated with the throttling pressure difference change of the corresponding evaporation branch 100, realizing liquid replenishment adjustment according to the branch status.

[0054] When liquid-enriched refrigerant is added to the corresponding evaporation branch 100, the downstream pressure of the basic throttling orifice 205 of the evaporation branch 100 increases, and the throttling pressure difference decreases. After the throttling pressure difference decreases, the axial driving force on the valve core rod 203 decreases, and the elastic reset member 204 pushes the valve core rod 203 to reset in a direction away from the corresponding evaporation branch 100. During the reset process of the valve core rod 203, the liquid replenishment channel 206 gradually returns to the blocking range of the fixed sleeve 213, and the flow area of ​​the liquid replenishment channel 206 gradually decreases until it is closed or returns to a small opening state.

[0055] This embodiment utilizes the blocking and misalignment of the annular groove on the outer periphery of the valve core rod 203 by the fixed sleeve 213 to achieve the opening and closing of the liquid replenishment channel 206. The structure is simple and does not require an electronically controlled valve, sensor, or external drive mechanism. This structure is suitable for installation in the distributor 200 at the input end of the evaporation branch 100, enabling liquid replenishment regulation based on throttling pressure difference within a small space.

[0056] In other embodiments, the replenishment channel 206 can also be an axial groove, oblique groove, circumferential hole, or multiple spaced replenishment holes provided on the outer periphery of the valve core rod 203. The fixing sleeve 213 can also be replaced by a fixing ring, a fixing valve seat, or a shielding flange provided on the inner wall of the distributor 200. As long as the structure can shield the replenishment channel 206 when the valve core rod 203 is in the initial position and allow the replenishment channel 206 to communicate with the evaporation branch 100 after the valve core rod 203 slides, the technical effect of this embodiment can be achieved. Example 4

[0057] This embodiment further optimizes the flow area variation method of the replenishment channel 206 based on embodiment 3.

[0058] like Figure 5As shown, the replenishment channel 206 is an annular groove disposed on the outer periphery of the valve core rod 203. The annular groove includes a slow-opening section and a compensation section arranged sequentially along the sliding direction of the valve core rod 203. The flow area of ​​the slow-opening section is smaller than that of the compensation section, and the slow-opening section is gradually changing, so that the opening area of ​​the replenishment channel 206 gradually increases as the valve core rod 203 slides.

[0059] When the valve core rod 203 first begins to slip against the elastic reset element 204, the slow-opening section is exposed first. Because the flow area of ​​the slow-opening section is small and gradually changes, the liquid replenishment channel 206 can gradually open with a small opening, allowing the liquid-enriched refrigerant to enter the corresponding evaporation branch 100 at a small flow rate. This avoids a sudden large opening of the liquid replenishment channel 206, which would cause a large amount of liquid-enriched refrigerant to instantly enter the evaporation branch 100, thereby reducing pressure shocks in the branch and vibration of the valve core rod 203.

[0060] like Figure 8 As shown, when the liquid supply to the corresponding evaporator branch 100 is significantly insufficient, and the pressure difference across the basic throttling orifice 205 further increases, the valve core rod 203 continues to slide, and the compensation section gradually crosses the blocking edge of the fixed sleeve 213 and participates in the connection. Since the flow area of ​​the compensation section is larger than that of the slow-start section, it can provide a larger liquid replenishment flow area, allowing the liquid phase enriched with refrigerant in the liquid replenishment chamber 202 to replenish the corresponding evaporator branch 100 at a larger flow rate, thereby promptly improving the insufficient liquid supply state of the evaporator branch 100.

[0061] When liquid-enriched refrigerant is added, the downstream pressure of the basic throttling orifice 205 of the evaporation branch 100 gradually increases, the throttling pressure difference decreases, and the valve core rod 203 retracts under the action of the elastic reset element 204. During the retraction process, the compensation section is first gradually blocked by the fixing sleeve 213, reducing the high-flow compensation capacity of the liquid replenishment channel 206; subsequently, the slow-opening section is gradually blocked, and the liquid replenishment channel 206 enters a low-flow or closed state. Thus, both the liquid replenishment and closing processes have gradual characteristics.

[0062] By incorporating a slow-opening section and a compensation section, this embodiment enables the liquid replenishment channel 206 to adjust its flow area in stages according to the sliding amount of the valve core rod 203. In cases of slight liquid supply shortage, only the slow-opening section participates in liquid replenishment, achieving small flow rate and stable compensation. In cases of severe liquid supply shortage, the compensation section participates in liquid replenishment, providing a larger liquid phase compensation. This structure balances liquid replenishment stability and capacity, reduces valve core rod 203 vibration caused by two-phase refrigerant pressure fluctuations, and avoids pressure fluctuations in the evaporator branch 100 caused by sudden opening and closing of the liquid replenishment channel 206.

[0063] In one alternative embodiment, the slow-start section can be designed as an annular groove with gradually increasing width, an annular groove with gradually increasing depth, an oblique guide groove, or multiple replenishment holes with gradually increasing diameters. The compensation section can be designed as an annular groove with a larger width or multiple replenishment holes with large diameters. As long as the replenishment channel 206 can slide with the valve core rod 203 to achieve a gradual opening from a small flow rate to a large flow rate, the technical effect of this embodiment can be achieved.

[0064] Working principle: like Figure 6 As shown, when the device is working, the throttled gas-liquid two-phase refrigerant first enters the gas-liquid separator 500. The gas-liquid separator 500 divides the refrigerant into two paths. One path, a gas-liquid mixed refrigerant, enters the basic liquid distribution pipe 300 through the first output end, while the other path, a liquid-enriched refrigerant, enters the liquid-phase compensation pipe 400 through the second output end.

[0065] like Figure 7 As shown, the gas-liquid mixed refrigerant enters the distribution chamber 201 of each distributor 200 through the basic liquid distribution pipe 300, and then enters each evaporation branch 100 through the basic throttling orifice 205 on the corresponding valve core rod 203. The liquid-enriched refrigerant enters the liquid replenishment chamber 202 of each distributor 200 through the liquid phase compensation pipe 400. Under normal conditions, the valve core rod 203 is in its initial position under the action of the elastic reset member 204, the liquid replenishment channel 206 is blocked, and each evaporation branch 100 mainly relies on the basic throttling orifice 205 to obtain basic liquid supply.

[0066] like Figure 8 As shown, when the liquid supply to a certain evaporation branch 100 is insufficient, the downstream pressure of the corresponding basic throttling orifice 205 of the evaporation branch 100 decreases, and the throttling pressure difference on both sides of the basic throttling orifice 205 increases. This throttling pressure difference acts on the valve core rod 203, causing the valve core rod 203 to slide against the elastic reset element 204. After the valve core rod 203 slides, the flow area of ​​the liquid replenishment channel 206 increases, and the liquid-enriched refrigerant in the liquid replenishment chamber 202 is replenished into the corresponding evaporation branch 100 through the liquid replenishment channel 206.

[0067] After the liquid-phase enriched refrigerant is added, the proportion and mass flow rate of the liquid refrigerant in the corresponding evaporation branch 100 increase, the downstream pressure of the basic throttling orifice 205 of the evaporation branch 100 increases, and the throttling pressure difference decreases. After the throttling pressure difference decreases, the valve core rod 203 retracts under the action of the elastic reset element 204, reducing or closing the flow area of ​​the liquid replenishment channel 206. Thus, the present invention can independently compensate for insufficient liquid supply in branches according to the changes in the throttling pressure difference of each evaporation branch 100, and automatically reduce the replenishment amount after replenishment, thereby achieving dynamic flow equalization among multiple evaporation branches 100.

[0068] The above description is only a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention, based on the technical solution and inventive concept of the present invention, should be covered within the scope of protection of the present invention.

Claims

1. An air conditioning evaporator with a uniform flow distribution structure, characterized in that, include: Multiple evaporation branches (100); Multiple distributors (200) are installed at the input end of each of the evaporation branches (100), and each distributor (200) is provided with a flow distribution chamber (201), a liquid replenishment chamber (202) and a valve core assembly; A basic liquid distribution pipe (300) is connected to the distribution chamber (201) of a plurality of the distributors (200); Liquid phase compensation pipes (400) are respectively connected to the replenishment chambers (202) of the plurality of distributors (200); A vapor-liquid separator (500) has an input end, a first output end and a second output end. The first output end is connected to the basic liquid distribution pipe (300) and is used to output a vapor-liquid mixed refrigerant to the basic liquid distribution pipe (300). The second output end is connected to the liquid phase compensation pipe (400) and is used to output a liquid phase enriched refrigerant to the liquid phase compensation pipe (400). Each of the distributors (200) includes a valve core assembly comprising a slidable valve core rod (203) and an elastic reset member (204). The valve core rod (203) is provided with a basic throttling orifice (205) and a liquid replenishment channel (206). The basic throttling orifice (205) connects the distribution chamber (201) with the corresponding evaporation branch (100), so that the gas-liquid mixed refrigerant in the distribution chamber (201) enters the corresponding evaporation branch (100) through the basic throttling orifice (205), and a throttling pressure difference is formed on both sides of the basic throttling orifice (205). The valve core rod (203) overcomes the slippage of the elastic reset member (204) under the action of the throttling pressure difference, so as to change the flow area of ​​the liquid replenishment channel (206) and make the liquid phase enriched refrigerant in the liquid replenishment chamber (202) replenish the corresponding evaporation branch (100) in parallel with the basic throttling orifice (205) through the liquid replenishment channel (206).

2. An air conditioning evaporator with a uniform flow distribution structure according to claim 1, characterized in that: The basic throttling orifices (205) in the plurality of distributors (200) have equal flow areas, the effective pressure-bearing areas of the plurality of valve core rods (203) are equal, and the preload of the plurality of elastic reset members (204) is equal.

3. An air conditioning evaporator with a uniform flow distribution structure according to claim 1, characterized in that: The valve core rod (203) is provided with a pull rod (207) at its end. A spring seat (208) is slidably mounted on the surface of the pull rod (207). The elastic reset member (204) is a spring sleeved on the pull rod (207). The two ends of the spring abut against the valve core rod (203) and the spring seat (208) respectively. The distributor (200) is provided with a limiting step for limiting the position of the spring seat (208).

4. An air conditioning evaporator with a uniform flow distribution structure according to claim 1, characterized in that: The valve core rod (203) has a stepped structure. The surface of the valve core rod (203) is provided with a first sealing ring (209) and a second sealing ring (210). The first sealing ring (209) slides in contact with the inner wall of the diversion chamber (201), and the second sealing ring (210) slides in contact with the inner wall of the replenishment chamber (202).

5. An air conditioning evaporator with a uniform flow distribution structure according to claim 1, characterized in that: The valve core rod (203) is provided with a first pressure-bearing end face (211) and a second pressure-bearing end face (212). The basic throttling orifice (205) is provided through the valve core rod (203) along the axial direction. The two ends of the basic throttling orifice (205) are respectively provided on the first pressure-bearing end face (211) and the second pressure-bearing end face (212). The inlet end of the basic throttling orifice (205) faces the flow distribution chamber (201), and the outlet end of the basic throttling orifice (205) faces the corresponding evaporation branch (100). An effective pressure-bearing surface is formed between the first pressure-bearing end face (211) and the second pressure-bearing end face (212).

6. An air conditioning evaporator with a uniform flow distribution structure according to claim 1, characterized in that: The liquid-enriched refrigerant is added to the corresponding evaporation branch (100), which increases the downstream pressure of the basic throttling orifice (205) of the corresponding evaporation branch (100) and reduces the corresponding throttling pressure difference.

7. An air conditioning evaporator with a uniform flow distribution structure according to claim 1, characterized in that: The interior of the vapor-liquid separator (500) is a liquid phase deposition chamber. The input end is located in the top, side or upper region of the liquid phase deposition chamber, the first output end is located in the middle or upper region of the liquid phase deposition chamber, and the second output end is located in the bottom region of the liquid phase deposition chamber.

8. An air conditioning evaporator with a uniform flow distribution structure according to claim 1, characterized in that: The replenishment channel (206) is an annular groove provided on the outer periphery of the valve core rod (203). A fixing sleeve (213) is fixedly installed inside the distributor (200). One end of the valve core rod (203) with the replenishment channel (206) is slidably inserted into the fixing sleeve (213). When the valve core rod (203) is in the initial position, the fixing sleeve (213) blocks the liquid replenishment channel (206), so that the liquid replenishment chamber (202) is cut off from the corresponding evaporation branch (100), and the liquid replenishment chamber (202) temporarily stores the liquid-enriched refrigerant from the liquid phase compensation pipe (400); When the valve core rod (203) slides toward the direction of the corresponding evaporation branch (100), the liquid replenishment channel (206) passes over the blocking edge of the fixed sleeve (213) and connects with the corresponding evaporation branch (100), so that the liquid-phase enriched refrigerant temporarily stored in the liquid replenishment chamber (202) is replenished into the corresponding evaporation branch (100) through the liquid replenishment channel (206).

9. An air conditioning evaporator with a uniform flow distribution structure according to claim 8, characterized in that: The annular groove includes a slow-opening section and a compensation section arranged sequentially along the sliding direction of the valve core rod (203). The flow area of ​​the slow-opening section is smaller than that of the compensation section, and the slow-opening section is gradually changing, so that the opening area of ​​the liquid replenishment channel (206) gradually increases when the valve core rod (203) slides.

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