WO2020042964A1

WO2020042964A1 - Mobile air conditioner and heat exchanger system thereof

Info

Publication number: WO2020042964A1
Application number: PCT/CN2019/101486
Authority: WO
Inventors: 林晨; 岳宝; 刘和成; 大森宏
Original assignee: 广东美的白色家电技术创新中心有限公司; 美的集团股份有限公司
Priority date: 2018-08-31
Filing date: 2019-08-20
Publication date: 2020-03-05
Also published as: CN110873384A

Abstract

Disclosed are a mobile air conditioner and a heat exchanger system thereof. The heat exchanger system of the mobile air conditioner comprises: a first heat exchanger (100); a fan (200) for driving airflow to exchange heat with the first heat exchanger (100); a phase-change energy storage heat-exchange device (300), comprising a second heat exchanger (310) and a phase-change material capable of exchanging heat with the second heat exchanger (310); and heat pipes (400) in communication with the first heat exchanger (100) and the second heat exchanger (310), wherein a refrigerant can pass through the heat pipes (400) between the first heat exchanger (100) and the second heat exchanger (310) when the heat pipes (400) are connected. heat pipes (400) in communication with the first heat exchanger (100) and the second heat exchanger (310), wherein a refrigerant can pass through the heat pipes (400) between the first heat exchanger (100) and the second heat exchanger (310) when the heat pipes (400) are connected.

Description

Mobile air conditioner and heat exchanger system

This application claims priority from a Chinese patent application filed on August 31, 2018 with the Chinese Patent Office, application number 201811012902.1, and the invention name is "mobile air conditioner and its heat exchanger system", the entire contents of which are incorporated herein by reference. Applying.

Technical field

The present application relates to the field of mobile air conditioners, and in particular, to a heat exchanger system for a mobile air conditioner and a mobile air conditioner.

Background technique

Existing mobile air conditioners have the advantages of low cooling capacity, small size, and faster cooling effect than ordinary air conditioners in some areas. Mobile air conditioners have good mobility and can be easily moved to spaces and areas that require refrigeration, especially suitable for installation without outdoor units. Places such as offices and workshops in space can be plug-and-play, but in the process of implementing this application, the inventor found that the prior art has the following problems: Due to the compact arrangement of existing mobile air conditioners, the compressor noise during cooling operation will Brings noise pollution and affects user experience.

Summary of the Invention

In order to solve at least one of the above technical problems, an object of the present application is to provide a heat exchanger system for a mobile air conditioner.

Another object of the present application is to provide a mobile air conditioner having the heat exchanger system of the mobile air conditioner.

To achieve the foregoing object, an embodiment of the first aspect of the present application provides a heat exchanger system for a mobile air conditioner, including: a first heat exchanger; and a fan for driving airflow to exchange heat with the first heat exchanger; A phase change energy storage heat exchange device includes a second heat exchanger and a phase change material capable of exchanging heat with the second heat exchanger; a heat pipe is in communication with the first heat exchanger and the second heat exchanger When the heat pipe is turned on, a refrigerant can flow between the first heat exchanger and the second heat exchanger along the heat pipe.

In the heat exchanger system of the mobile air conditioner provided by the above embodiments of the present application, when a cooling mode is required, the first heat exchanger performs air-cooled heat exchange for evaporative cooling, and the second heat exchanger uses phase change materials to exchange heat from the second The heat exchanger absorbs heat for condensation. The first heat exchanger and the second heat exchanger are connected through a heat pipe. When the refrigerant in the second heat exchanger cools down and condenses into a liquid, the second heat exchanger can be realized by using a heat pipe. The low-temperature liquid refrigerant in the medium is actively sent to the first heat exchanger for evaporation, and at the same time, the heat pipe can also actively send the high-temperature refrigerant evaporated to the gaseous state in the first heat exchanger to the first heat exchanger for condensation. As a result, a refrigerant circulation circuit is formed between the first heat exchanger and the second heat exchanger through a heat pipe. While meeting the operating requirements of the refrigeration mode, the refrigeration work and refrigerant circulation drive in this structure do not need to be applied to the compressor. , Thereby avoiding the noise problem caused by the compressor operation during the refrigeration process, which can greatly improve the operation noise problem of mobile air conditioning refrigeration conditions, and the product has a better mute effect, especially suitable for rest and And other public occasions, mobile air-conditioning convenience, comfort advantages more fully to play.

In addition, the heat exchanger system of the mobile air conditioner in the above embodiments provided by the present application may also have the following additional technical features:

In the above technical solution, the heat pipe is arranged longitudinally or obliquely, and a portion of the heat pipe for connecting with the first heat exchanger is lower than a portion of the heat pipe for connecting with the second heat exchanger.

In this solution, the heat pipe is arranged longitudinally or obliquely, and the part of the heat pipe used to connect with the first heat exchanger is lower than the part used to connect with the second heat exchanger. In this way, the liquid inside the heat pipe is liquid The refrigerant can be sent to the first heat exchanger spontaneously by gravity, which can improve the efficiency of the refrigerant condensed into a liquid along the heat pipe to the first heat exchanger, which is conducive to ensuring the cooling efficiency, and can greatly reduce the residual amount of refrigerant in the heat pipe. Energy efficiency of mobile air-conditioning operation.

In a technical solution of the present application, the heat pipe is a coreless gravity heat pipe.

In this solution, the heat pipe is set as a coreless gravity heat pipe. It can be understood that when the heat pipe is longitudinally arranged or inclined at a sufficient angle, the refrigerant in the second heat exchanger can completely utilize itself through the siphon effect after condensing into a liquid state. Gravity potential energy can be used to enter the first heat exchanger along the coreless gravity heat pipe without having to set a liquid wick to drive by capillary action. In this way, the structure of the heat pipe is more simplified, and the residual amount of refrigerant in the heat pipe can be lower.

In a technical solution of the present application, the heat pipe is a cored heat pipe.

In this solution, the heat pipe is set as a cored heat pipe. It can be understood that a liquid wick is provided in the cored heat pipe, and a capillary channel is formed in the wick to spontaneously condense the second heat exchanger into a liquid refrigerant. The liquid is transported along the wick to the first heat exchanger for evaporation. In this way, the capillary action on the liquid refrigerant is formed. In this case, the heat pipe can be arranged horizontally according to requirements, instead of having to be longitudinal or inclined. The scope of application is wider, the limitations of the relative distribution form of the first heat exchanger and the second heat exchanger are also small, and the product design is more flexible.

In any one of the above technical solutions, a portion where the first heat exchanger is connected to the heat pipe is at a top end of the first heat exchanger or at a position near the top end of the first heat exchanger; and And / or the second heat exchanger is connected to the heat pipe at a bottom end of the second heat exchanger or at a position near the bottom end of the second heat exchanger; and / or the A second heat exchanger is located above the first heat exchanger.

In this solution, a portion where the first heat exchanger is connected to the heat pipe is provided at the top of the first heat exchanger or at a position adjacent to the top of the first heat exchanger. In this way, the first heat exchanger can be facilitated. The internal evaporation becomes a gaseous refrigerant, which is discharged along the heat pipe into the second heat exchanger to condense and cool down, so as to avoid the problem of local trapped gas in the first heat exchanger, which can help ensure that the first heat exchanger maintains efficient evaporation, thereby Ensure the cooling efficiency; the part where the second heat exchanger is connected to the heat pipe is located at the bottom end of the second heat exchanger or at a position close to the bottom end of the second heat exchanger, so as to ensure the second heat exchanger The position of the liquid part is relatively low, and the refrigerant condensed into a liquid state can be more fully discharged along the heat pipe into the first heat exchanger for evaporation and cooling, and the second heat exchanger will not retain liquid, thereby improving the cooling energy efficiency of the product; The heat exchanger is located above the first heat exchanger, with a more compact layout and a small horizontal dimension of the product. At the same time, this structural design is also more conducive to cooling the second heat exchanger into a liquid after the refrigerant has been discharged into the first. Heat Exchanger For evaporating, the second heat exchanger does not remain fluid, so as to enhance the energy efficiency of refrigeration products.

In any of the above technical solutions, the first heat exchanger has a refrigerant inlet, a refrigerant outlet, and a refrigerant pipeline provided between the refrigerant inlet and the refrigerant outlet of the first heat exchanger, and the first heat exchanger A plurality of first branch pipe interfaces are provided on the refrigerant pipeline, each of the first branch pipe interfaces is connected to the second heat exchanger through one of the heat pipes; and / or the second heat exchanger has a refrigerant An inlet, a refrigerant outlet, and a refrigerant pipeline provided between the refrigerant inlet and the refrigerant outlet of the second heat exchanger. The refrigerant pipeline of the second heat exchanger is provided with a plurality of second branch pipe interfaces. The second branch pipe interface is connected to the first heat exchanger through one of the heat pipes.

In this solution, a refrigerant pipe between the refrigerant inlet and the refrigerant outlet of the first heat exchanger is provided with a first branch pipe interface for connecting the heat pipe. In this way, in the first heat exchanger, the evaporation of the refrigerant pipe on the refrigerant pipe is completed. The refrigerant can be discharged directly along the heat pipe to the second heat exchanger, without having to complete the entire refrigerant pipeline in the first heat exchanger, and then discharged along the refrigerant inlet or the refrigerant outlet, the refrigerant flow resistance loss is smaller, and the first heat exchanger The refrigerant circulation between the second heat exchanger and the second heat exchanger is more efficient; a refrigerant pipe between the refrigerant inlet and the refrigerant outlet of the second heat exchanger is provided with a second branch pipe interface for connecting the heat pipe. The refrigerant that has been condensed on the refrigerant pipeline can be discharged directly to the first heat exchanger along the heat pipe, without having to complete the entire refrigerant pipeline in the second heat exchanger and discharged along the refrigerant inlet or the refrigerant outlet after the whole process. The refrigerant flow resistance The loss is smaller, and the refrigerant flow between the first heat exchanger and the second heat exchanger is more efficient.

In the above technical solution, the refrigerant pipeline of the second heat exchanger includes: a second heat exchange tube, which is in communication with the refrigerant inlet and the refrigerant outlet of the second heat exchanger; On the lower side of the second heat exchange tube, the merging pipeline has inlets and outlets, and the number of the inlets is more than the outlets, and an inside of the merging pipeline is formed to extend from the inlet to the outlet and Converging in the channel of the outlet, wherein each of the inlets is connected to the second heat exchange tube, and the outlet serves as the second branch tube interface.

In this solution, the refrigerant pipeline in the second heat exchanger is provided including a second heat exchange pipe and a plurality of converging pipes, so that multiple inlets of the confluence pipe are connected to the second heat exchange pipe so as to run along the multiple inlets, respectively. After the liquid refrigerant in the second heat exchange tube is collected, the collected liquid refrigerant is collected through the merging pipe and then concentratedly discharged to the first heat exchanger along the heat pipe. In this way, the design can be made without excessively increasing the number of heat pipes. The number of liquid refrigerant collection points in the second heat exchange tube is greater, and the distribution of the collection points can be more extensive and uniform. Accordingly, the refrigerant is condensed into a liquid in the second heat exchange tube and discharged to the second heat exchange tube. The length of the detention period and the flow path are effectively shortened, which can ensure sufficient and efficient rehydration of the first heat exchanger, and promote the improvement of the refrigerant circulation efficiency between the first heat exchanger and the second heat exchanger, especially when the compressor is not driven. In the occasion, it can be more conducive to ensuring refrigeration reliability and refrigeration efficiency.

In the above technical solution, the second heat exchange pipe includes a plurality of branch pipes, and the plurality of branch pipes are connected in parallel, and each of the branch pipes communicates with a refrigerant inlet and a refrigerant outlet of the second heat exchanger, and each of the The branch pipe is connected to one or more of said inlets.

In this solution, the second heat exchange tube is provided including a plurality of branch pipes, and the plurality of branch pipes are connected in parallel, so that the specific surface area of the second heat exchanger can be improved, the condensation efficiency of the refrigerant in the second heat exchanger can be improved, and It is beneficial for the heat exchange surface of the second heat exchanger to be dispersed in the phase change material, so that the phase change material is evenly heated. In this way, the product evaporation temperature is more uniform, and the cooling capacity utilization of the phase change material is higher.

In the above technical solution, the branch pipe is in a serpentine shape, and includes a straight pipe section, a bottom elbow at a bottom end of the straight pipe section, and a top elbow at a top end of the straight pipe section, the inlet and the bottom elbow of the branch pipe. connection.

In this solution, the branch pipe is provided in a serpentine shape, more specifically in the shape of a long snake. Specifically, the branch pipe is arranged longitudinally or generally longitudinally, so that the straight pipe section portion is generally along the longitudinal direction, and the top elbow is located at the top of the straight pipe section. , The bottom elbow is located at the bottom end of the straight pipe section, and a plurality of horizontally arranged straight pipe sections are alternately connected two by two by using the top elbow and the bottom elbow to construct the serpentine branch pipe, wherein the branch pipe is arranged longitudinally Or it can be arranged in a longitudinal direction to facilitate the downward convergence of the refrigerant in the branch pipe. In this solution, the inlet is connected to the bottom elbow of the branch pipe, and the bottom elbow can be used to converge the refrigerant flowing down the straight pipe section at its two ends. The rear edge is then discharged into the inlet. At the same collection efficiency, the number of imports is simplified, and the structure is more simplified. The structure is also conducive to exhausting the liquid refrigerant in the branch pipe to avoid residual liquid refrigerant in the branch pipe.

In any of the above technical solutions, the converging pipeline includes: a plurality of first-stage tees, the first-stage tee has three interfaces, and two of the interfaces serve as the inlets, and the remaining The interface is used as a junction; a plurality of second-stage tees, and the second-stage tee has three interfaces, and two of the interfaces correspond to the two-stage tees. Connection, the other interface of the second-stage tee serves as the outlet.

In this solution, a multi-stage junction structure composed of a combination of a first-stage tee and a second-stage tee is provided for the merging pipeline, so that the design can greatly increase the number of pairs without increasing the number of heat pipes. The number of liquid refrigerant collection points in the second heat exchange tube also further makes the distribution of the collection points more extensive and uniform. In this way, the residence time and flow path of the refrigerant after it is condensed in the second heat exchanger to the discharge stage are more It is shorter, which is more conducive to ensuring the reliability and efficiency of refrigeration. The three-level confluence formed by the two-stage confluence structure combined with the confluence effect of the bottom elbow of the branch pipe itself can basically meet the refrigeration conditions of existing mobile air conditioners. Maximum refrigerant circulation volume and maximum cycle efficiency requirements, and can achieve compact product structure.

In any of the above technical solutions, the refrigerant pipeline of the first heat exchanger includes: a first heat exchange tube, which is in communication with the refrigerant inlet and the refrigerant outlet of the first heat exchanger; and an outlet interface is located in the first The top of the heat exchange tube is in communication with the first heat exchange tube, and the outlet interface is used as the first branch tube interface.

In the above technical solution, the first heat exchange tube includes a plurality of parallel pipelines including a plurality of branches and a main pipe provided at both ends of the plurality of branches; a plurality of connecting pipes and a plurality of the parallel pipes; The main pipes of the pipeline are connected by the connecting pipe, so that a plurality of the parallel pipes of the first heat exchange pipe are connected in series, wherein one or more of the plurality of connecting pipes are connected to each other. The lead-out interface is provided.

In this solution, an outlet interface is provided as a first branch pipe interface on a connection pipe for connecting in parallel and parallel pipelines. At this time, the first branch pipe interface of the connection pipe can have a confluence effect, such as connecting to it. After the gaseous refrigerants in the parallel pipes at both ends converge to the connection pipe, they are discharged through the heat pipe to the second heat exchanger through the first branch pipe connection of the connection pipe. This design can make the The number of gaseous refrigerant collection points in the first heat exchange tube is greater, and the distribution of the collection points can be more extensive and uniform. Accordingly, the refrigerant is condensed into a liquid in the first heat exchange tube and discharged to the first heat exchange tube. The length of residence period and flow path are effectively shortened, which can ensure sufficient and efficient air supply to the second heat exchanger, and promote the improvement of the refrigerant circulation efficiency between the first heat exchanger and the second heat exchanger, especially when there is no compressor. In driving applications, it is more conducive to ensuring refrigeration reliability and refrigeration efficiency.

In the above technical solution, the branches in the parallel pipeline are arranged longitudinally or obliquely, and the top ends of multiple branches form a first main pipe, and the bottom ends of multiple branches form a second main pipe. Wherein, the connecting pipe is connected between the first main pipes of a plurality of parallel pipelines, and the connecting pipe connected to the first main pipe is provided with the lead-out interface.

In this solution, the branches in the parallel pipeline are arranged longitudinally or at an inclined arrangement. In this way, after the refrigerant in the parallel pipeline evaporates to a gaseous state, the branches can be directly moved up or down along the branches arranged longitudinally or obliquely. The first main pipe at the top is discharged into the heat pipe along the lead-out interface of the connecting pipe connected to the first main pipe. In this way, the flow trajectory of the refrigerant after vaporization basically faces upward, the flow resistance of the gaseous refrigerant is small, and the loss of kinetic energy is small. The heat supply of the heat exchanger is sufficient and efficient, which promotes the improvement of the refrigerant circulation efficiency between the first heat exchanger and the second heat exchanger, especially in the case of no compressor drive, which can be more conducive to ensuring refrigeration reliability and efficiency.

In any of the above technical solutions, the entire first heat exchanger is inclined with respect to a longitudinal plane, and a predetermined angle is formed between the first heat exchanger and the longitudinal plane.

In this solution, the entire first heat exchanger is set to be inclined with respect to the longitudinal plane. More specifically, for example, the first heat exchanger is a fin heat exchanger, and the airflow penetrates the fin heat exchanger from the inner surface of the fin heat exchanger to exchange heat. The rear of the heat exchanger is discharged along the outer surface of the fin heat exchanger, and the airflow realizes heat exchange with the airflow during the process of penetrating the fin heat exchanger. The first heat exchanger as a whole is inclined relative to the longitudinal plane, which can be specifically understood as The inner or outer surface of the fin heat exchanger is inclined with respect to the longitudinal plane and has a predetermined included angle, so that the cold wind can be blown out at a certain angle, avoiding direct horizontal blow, and preferably blown out toward the inclined, wherein the more preferably the preset included angle is based on the first The position of a heat exchanger is highly designed, so that the cold air blown can point at the user's torso, and the user experience is better.

In any of the above technical solutions, the heat exchanger system of the mobile air conditioner further includes: a valve, and the heat pipe is connected with the valve for controlling the on or off of the heat pipe.

In this solution, a valve is provided to control the on or off of the heat pipe. In this way, there is no need to use a heat pipe to transport the refrigerant between the first heat exchanger and the second heat exchanger to realize the first heat exchanger and the second heat exchanger. When the refrigerant is circulated between the radiators, the valve can be controlled to stop the heat pipe from conducting. At this time, the refrigerant circulation can be performed between the first heat exchanger and the second heat exchanger based on the refrigerant circulation mode in the traditional air conditioner. The product working mode Can be more diverse.

In the above technical solution, the heat exchanger system of the mobile air conditioner further includes: an opening degree adjustment mechanism connected to the valve for adjusting the opening degree of the valve.

In this solution, an opening degree adjusting mechanism is provided for adjusting the opening degree of the valve. In this way, the opening degree of the valve can be adjusted by the opening degree adjusting mechanism, so as to control the distance between the first heat exchanger and the second heat exchanger accordingly. Refrigerant cycle efficiency is used to achieve the purpose of controlling refrigeration efficiency. For example, when there is a high demand for refrigeration efficiency, you can increase the opening of the valve and increase the evaporation efficiency in the first heat exchanger accordingly, thereby increasing the refrigeration efficiency, and vice versa. When the demand for refrigeration efficiency is low, the opening degree of the valve can be reduced to correspondingly lower the evaporation efficiency in the first heat exchanger, thereby lowering the refrigeration efficiency, or for refrigeration workers with a large total amount of cold storage in the phase change material. In the early stage of operation, due to the high heat absorption efficiency of the phase change material for the second heat exchanger, the valve opening can be reduced. As the operating time of the refrigeration mode accumulates, the total amount of cold storage in the phase change material decreases, and the phase change The heat absorption efficiency of the material on the second heat exchanger is correspondingly reduced. At this time, the valve opening degree can be increased to make the cooling output in the early and late refrigeration conditions substantially uniform.

It can be understood that the opening degree adjustment mechanism can be an electronically controlled structure for adjusting the valve opening degree, such as a mobile terminal, a control panel, and an electronic control knob. The output signals of the mobile terminal and the control panel are used to control valves such as solenoid valves to change the valve. The opening degree, the opening degree adjusting mechanism may be a structure for mechanically adjusting the opening degree of the valve, such as an operating handle, an operating handle connection or a mechanical valve such as a flap valve as a valve connected through a transmission mechanism to adjust the opening degree of the mechanical valve accordingly.

In the above technical solution, the valve has a valve body, the valve body has a first interface and a second interface, the valve body is arranged obliquely and the position of the first interface is higher than the second interface, wherein, The first interface is connected to the second heat exchanger, and the second interface is connected to the first heat exchanger.

In this solution, the valve body of the valve is arranged obliquely and the position of the first interface is higher than that of the second interface, which is conducive to the spontaneous flow of the liquid refrigerant inside the valve to the first heat exchanger, and helps heat pipes such as gravity heat pipes to change more. It can effectively play the role of conduction, improve the refrigerant circulation efficiency between the first heat exchanger and the second heat exchanger, and at the same time, avoid the refrigerant remaining in the valve body, and improve the energy efficiency of the product.

In any one of the above technical solutions, the heat exchanger system of the mobile air conditioner further includes: a first heat insulation member, wherein the phase change energy storage heat exchange device further includes a container, and the first heat insulation member heats the container. An accommodation space is formed inside the container, and the phase change material is located in the accommodation space; and / or a second heat insulation member is provided on the heat pipe and heat-insulates the heat pipe.

In this solution, a first heat insulation member is provided to heat the container of the phase change energy storage and heat exchange device for holding the phase change material. For example, the first heat insulation member is designed as a heat insulation sleeve made of cotton, sponge, etc. Insulation of the container on the outside of the container can reduce the loss of phase change material and improve the energy efficiency of the product. Set a second insulation member to heat the heat pipe. For example, design the second insulation member as a thermal insulation jacket made of cotton, sponge, etc. Putting a jacket on the outside of the heat pipe to heat the heat pipe can reduce the self-vaporization and heating of the refrigerant inside the heat pipe during transmission, and improve the energy efficiency of the product.

An embodiment of the second aspect of the present application provides a mobile air conditioner, including the heat exchanger system of the mobile air conditioner described in any one of the foregoing technical solutions.

The mobile air conditioner provided by the embodiment of the second aspect of the present application has all the above beneficial effects by being provided with the heat exchanger system of the mobile air conditioner described in any of the above technical solutions, which is not repeated here.

In addition, the mobile air conditioner in the above embodiments provided by the present application may also have the following additional technical features:

In the above technical solution, the mobile air conditioner further includes: a compressor having a return air port and an exhaust port, the exhaust port is in communication with the refrigerant inlet of the first heat exchanger, and the return port is in communication with the second The refrigerant outlet of the heat exchanger is in communication; the throttling element is in communication with the refrigerant outlet of the first heat exchanger and the refrigerant inlet of the second heat exchanger.

In this solution, a compressor and a throttling element are connected to the first heat exchanger and the second heat exchanger to form a circuit. When the phase change material is saturated and needs to be regenerated and stored, the mobile air conditioner can be moved outdoors or In other places where there is no need for refrigeration, at this time, the control of the heat pipe is cut off and the compressor is controlled to run. At this time, the refrigerant discharged by the compressor flows through the first heat exchanger, the throttling element, the second heat exchanger in sequence, and finally returns to The compressor completes the refrigerant cycle, and in this process, the first heat exchanger acts as a condenser, the second heat exchanger acts as an evaporator, and the refrigerant evaporates at the second heat exchanger to absorb heat from the phase change material and store the phase change material. Compared with natural regeneration, regeneration takes less time, and compared with regeneration through refrigeration equipment such as refrigerators, the user's workload is reduced and the use is more convenient.

In the above technical solution, the compressor is arranged below the heat exchanger system of the mobile air conditioner; and / or the throttling element is connected to a refrigerant inlet of the second heat exchanger through a pipe, and the A third insulation member is provided at the connection between the throttling element and the pipeline, and the pipeline is insulated by the third insulation member; and / or an air suction pipe is connected to the return port of the compressor, and The suction pipe is in communication with the refrigerant outlet of the second heat exchanger, wherein the suction pipe is wound around the throttling element, and / or a fourth heat insulation member is provided at the suction pipe And the suction pipe is insulated by the fourth heat insulation member, and / or the mobile air conditioner includes a regenerator connected to the suction pipe and a refrigerant outlet of the second heat exchanger.

In this solution, the compressor is arranged below the heat exchanger system of the mobile air conditioner. In this way, the horizontal dimension of the product is smaller, the structure is more compact, and it is conducive to the downward movement of the center of gravity of the product. It is more stable when the product is placed, and it is also beneficial to reduce compression. When the machine is running, the whole machine amplitude improves the product quality.

A third heat insulation element is provided on the pipe between the throttling element and the refrigerant inlet of the second heat exchanger, and the joint between the throttling element and the pipe is provided with a third heat insulation member, for example, the third heat insulation member is designed to be insulation cotton, sponge, etc. Insulation jacket made of material, which is placed on the outside of the pipe and outside of the joint between the pipe and the throttling element to heat it, can improve the evaporation efficiency of the refrigerant, thereby improving the regeneration efficiency of the phase change material, shortening the regeneration time and reducing energy Consuming.

An air suction pipe is connected to the return port of the compressor. The air suction pipe is in communication with the refrigerant outlet of the second heat exchanger, and the air suction pipe is wound around the throttling element. The internal refrigerant is fully vaporized to avoid the compressor from entering the liquid and prevent liquid strike.

An air suction pipe is connected to the return port of the compressor, and the air suction pipe is in communication with the refrigerant outlet of the second heat exchanger, and a fourth heat insulation member is provided at the air suction pipe, and the air suction pipe is insulated by the fourth heat insulation member, for example, Design the fourth insulation piece is a thermal insulation sleeve made of cotton, sponge, etc., and put it on the outside of the suction pipe to keep it warm. This can suppress the heat absorption from the environment at the suction pipe and avoid excessive return air temperature. High, improve compressor working efficiency.

An air suction pipe is connected to the air return port of the compressor, and the air suction pipe is in communication with the refrigerant outlet of the second heat exchanger, and the mobile air conditioner further includes a heat exchanger, which is connected to the air suction pipe and the second heat exchanger. The refrigerant outlet of the compressor is reheated by a regenerator to prevent the compressor from entering the liquid and prevent liquid strike.

Additional aspects and advantages of the application will become apparent in the following description, or be learned through practice of the application.

BRIEF DESCRIPTION OF THE DRAWINGS

The above and / or additional aspects and advantages of the present application will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

1 is a schematic structural diagram of a heat exchanger system according to an embodiment of the present application;

2 is a schematic side structural view of a heat exchanger system according to an embodiment of the present application;

3 is a schematic structural diagram of a heat exchanger system according to an embodiment of the present application;

4a is a schematic front structural view of a part of a structure of a second heat exchanger according to an embodiment of the present application;

4b is a schematic plan view of the structure of a portion of the second heat exchanger shown in FIG. 4a;

FIG. 4c is a left-view structural schematic diagram of a part of the structure of the second heat exchanger shown in FIG. 4a; FIG.

FIG. 5a is a schematic front structural view of a part of a structure of a first heat exchanger according to an embodiment of the present application; FIG.

FIG. 5b is a bottom view of the first heat exchanger structure shown in FIG. 5a;

FIG. 5c is a left-side structural schematic diagram of the structure of the first heat exchanger shown in FIG. 5a; FIG.

6 is a schematic structural diagram of a mobile air conditioner according to an embodiment of the present application;

FIG. 7 is a schematic structural diagram of a mobile air conditioner in an outdoor ice storage mode according to an embodiment of the present application.

Wherein, the correspondence between the reference numerals in FIG. 1 to FIG. 7 and the component names is:

100 first heat exchanger, 111 refrigerant inlet-A, 112 refrigerant outlet-A, 120 refrigerant pipeline-A, 121 first heat exchange tube, 1211 parallel pipeline, 1211a branch, 1211b first supervisor, 1211c second supervisor , 1212 connecting pipe, 122 outlet interface, 123 first branch pipe interface, 200 fan, 300 phase change energy storage heat exchange device, 310 second heat exchanger, 311 refrigerant inlet-B, 312 refrigerant outlet-B, 313 refrigerant pipeline -B, 3131 second heat exchange pipe, 31311 branch pipe, 31311a straight pipe section, 31311b bottom elbow, 31311c top elbow, 3132 confluence pipe, 3132a inlet, 3132b outlet, 3132c first stage tee, 3132d second stage Tee, 3133 second branch pipe connection, 400 heat pipe, 500 valve, 510 valve body, 520 first connection, 530 second connection, 600 compressor, 610 return port, 620 exhaust port, 700 throttle element, 800 suction trachea.

detailed description

In order to more clearly understand the foregoing objectives, features, and advantages of the present application, the present application is described in further detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, in the case of no conflict, the embodiments of the present application and the features in the embodiments can be combined with each other.

In the following description, many specific details are set forth in order to fully understand the present application. However, the present application can also be implemented in other ways than those described herein. Therefore, the scope of protection of the present application is not limited to the specifics disclosed below. Limitations of Examples.

The following describes a mobile air conditioner and a heat exchanger system thereof according to some embodiments of the present application with reference to FIGS. 1 to 7.

As shown in FIG. 1 to FIG. 5 c, a heat exchanger system for a mobile air conditioner provided by an embodiment of the first aspect of the present application includes: a first heat exchanger 100, a fan 200, a phase-change energy storage heat exchange device 300, and a heat pipe 400 .

Specifically, as shown in FIG. 1, a fan 200 is used to drive airflow to exchange heat with the first heat exchanger 100; the phase-change energy storage heat exchange device 300 includes a second heat exchanger 310 and can be exchanged with the second heat exchanger 310 Hot phase change material; the heat pipe 400 communicates with the first heat exchanger 100 and the second heat exchanger 310, and when the heat pipe 400 is turned on, the refrigerant can pass along the heat pipe 400 in the first heat exchanger 100 and the second heat exchanger 310 Between circulation.

It is worth noting that the heat pipe 400 in this solution is a heat pipe structure with two ends not closed, and the two ends of the heat pipe 400 are connected to the first heat exchanger 100 and the second heat exchanger 310 respectively. The heat exchanger 100 and the second heat exchanger 310 play a communication role, and the heat pipe 400 does not need to be additionally filled with a heat-carrying medium. Instead, the heat exchangers in the first heat exchanger 100 and the second heat exchanger 310 are directly used. The refrigerant is used as a heat carrier medium. When the heat exchanger system operates in the cooling mode, the first heat exchanger 100 is used as the evaporation end of the heat pipe, and the second heat exchanger 310 is used as the condensation end of the heat pipe, as shown in Figures 1 and 3. As shown by the dashed arrows, the vaporized refrigerant in the first heat exchanger 100 carries latent heat through the heat pipe 400 and is transferred to the second heat exchanger 310 in the direction of the dashed arrow. Thereafter, the The gaseous refrigerant condenses by releasing the latent heat to the phase change material through the second heat exchanger 310. Subsequently, as shown by the solid arrows in FIG. 1 and FIG. 3, the condensed refrigerant in the second heat exchanger 310 passes through the heat pipe 400 as shown in FIG. Effects such as siphon or capillary are sent along the heat pipe 400 in the direction of the solid arrow back to the first In the heat exchanger 100, to thereby form a refrigerant cycle, while complete evaporation of the working of the first heat exchanger 100 and the second heat exchanger 310 is condensed working.

The advantages of the heat exchanger system of the mobile air conditioner provided by the foregoing embodiments of the present application are:

(1) The second heat exchanger 310 exchanges heat with the phase-change material. In this way, the heat emitted by the second heat exchanger 310 can be absorbed by the phase-change material, so there is no need to drain the heat through a thick connection pipe to move the heat. The advantage of more flexibility and convenience, and the phase change material can directly absorb the heat of the second heat exchanger 310 for storage, and the mobile air conditioner generates less heat to the indoor environment during the indoor cooling process, and the energy efficiency of the cooling operation is more efficient. high;

(2) The first heat exchanger 100 and the second heat exchanger 310 are connected through a heat pipe 400. After the refrigerant in the second heat exchanger 310 cools down and condenses into a liquid, the second heat exchanger 310 can be realized by using the heat pipe 400 The low-temperature liquid refrigerant in the medium is transferred to the first heat exchanger 100 for evaporation, and at the same time, the heat pipe 400 can also transfer the high-temperature refrigerant evaporated into the gaseous state in the first heat exchanger 100 to the first heat exchanger 100 for Condensation, so as to realize refrigerant circulation through the heat pipe 400 between the first heat exchanger 100 and the second heat exchanger 310, the structure is simple, and at the same time that it meets the operating requirements of the refrigeration condition, the refrigerant to the vapor and liquid is realized through the heat pipe 400 The transmission between the first heat exchanger 100 and the second heat exchanger 310 has high efficiency and reliability, and the entire refrigeration work and refrigerant cycle driving need not be applied to the compressor 600, thereby avoiding the compressor 600 during the refrigeration process. The noise problem caused by operation can greatly improve the operation noise problem of mobile air-conditioning refrigeration conditions. The product has a better mute effect, especially suitable for rest and office occasions. The convenience and comfort advantages of mobile air-conditioning are more fully obtained. Play;

(3) The refrigerant cools the indoor air through the first heat exchanger 100 and airflow heat exchange. Compared with ordinary air conditioning fans and other products, the problem of high humidity of cold air does not occur, and it is more comfortable and healthy to use.

Optionally, the number of the heat pipes 400 may be single or multiple.

In one embodiment of the present application, preferably, the phase change material is ice. Among them, the phase change material has a small temperature fluctuation in the phase change area, and the phase change material is used to exchange heat with the second heat exchanger 310. Compared with air-cooled heat exchange, it can not only achieve energy storage heat exchange, but also reduce the second heat exchange. The heat dissipation capacity of the radiator 310 to the environment has the advantages of high heat exchange efficiency and good temperature stability, which is conducive to controlling the product to operate at the ideal evaporation temperature and condensation temperature, and improve the cooling efficiency of the system. Among them, the ice storage density is relatively low The phase change material is relatively high, about 330kJ / kg, and the phase change material is set to ice. Under the same conditions, it can help to extend the single effective operation time of the refrigeration mode and the cost is low.

In an embodiment of the present application, preferably, the heat pipe 400 is arranged longitudinally or obliquely, and a part of the heat pipe 400 for connecting with the first heat exchanger 100 is lower than a part of the heat pipe 400 for connecting with the second heat exchanger 310. In this way, the liquid refrigerant inside the heat pipe 400 can be sent to the first heat exchanger 100 spontaneously by virtue of gravity, which can improve the efficiency of the refrigerant condensed into a liquid to be conveyed along the heat pipe 400 to the first heat exchanger 100, which is helpful for ensuring the cooling efficiency and can The residual amount of refrigerant in the heat pipe 400 is greatly reduced, and the energy efficiency of the mobile air conditioner is ensured.

In one embodiment of the present application, the heat pipe 400 is a coreless gravity heat pipe. It can be understood that when the heat pipe 400 is arranged longitudinally or inclined at a sufficient angle, the refrigerant in the second heat exchanger 310 is completely condensed after it is condensed into a liquid state. The siphon effect can be used to realize the entry of the first heat exchanger 100 along the coreless gravity heat pipe by using its own gravitational potential energy, instead of having to set the liquid wick to drive by capillary action. In this way, the structure of the heat pipe 400 is more simplified, and the refrigerant residue in the heat pipe 400 Can also be lower.

In one embodiment of the present application, the heat pipe 400 is a cored heat pipe. It can be understood that the cored heat pipe is provided with a liquid wick, and a capillary channel is formed in the liquid wick to spontaneously transfer the heat exchanger 310 into the second heat exchanger 310. The refrigerant condensed into a liquid is transported along the wick to the first heat exchanger 100 for evaporation. In this way, the driving effect of capillary action on the liquid refrigerant is formed. In this case, the heat pipe 400 can be arranged horizontally according to demand, and It does not have to be longitudinal or inclined, has a wider application range, has less limitations on the relative distribution form of the first heat exchanger 100 and the second heat exchanger 310, and has more flexible product design.

In any of the above embodiments, preferably, the portion where the first heat exchanger 100 is used to connect with the heat pipe 400 is located at the top of the first heat exchanger 100 or at a position near the top of the first heat exchanger 100. It can help to promote the evaporation of the refrigerant in the first heat exchanger 100 into a gaseous state along the heat pipe 400 into the second heat exchanger 310 for condensation and temperature reduction, and avoid the problem of local trapped gas in the first heat exchanger 100. It is beneficial to ensure that high-efficiency evaporation is maintained in the first heat exchanger 100, thereby ensuring refrigeration efficiency.

In any of the above embodiments, preferably, the portion of the second heat exchanger 310 for connecting with the heat pipe 400 is located at the bottom end of the second heat exchanger 310 or at a position adjacent to the bottom end of the second heat exchanger 310. This can ensure that the liquid drain position of the second heat exchanger 310 is relatively low, and the refrigerant condensed into a liquid state can be more fully discharged into the first heat exchanger 100 along the heat pipe 400 for evaporative cooling. The second heat exchanger 310 does not Residual liquid accumulation, which improves the cooling energy efficiency of the product.

In any of the above embodiments, preferably, the second heat exchanger 310 is located above the first heat exchanger 100, the layout is more compact, and the lateral size of the product is small. At the same time, such a structural design is more conducive to the second heat exchanger The refrigerant condensed into a liquid state in the heat exchanger 310 can be discharged into the first heat exchanger 100 as much as possible for evaporation, and the second heat exchanger 310 will not retain the accumulated liquid, thereby improving the refrigeration energy efficiency of the product.

In any of the above embodiments, as shown in FIG. 3, the first heat exchanger 100 has a refrigerant inlet-A 111, a refrigerant outlet-A 112, and a refrigerant pipe provided between the refrigerant inlet-A 111 and the refrigerant outlet-A 112 Road-A120, the refrigerant pipe-A of the first heat exchanger 100 is provided with a plurality of first branch pipe interfaces 123, and each first branch pipe interface 123 is connected to the second heat exchanger 310 through a heat pipe 400, where By setting a refrigerant pipeline-A between the refrigerant inlet-A 111 and the refrigerant outlet-A 112 of the first heat exchanger 100, a first branch pipe interface 123 is provided for connecting the heat pipe 400 in the middle, so that the first heat exchanger 100 In the refrigerant pipe-A 120, the refrigerant that has been evaporated can be discharged directly along the heat pipe 400 to the second heat exchanger 310 without having to go through the entire refrigerant pipe-A 120 in the first heat exchanger 100. Discharge along the refrigerant inlet-A111 or refrigerant outlet-A112, the refrigerant flow resistance loss is smaller, and the refrigerant circulation between the first heat exchanger 100 and the second heat exchanger 310 is more efficient.

In any of the above embodiments, as shown in FIG. 3, the second heat exchanger 310 has a refrigerant inlet-B, a refrigerant outlet-B, 312, and a refrigerant pipe provided between the refrigerant inlet-B, 311 and the refrigerant outlet-B, 312 Road-B, 313, and the refrigerant pipe-B of the second heat exchanger 310 are provided with a plurality of second branch pipe interfaces 3133. Each second branch pipe interface 3133 is connected to the first heat exchanger 100 through a heat pipe 400. By setting a refrigerant pipe-B between the refrigerant inlet-B of the second heat exchanger 310 and the refrigerant outlet-B of the second heat exchanger 310, a second branch pipe interface 3133 is provided for connecting the heat pipe 400 in the middle, so that the second heat exchanger In 310, the refrigerant that has been condensed on the refrigerant pipe-B 313 can be discharged directly to the first heat exchanger 100 along the heat pipe 400 without going through the entire refrigerant pipe-B 313 in the second heat exchanger 310. The trailing refrigerant inlet-B 311 or refrigerant outlet-B 312 is discharged, the refrigerant flow resistance loss is smaller, and the refrigerant circulation between the first heat exchanger 100 and the second heat exchanger 310 is more efficient.

In any of the above embodiments, as shown in FIG. 4a, FIG. 4b, and FIG. 4c, the refrigerant pipe-B of the second heat exchanger 310 includes a second heat exchange pipe 3131 and a plurality of converging pipes 3132. The heat pipe 3131 communicates with the refrigerant inlet-B and the refrigerant outlet-B 312 of the second heat exchanger 310; a plurality of merge pipes 3132 are located below the second heat exchange pipe 3131, and the merge pipe 3132 has an inlet 3132a and an outlet 3132b. The number of inlets 3132a is more than that of outlets 3132b, and a passage extending from inlet 3132a to outlet 3132b and converging at outlet 3132b is formed inside the convergence pipe 3132, where each inlet 3132a is connected to the second heat exchange tube 3131, and the outlet 3132b serves as the second branch pipe connection 3133.

Among them, by setting the refrigerant pipeline-B in the second heat exchanger 310 to include a second heat exchange pipe 3131 and a plurality of converging pipes 3132, a plurality of inlets 3132a of the converging pipe 3132 are connected to the second heat exchange pipe 3131. After the liquid refrigerant in the second heat exchange tube 3131 is collected along the multiple inlets 3132a, the collected liquid refrigerant is collected through the convergence pipe 3132, and then concentratedly discharged to the first heat exchanger 100 along the heat pipe 400. Without excessively increasing the number of heat pipes 400, the number of liquid refrigerant collection points in the second heat exchange tube 3131 can be increased, and the distribution of the collection points can be more extensive and uniform. Accordingly, the refrigerant is After condensing to a liquid state in the heat pipe 3131, the residence time and the flow path of the second heat exchange pipe 3131 are effectively shortened, which can ensure sufficient and efficient rehydration of the first heat exchanger 100 and promote the improvement of the first heat exchanger The refrigerant circulation efficiency between 100 and the second heat exchanger 310, especially in the case where the compressor 600 is not driven, can be more conducive to ensuring refrigeration reliability and refrigeration efficiency.

Further, as shown in FIGS. 4a, 4b, and 4c, the second heat exchange tube 3131 includes a plurality of branch pipes 31311, and the plurality of branch pipes 31311 are connected in parallel. Each branch pipe 31311 is connected to the refrigerant inlet of the second heat exchanger 310-B And refrigerant outlet -B 312 communication, and each branch pipe 31311 is connected to one or more inlets. The second heat exchange pipe 3131 includes a plurality of branch pipes 31311, and the plurality of branch pipes 31311 are connected in parallel. This can improve the specific surface area of the second heat exchanger 310 and the condensation efficiency of the refrigerant in the second heat exchanger 310. It is also beneficial for the heat exchange surface of the second heat exchanger 310 to be dispersed in the phase change material, so that the phase change material is evenly heated. In this way, the product evaporation temperature is more uniform, and the cooling efficiency of the phase change material is higher. .

Further, as shown in Figs. 4a, 4b and 4c, the branch pipe 31311 has a serpentine shape, and specifically includes a straight pipe section 31311a, a bottom elbow 31311b at the bottom end of the straight pipe section 31311a, and a top elbow 31311c at the top of the straight pipe section 31311a. 3132a is connected to the bottom elbow 31311b of the branch pipe 31311. Wherein, the branch pipe 31311 has a serpentine shape, more specifically, a long snake shape. Specifically, the branch pipe 31311 is longitudinally arranged or roughly longitudinally arranged, so that the straight pipe section 31311a is generally along the longitudinal direction, and the top elbow 31311c is located in the straight pipe section 31311a. The top and bottom elbows 31111b are located at the bottom end of the straight pipe section 31311a. The top elbows 31111c and the bottom elbows 31111b are used to alternately connect a plurality of horizontally arranged straight pipe sections 31311a in pairs to construct the serpentine branch pipe 31311. Among them, the branch pipe 31311 is arranged longitudinally or substantially in the form of a longitudinal arrangement, which is conducive to the downward convergence of the refrigerant gravity in the branch pipe 31311. In this solution, the inlet 3132a is connected to the bottom elbow 31311b of the branch pipe 31311, and the bottom elbow 31311b can be used. The refrigerant flowing down the straight pipe section 31311a at both ends is merged and then discharged into the inlet 3132a. At the same collection efficiency, the number of the inlet 3132a is simplified, the structure is more simplified, and the structure is also conducive to the liquid in the branch pipe 31311. Refrigerant is discharged as much as possible to avoid liquid refrigerant remaining in the branch pipe 31311.

Of course, this solution is not limited to this, and the second heat exchanger 310 does not have to be the coiled-tube heat exchanger. Those skilled in the art can also design the second heat exchanger 310 as a coiled-tube heat exchanger or a rotary tube according to requirements. Fin heat exchangers, etc.

In any of the above technical solutions, as shown in FIG. 4a, FIG. 4b, and FIG. 4c, the convergence pipeline 3132 includes: a plurality of first-stage tees 3132c and a plurality of second-stage tees 3132d. The pipe 3132c has three interfaces, and two of them are used as the inlet 3132a, and the remaining interfaces are used as the junction; the second-stage tee 3132d has three interfaces, and two of them correspond to two firsts. The junction of the first stage tee 3132c is connected, and the other interface of the second stage tee 3132d is used as the outlet 3132b. Among them, the multi-stage confluence structure composed of the combination of the first stage three-way pipe 3132c and the second stage three-way pipe 3132d is provided. This design can greatly increase the number of heat pipes 400 without increasing the number of heat pipes 400. The number of liquid refrigerant collection points in the second heat exchange tube 3131 further makes the distribution of the collection points more extensive and uniform. In this way, the residence time and flow of the refrigerant after the condensation in the second heat exchanger 310 to the discharge stage The paths are shorter, which is more conducive to ensuring the reliability and efficiency of refrigeration. The two-stage confluence structure combined with the confluence effect of the bottom elbow 31311b of the branch pipe 31311 itself can basically meet the requirements of existing mobile air conditioners. The maximum refrigerant circulation volume and maximum cycle efficiency requirements under refrigeration conditions, and the product structure can be compact.

Preferably, each converging pipe 3132 has one outlet 3132b, four inlets 3132a, and the number of branch pipes 31311 is 4. The four inlets 3132a of the converging pipe 3132 correspond to the four bottom elbows 31311b connected to the four branch pipes 31311. Among them, each branch pipe 31311 has 4 bottom end elbows 31111b, and is provided with 4 converging pipes 3132, with 16 inlets 3132a corresponding to 16 bottom end elbows 31311b, which are connected to the 4 branch pipes 31311, and is provided with 4 A heat pipe is connected to the four outlets 3132b of the four junction pipes 3132 correspondingly.

In any of the above embodiments, as shown in FIG. 5a, FIG. 5b, and FIG. 5c, the refrigerant pipeline A of the first heat exchanger 100 includes: a first heat exchange tube 121 and an outlet interface 122; 121 communicates with the refrigerant inlet-A 111 and the refrigerant outlet-A 112 of the first heat exchanger 100; the outlet interface 122 is located at the top of the first heat exchange tube 121 and communicates with the first heat exchange tube 121, and the outlet interface 122 serves as the first branch pipe Interface 123.

Further, as shown in FIG. 5a, FIG. 5b, and FIG. 5c, the first heat exchange tube 121 includes a plurality of parallel pipes 1211 and a plurality of connecting pipes 1212. The parallel pipe 1211 includes a plurality of branches 1211a and is provided in a plurality of branches. The main pipes at both ends of 1211a; the main pipes of the multiple parallel pipes 1211 are connected through a connecting pipe 1212, so that the multiple parallel pipes 1211 of the first heat exchange pipe 121 are connected in series, and one of the several connecting pipes 1212 An outlet interface 122 is provided on one or more roots. Among them, the connecting pipe 1212 for connecting the parallel pipe 1211 in series is provided with a lead-out interface 122 as the first branch pipe interface 123. At this time, the first branch pipe interface 123 of the connecting pipe 1212 can play a confluent effect, as shown in FIG. After the gaseous refrigerant in the parallel pipe 1211 connected to the two ends of the parallel pipe 1211 converges to the connecting pipe 1212, it is concentrated to be discharged to the second heat exchanger 310 through the heat pipe 400 through the first branch pipe interface 123 of the connecting pipe 1212. On the premise of the number of heat pipes 400, the number of gaseous refrigerant collection points in the first heat exchange tube 121 can be increased, and the distribution of the collection points can be more extensive and uniform. Accordingly, the refrigerant is in the first heat exchange tube 121. After condensing to a liquid state, the residence time and the flow path of the first heat exchange tube 121 are effectively shortened, which can ensure that the second heat exchanger 310 is fully and efficiently replenished, and promote the improvement of the first heat exchanger 100 and the first heat exchanger 100. The efficiency of the refrigerant circulation between the two heat exchangers 310, especially in the case where the compressor 600 is not driven, can be more conducive to ensuring refrigeration reliability and refrigeration efficiency.

More specifically, as shown in FIG. 5a, FIG. 5b, and FIG. 5c, the branches 1211a in the parallel pipeline 1211 are longitudinally arranged or inclined, and the top ends of the plurality of branches 1211a merge to form a first main pipe 1211b, and the plurality of branches 1211a The bottom end of the second main pipe 1211c merges, wherein a connecting pipe 1212 is connected between the first main pipes 1211b of a plurality of parallel pipes 1211, and a connecting port 1212 connected to the first main pipe 1211b is provided with a lead-out interface 122. Wherein, the branches 1211a in the parallel pipeline 1211 are arranged longitudinally or obliquely. In this way, after the refrigerant in the parallel pipeline 1211 evaporates into a gaseous state, the branches 1211a arranged vertically or obliquely can be moved upward and passed through. The first main pipe 1211b at the top of the branch 1211a is discharged into the heat pipe 400 along the lead-out interface 122 of the connecting pipe 1212 connected to the first main pipe 1211b. In this way, the flow trajectory of the refrigerant after vaporization basically faces upward, the flow resistance of the gaseous refrigerant is small, and the kinetic energy is lost. Less, can ensure sufficient and efficient air supply to the second heat exchanger 310, and promote the improvement of the refrigerant circulation efficiency between the first heat exchanger 100 and the second heat exchanger 310, especially in the case of no compressor 600 driving, Can be more conducive to ensuring refrigeration reliability and cooling efficiency.

Preferably, the first heat exchange pipe 121 includes eight parallel pipes 1211, and at the top of the branch 1211a, the eight first main pipes 1211b are connected in pairs by four connection pipes 1212, and the four connection pipes 1212 are respectively connected to each other. A lead-out interface 122 is provided. At the bottom end of the branch 1211a, the eight second main pipes 1211c are connected in pairs by the other four connecting pipes 1212.

In any of the above embodiments, as shown in FIG. 2, the first heat exchanger 100 is inclined relative to the longitudinal plane as a whole, and a predetermined angle α is formed between the first heat exchanger 100 and the longitudinal plane, such as α> 0 °. . Wherein, the first heat exchanger 100 is arranged to be inclined with respect to the longitudinal plane as a whole. More specifically, for example, the first heat exchanger 100 is a fin heat exchanger, and the airflow penetrates the fin heat exchanger from the inner surface of the fin heat exchanger. The rear surface is discharged along the outer surface of the fin heat exchanger, and the airflow achieves heat exchange with the airflow during the process of penetrating the fin heat exchanger. The first heat exchanger 100 as a whole is inclined relative to the longitudinal plane, which can be specifically understood as The inner or outer surface of the fin heat exchanger is inclined with respect to the longitudinal plane and has a predetermined included angle, so that the cold wind can be blown out at a certain angle, avoiding direct horizontal blow, and preferably blown out toward the inclined, wherein the more preferably the preset included angle is based on the first The position of a heat exchanger 100 is highly designed, so that the cold air blown can point to the user's torso, and the user experience is better.

In any of the above embodiments, as shown in FIG. 2, the heat exchanger system of the mobile air conditioner further includes a valve 500, and the heat pipe 400 is connected with a valve 500 for controlling the on or off of the heat pipe 400. Among them, a valve 500 is provided to control the heat pipe 400 to be turned on or off. In this way, there is no need to use the heat pipe 400 to transport the refrigerant between the first heat exchanger 100 and the second heat exchanger 310 to realize the first heat exchanger 100 and the first heat exchanger 100. When the refrigerant is circulated between the two heat exchangers 310, the valve 500 can be controlled to stop the heat pipe 400 from conducting. At this time, the first heat exchanger 100 and the second heat exchanger 310 can be based on the refrigerant circulation in the conventional air conditioner. The mode performs refrigerant circulation, and the product working mode can be more diversified.

Further, the heat exchanger system of the mobile air conditioner further includes an opening degree adjustment mechanism. The opening degree adjustment mechanism is connected to the valve 500 for adjusting the opening degree of the valve 500. In this way, the opening degree of the valve 500 can be adjusted by the opening degree adjusting mechanism. In order to control the refrigerant circulation efficiency between the first heat exchanger 100 and the second heat exchanger 310 accordingly, and thus achieve the purpose of controlling the refrigeration efficiency, for example, when the demand for refrigeration efficiency is high, the valve 500 can be increased. The opening degree is adjusted to increase the evaporation efficiency in the first heat exchanger 100 accordingly, thereby increasing the cooling efficiency. Conversely, when the demand for cooling efficiency is low, the opening degree of the valve 500 may be reduced to correspondingly reduce the evaporation in the first heat exchanger 100. Efficiency, thereby reducing the cooling efficiency, or, in the early phase of the cooling operation with a large amount of cold storage in the phase change material, since the phase change material has a higher heat absorption efficiency for the second heat exchanger 310, the valve 500 can be reduced Opening degree. With the accumulation of the operating time of the refrigeration mode, the total amount of cold storage in the phase change material is reduced, and the heat absorption efficiency of the phase change material to the second heat exchanger 310 is correspondingly reduced. At this time, the opening degree of the valve 500 can be increased. So that the cold output of the early and late substantially uniform cooling conditions.

It can be understood that the opening adjustment mechanism may be a structure for electronically adjusting the opening degree of the valve 500, such as a mobile terminal, a control panel, an electric control knob, etc., and control the valve 500 such as a solenoid valve through the output signal of the mobile terminal, the control panel, etc. To change the opening degree, the opening degree adjusting mechanism may be a structure for mechanically adjusting the opening degree of the valve 500, for example, an operating handle, an operating handle connection or a transmission mechanism connected to a mechanical valve such as a flap valve such as the valve 500, so as to adjust the mechanical valve accordingly. Opening degree. As for the specific type of valve, those skilled in the art can choose based on the requirements of cut-off conduction function and opening degree adjustment, such as cut-off valve, automatic control on-off valve, etc., to ensure the internal nominal diameter of the valve and the heat pipe 400 pipeline. It is basically the same to ensure that the heat pipe 400 can flow normally.

Further, as shown in FIG. 2, the valve 500 has a valve body 510, the valve body 510 has a first interface 520 and a second interface 530, the valve body 510 is arranged obliquely and the position of the first interface 520 is higher than the second interface 530, The first interface 520 is connected to the second heat exchanger 310, and the second interface 530 is connected to the first heat exchanger 100. The valve body 510 provided with the valve 500 is arranged obliquely and positions the first interface 520. Higher than the second interface 530, this facilitates the liquid refrigerant inside the valve 500 to flow to the first heat exchanger 100 spontaneously, and helps the heat pipe 400 such as a gravity heat pipe to better function and conduct conduction, and improves the first heat exchanger 100 and the The efficiency of the refrigerant circulation between the second heat exchangers 310 is avoided, and at the same time, the refrigerant is prevented from remaining in the valve body 510 and the energy efficiency of the product is improved.

In any of the above embodiments, preferably, the heat exchanger system of the mobile air conditioner further includes a first heat insulation member, wherein the phase change energy storage heat exchange device 300 further includes a container, and the first heat insulation member heats the container, and the inside of the container is formed with A receiving space, and the phase change material is located in the receiving space. For example, designing the first insulation part as a thermal insulation sleeve made of insulation cotton, sponge, etc., and putting it on the outside of the container to insulate the container, can reduce the loss of phase change material cooling and improve the energy efficiency of the product.

In any of the above embodiments, preferably, the heat exchanger system of the mobile air conditioner further includes a second heat insulation member, and the second heat insulation member is disposed on the heat pipe 400 and heat-insulates the heat pipe 400. For example, the second heat insulation member is designed as heat insulation cotton, A thermal insulation sleeve made of sponge and other materials is used to heat the heat pipe 400 outside the heat pipe 400, which can reduce the self-vaporization and heating of the refrigerant inside the heat pipe 400 during transmission, and improve the energy efficiency of the product.

The mobile air conditioner provided by the embodiment of the second aspect of the present application includes the heat exchanger system of the mobile air conditioner described in any of the above embodiments.

In an embodiment of the present application, as shown in FIGS. 6 and 7, the mobile air conditioner further includes: a compressor 600 and a throttle element 700. The compressor 600 has a return air port 610 and an exhaust port 620, and the exhaust port 620 communicates with the refrigerant inlet-A of the first heat exchanger 100, and the return air port 610 communicates with the refrigerant outlet-B of the second heat exchanger 310; The throttle element 700 is connected to the refrigerant outlet-A of the first heat exchanger 100 The refrigerant inlet-B of 112 and the second heat exchanger 310 are connected to 311.

In this solution, a compressor 600 and a throttling element 700 are connected to the first heat exchanger 100 and the second heat exchanger 310 to form a loop. When the phase change material absorbs heat and saturates and needs to be regenerated and stored, the mobile air conditioner can be used. Move to the outdoor or other places where there is no need for refrigeration. At this time, the control heat pipe 400 is turned off and the compressor 600 is controlled to run. At this time, the refrigerant discharged from the compressor 600 flows through the first heat exchanger 100, the throttling element 700, The second heat exchanger 310 finally returns to the compressor 600 to complete the refrigerant cycle. In this process, the first heat exchanger 100 serves as a condenser, the second heat exchanger 310 serves as an evaporator, and the refrigerant at the second heat exchanger 310 is used. Evaporation absorbs heat from phase change materials and makes phase change materials store energy for regeneration. Compared with natural regeneration, it takes less time, and compared with regeneration through refrigeration equipment such as refrigerators, the user's workload is reduced and the use is more convenient.

Optionally, the compressor 600 may be a fixed-frequency compressor or a variable-frequency compressor. A suitable variable-frequency compressor can further reduce ice storage time to a certain extent.

Optionally, the throttle element 700 is a capillary tube, an electronic expansion valve, or a thermal expansion valve.

In an embodiment of the present application, preferably, the compressor 600 is arranged below the heat exchanger system of the mobile air conditioner. In this way, the horizontal dimension of the product is small, the structure is more compact, and the center of gravity of the product is moved downward. For stability, it is also beneficial to reduce the amplitude of the whole machine when the compressor 600 is running, and improve product quality.

In an embodiment of the present application, preferably, the throttling element 700 is connected to the refrigerant inlet-B of the second heat exchanger 310 through a pipe, and the connection between the throttling element 700 and the pipe and the first Three thermal insulation parts, and heat insulation by the third thermal insulation part. For example, designing the third insulation piece as a thermal insulation sleeve made of insulation cotton, sponge, etc., to put it on the outside of the pipe and the outside of the joint between the pipe and the throttling element 700 to heat it, can improve the evaporation efficiency of the refrigerant, thereby improving The regeneration efficiency of phase change materials can shorten the regeneration time and reduce energy consumption.

In an embodiment of the present application, preferably, an air suction pipe 800 is connected to the air return port 610 of the compressor 600, and the air suction pipe 800 is in communication with the refrigerant outlet-B312 of the second heat exchanger 310. The trachea 800 is wound around the throttle element 700. In this way, the suction pipe 800 is reheated from the throttle element 700 to fully vaporize the internal refrigerant, to prevent the compressor 600 from entering the liquid, and to prevent the occurrence of liquid strikes.

In an embodiment of the present application, preferably, an air intake pipe 800 is connected to the return port 610 of the compressor 600, and the air intake pipe 800 is in communication with the refrigerant outlet-B312 of the second heat exchanger 310, where The air conditioner further includes a regenerator, which is connected to the suction pipe 800 and the refrigerant outlet-312 of the second heat exchanger 310. In this way, by using the regenerator for reheating, the compressor 600 can be prevented from entering the liquid, and the liquid hammering phenomenon can be prevented.

In an embodiment of the present application, preferably, as shown in FIG. 6 and FIG. 7, an air suction pipe 800 is connected to the return port 610 of the compressor 600, and the air suction pipe 800 and the refrigerant of the second heat exchanger 310 The outlet-B communicates with 312, in which a fourth heat insulation member is provided at the suction pipe 800 and the suction pipe 800 is insulated by the fourth heat insulation member. For example, the fourth insulation piece is designed as a thermal insulation sleeve made of insulation cotton, sponge, etc., and it is put on the outside of the suction pipe 800 to heat it, so that the heat absorption from the environment of the suction pipe 800 can be suppressed, and the return of heat can be avoided. The air temperature is too high, which improves the working efficiency of the compressor 600.

For the existing mobile air conditioners, the problem of the limited mobility caused by the need for 400 external heat pipes, coupled with the existing conventional thermal storage phase change materials have low energy storage density, and the refrigeration process needs to start the compressor 600 and other disadvantages. , And the use of cold air fans to replace mobile air conditioners and the existing cold air blowing usually contains high humidity, users are uncomfortable to use and easily cause pain points such as rheumatism.

In a specific embodiment of the present application, a mobile air conditioner is provided. As shown in FIG. 6, it specifically includes a compressor 600 (for a fixed frequency or variable frequency compressor), a throttle element 700 (preferably a capillary tube), and a mobile Air conditioner heat exchanger system, wherein the mobile air conditioner heat exchanger system includes a first heat exchanger 100 (is an air-cooled heat exchanger, preferably such as a finned tube heat exchanger), a fan 200, and a phase change energy storage A heat device 300, a heat pipe 400 (preferably a gravity heat pipe), and a valve 500. The phase change energy storage heat exchange device 300 includes a container, a second heat exchanger 310 in the container, and a phase distributed around the second heat exchanger 310 in the container. Variable material (preferably ice), where the compressor 600, the first heat exchanger 100, the throttling element 700, and the second heat exchanger 310 are connected to form a refrigerant circuit, and the first heat exchanger 100 and the second heat exchanger The radiators 310 are connected through the heat pipe 400 to form another refrigerant circuit.

This mobile air-conditioning product has two operating modes to switch between outdoor ice storage mode and indoor cooling mode:

Outdoor ice storage mode: In this mode, the valve 500 is in the off state, and the heat pipe 400 is not conducting. At this time, the refrigerant circuit of the mobile air conditioner can be seen in FIG. 7, where the compressor 600 is running and the second heat exchanger 310 is used as Evaporator, the first heat exchanger 100 serves as the condenser, and the second heat exchanger 310 provides cold ice for the water in the container. When all the water in the container solidifies into ice, the ice storage is completed, and the outdoor ice storage can be stopped. Mode to move the mobile air conditioner into the room for the indoor cooling mode.

More specifically, in the outdoor ice storage mode, the refrigerant circulation circuit is a normal vapor compression refrigeration cycle, in which the refrigerant is compressed by the compressor 600 and enters the first heat exchanger 100 to release heat to the external environment, and then passes through the heat exchanger. The flow element 700 is throttled, and the throttled refrigerant enters the second heat exchanger 310 to evaporate to achieve a temperature lower than 0 ° C. In this way, the refrigerant in the second heat exchanger 310 absorbs the container through the second heat exchanger 310 The heat of the internal water causes the water to solidify into ice to realize the ice storage process, and the refrigerant in the second heat exchanger 310 completes the evaporation and then flows back to the compressor 600 to complete the refrigerant cycle. When the water in the container gradually cools down to completely freeze to ice, the system can prepare to switch to indoor cooling mode. Among them, since the temperature of the refrigerant in the refrigerant path from the throttle element outlet to the second heat exchanger and the compressor's return air port can be as low as 0 ° C or lower, it is preferable to adjust the second half of the throttle element and its The pipes of the second heat exchanger, the pipes of the second heat exchanger to the compressor, and the entire container are tightly insulated.

Indoor cooling mode: In this mode, the compressor 600 stops running, while the valve 500 is in the conducting state, and the heat pipe 400 is correspondingly conducting. At this time, the refrigerant circuit of the mobile air conditioner can be seen in Figure 3, and the refrigerant is in the first heat exchanger. Heat is transferred between 100 and the second heat exchanger 310 through the heat pipe 400 to achieve the purpose of cooling.

More specifically, in the indoor cooling mode, the compressor 600 is stopped, and the valve 500 on the heat pipe 400 between the first heat exchanger 100 and the second heat exchanger 310 is in a conducting state. The refrigerant circuit in the system is shown in the figure. The operation shown in FIG. 3 is performed, in which the refrigerant releases heat to the ice in the upper second heat exchanger 310 to condense into a liquid, and the liquid refrigerant formed by condensation can spontaneously sink to the first below the heat pipe 400 by its own gravity. In the heat exchanger 100, the refrigerant absorbs the heat of the indoor air in the first heat exchanger 100 and evaporates into a gas. Due to the low density, the gas will rise in the heat pipe 400 and enter the second heat exchanger 310 above to condense again. Repeatedly completed the refrigerant to transfer the heat absorbed by the first heat exchanger 100 to the ice in the container through the gravity heat pipe, thereby achieving the purpose of cooling the room air.

Among them, in order to stabilize the cooling capacity output, a corresponding opening degree adjustment mechanism can be added to the valve 500 of the heat pipe 400 to adjust the opening degree of the valve 500. The opening degree of the valve 500 can be adjusted to reduce the excessive cooling in the early stage of the indoor cooling mode operation. The volume output is controlled to be smaller, and by increasing the opening of the valve 500 to control the smaller cooling output in the later period of the indoor cooling mode operation, it can also be understood that for the early and late periods of the indoor cooling mode operation, the early valve The opening degree of 500 is smaller than the opening degree of the later-stage valve 500.

Among them, in order to ensure the efficient operation of the ice storage / refrigeration mode, the structure of the first heat exchanger 100 and the second heat exchanger 310 is more optimized in this solution. The first heat exchanger 100 and the second heat exchanger 100 are preferably replaced. The heat exchangers 310 all take the form of finned tubes. Among them, as shown in FIG. 4a, FIG. 4b, and FIG. 4c are schematic diagrams of a part of the structure of the second heat exchanger 310. Therefore, the number of pipelines is large, and the heat exchanger has a large volume. The difference between the second heat exchanger 310 and the conventional finned tube heat exchanger is mainly that the second heat exchanger 310 is placed in the vertical direction of the tube. The bottom elbow 31311b of the second heat exchanger 310 is replaced by a series of Y-shaped tees. The Y-shaped tees are summarized by three stages (such as: bottom elbow + first stage tee + second stage tee), and finally There are 4 flow paths output downward, and these 4 flow paths are the circulation channels of the gravity heat pipe. There are 4 flow path outputs on the top and left of the second heat exchanger 310, and the 4 flow path outputs on each side are in parallel, and are used as the refrigerant inlet-B and the refrigerant outlet-B of the second heat exchanger 310, respectively. .

Figures 5a, 5b, and 5c are schematic diagrams of some structures of the first heat exchanger 100. The situation of the first heat exchanger 100 is similar to that of the second heat exchanger 310, except that the Y-type tee replaces the first The top connecting pipe 1212 of a heat exchanger 100, that is, a Y-shaped tee replaces the half-moon tube on the top of the first heat exchanger 100 in the illustration, and the Y-shaped tee passes through two stages (such as: the first main pipe + the connecting pipe and Drainage interface) summary, and finally output 4 flow paths, which are also the flow channels of gravity heat pipes. The left and right sides of the first heat exchanger 100 each have a flow path converging, which respectively serves as a refrigerant inlet-A111 and a refrigerant outlet-A112 of the first heat exchanger 100.

In terms of product layout, the compressor 600 is located below the heat exchanger system of the mobile air conditioner. In the heat exchanger system of the mobile air conditioner, the second heat exchanger 310 is located above the first heat exchanger 100. The height of a heat exchanger 100, the first heat exchanger 100 may be arranged at a certain angle α with the vertical direction, so as to ensure that the cold air blown out can point to the user's torso. At the same time, the valve 500 used in this solution includes a valve body 510 substantially along the horizontal direction, and the valve body 510 maintains a certain inclination angle to help the gravity heat pipe to better function.

After preliminary design and testing, the current preliminary test results are shown in Table 1.

蓄冰运行时长Ice storage running time	制冷运行时长Cooling operation time	平均制冷量Average cooling capacity
2小时20分钟2 hours and 20 minutes	1小时50分钟1 hour and 50 minutes	>350W> 350W

It can be seen that through one-time ice storage, long-term continuous cooling can be achieved, and there is no compressor noise effect during the cooling process, and the use experience is good. At the same time, the cooling capacity is more than 350W, which can fully meet the room cooling demand, and through phase change The way in which the material provides heat absorption can make the condensation and evaporation temperatures basically stable throughout the refrigeration process, and the comfort is better.

In this application, the terms "first" and "second" are used for descriptive purposes only and should not be interpreted as indicating or implying relative importance; the term "plurality" means two or more unless otherwise stated Clearly defined. The terms "installation", "connected", "connected", "fixed" and the like should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral connection; "connected" can It is directly connected or indirectly connected through an intermediate medium. For those of ordinary skill in the art, the specific meanings of the above terms in this application can be understood according to specific situations.

In the description of the present application, it should be understood that the orientation or position relationship indicated by the terms “up” and “down” is based on the orientation or position relationship shown in the drawings, and is only for the convenience of describing the application and simplifying the description. It is not an indication or implied that the device or unit referred to must have a specific orientation, construction and operation in a specific orientation, and therefore cannot be understood as a limitation on this application.

In the description of this specification, the descriptions of the terms “one embodiment”, “some embodiments”, “specific embodiments” and the like mean that specific features, structures, materials, or characteristics described in conjunction with the embodiment or example are included in this application In at least one embodiment or example. In this specification, the schematic expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

The above description is only a preferred embodiment of the present application, and is not intended to limit the present application. For those skilled in the art, this application may have various modifications and changes. Any modification, equivalent replacement, or improvement made within the spirit and principle of this application shall be included in the protection scope of this application.

Claims

A heat exchanger system for a mobile air conditioner, comprising:

First heat exchanger

A fan for driving airflow to exchange heat with the first heat exchanger;

A phase change energy storage heat exchange device includes a second heat exchanger and a phase change material capable of exchanging heat with the second heat exchanger;

A heat pipe is in communication with the first heat exchanger and the second heat exchanger, and when the heat pipe is turned on, a refrigerant can pass along the heat pipe between the first heat exchanger and the second heat exchanger. Between circulation.
The heat exchanger system for a mobile air conditioner according to claim 1, wherein:

The heat pipe is arranged longitudinally or obliquely, and a part of the heat pipe for connecting with the first heat exchanger is lower than a part of the heat pipe for connecting with the second heat exchanger.
The heat exchanger system for a mobile air conditioner according to claim 2, wherein:

The heat pipe is a coreless gravity heat pipe.
The heat exchanger system for a mobile air conditioner according to claim 1, wherein:

The heat pipe is a cored heat pipe.
The heat exchanger system for a mobile air conditioner according to any one of claims 1 to 4, wherein:

The portion of the first heat exchanger for connecting with the heat pipe is at the top of the first heat exchanger or at a position adjacent to the top of the first heat exchanger.
The heat exchanger system for a mobile air conditioner according to any one of claims 1 to 5, wherein:

The portion of the second heat exchanger for connecting with the heat pipe is located at the bottom end of the second heat exchanger or at a position adjacent to the bottom end of the second heat exchanger.
The heat exchanger system for a mobile air conditioner according to any one of claims 1 to 6, wherein:

The second heat exchanger is located above the first heat exchanger.
The heat exchanger system for a mobile air conditioner according to any one of claims 1 to 4, wherein:

The first heat exchanger has a refrigerant inlet, a refrigerant outlet, and a refrigerant pipeline provided between the refrigerant inlet and the refrigerant outlet of the first heat exchanger, and the refrigerant pipeline of the first heat exchanger is provided with There are several first branch pipe interfaces, and each of the first branch pipe interfaces is connected to the second heat exchanger through one of the heat pipes.
The heat exchanger system for a mobile air conditioner according to any one of claims 1 to 4 or 8, wherein:

The second heat exchanger has a refrigerant inlet, a refrigerant outlet, and a refrigerant pipeline provided between the refrigerant inlet and the refrigerant outlet of the second heat exchanger, and the refrigerant pipeline of the second heat exchanger is provided with There are several second branch pipe interfaces, and each of the second branch pipe interfaces is connected to the first heat exchanger through one of the heat pipes.
The heat exchanger system for a mobile air conditioner according to claim 9, wherein the refrigerant pipe of the second heat exchanger comprises:

A second heat exchange tube, which is in communication with the refrigerant inlet and the refrigerant outlet of the second heat exchanger;

A plurality of merged pipelines are located below the second heat exchange tube, the merged pipelines have inlets and outlets, the number of the inlets is more than the outlets, and a slave unit is formed inside the merged pipelines. The inlet extends to the outlet and converges in a channel of the outlet, wherein each of the inlets is connected to the second heat exchange tube, and the outlet serves as the second branch pipe interface.
The heat exchanger system for a mobile air conditioner according to claim 10, wherein:

The second heat exchange pipe includes a plurality of branch pipes, and the plurality of branch pipes are connected in parallel. Each of the branch pipes is in communication with a refrigerant inlet and a refrigerant outlet of the second heat exchanger, and each of the branch pipes is connected to one or more of the branch pipes. The inlets are switched on.
The heat exchanger system for a mobile air conditioner according to claim 11, wherein:

The branch pipe is in the shape of a snake, and includes a straight pipe section, a bottom elbow at the bottom end of the straight pipe section, and a top elbow at the top end of the straight pipe section. The inlet is connected to the bottom elbow of the branch pipe.
The heat exchanger system for a mobile air conditioner according to claim 10, wherein the converging pipeline comprises:

A plurality of first-stage tees, the first-stage tee has three interfaces, and two of the interfaces are used as the inlets, and the remaining interfaces are used as the junctions;

A plurality of second-stage tees, the second-stage tee has three interfaces, and two of the interfaces are correspondingly connected to the junctions of the two first-stage tees, and the second The other interface of the stage tee serves as the outlet.
The heat exchanger system for a mobile air conditioner according to claim 8, wherein the refrigerant pipeline of the first heat exchanger comprises:

A first heat exchange tube in communication with a refrigerant inlet and a refrigerant outlet of the first heat exchanger;

An outlet interface is located at the top of the first heat exchange tube and communicates with the first heat exchange tube, and the outlet interface is used as the first branch pipe interface.
The heat exchanger system for a mobile air conditioner according to claim 14, wherein the first heat exchange tube comprises:

A plurality of parallel pipelines including a plurality of branches and a main pipe provided at both ends of the plurality of branches;

A plurality of connecting pipes, and the main pipes of a plurality of the parallel pipes are connected through the connecting pipe, so that a plurality of the parallel pipes of the first heat exchange pipe are connected in series, wherein a plurality of the The lead-out interface is provided on one or more of the connecting pipes.
The heat exchanger system for a mobile air conditioner according to claim 15, wherein:

The branches in the parallel pipeline are arranged longitudinally or inclinedly, and the top ends of a plurality of the branches meet to form a first main pipe, and the bottom ends of a plurality of the branches meet to form a second main pipe. The connection pipe is connected between the first main pipes of the parallel pipeline, and the connection pipe connected to the first main pipe is provided with the lead-out interface.
The heat exchanger system for a mobile air conditioner according to any one of claims 1 to 4, wherein:

The first heat exchanger as a whole is inclined with respect to a longitudinal plane, and a predetermined included angle is formed between the first heat exchanger and the longitudinal plane.
The heat exchanger system for a mobile air conditioner according to any one of claims 1 to 4, further comprising:

A valve, the heat pipe is connected with the valve for controlling the heat pipe to be turned on or off.
The heat exchanger system for a mobile air conditioner according to claim 18, further comprising:

The opening degree adjusting mechanism is connected to the valve and is used to adjust the opening degree of the valve.
The heat exchanger system for a mobile air conditioner according to claim 18, wherein:

The valve has a valve body, the valve body has a first interface and a second interface, the valve body is arranged obliquely and makes the position of the first interface higher than the second interface, wherein the first interface It is connected to the second heat exchanger, and the second interface is connected to the first heat exchanger.
The heat exchanger system for a mobile air conditioner according to any one of claims 1 to 4, further comprising:

The first heat-preserving member, wherein the phase-change energy storage heat-exchange device further includes a container, and the first heat-preserving member heats the container, and an accommodation space is formed inside the container, and the phase-change material is located in the container. In space.
The heat exchanger system for a mobile air conditioner according to any one of claims 1 to 4 or 21, further comprising:

A second heat-preserving member is provided on the heat pipe and heat-insulates the heat pipe.
A mobile air conditioner comprising the heat exchanger system of the mobile air conditioner according to any one of claims 1 to 22.
The mobile air conditioner according to claim 23, further comprising:

The compressor has a return air port and an exhaust port, the exhaust port is in communication with the refrigerant inlet of the first heat exchanger, and the return port is in communication with the refrigerant outlet of the second heat exchanger;

The throttle element is in communication with the refrigerant outlet of the first heat exchanger and the refrigerant inlet of the second heat exchanger.
The mobile air conditioner according to claim 24, wherein

The compressor is disposed below a heat exchanger system of the mobile air conditioner.
The mobile air conditioner according to claim 24 or 25, wherein:

The throttling element is connected to the refrigerant inlet of the second heat exchanger through a pipe, and a third heat insulation member is provided at the connection between the throttling element and the pipe and through the pipe, and passes through the pipe. The third heat-preserving member keeps heat.
The mobile air conditioner according to any one of claims 24 to 26, wherein

An air suction pipe is connected to the air return port of the compressor, and the air suction pipe is in communication with the refrigerant outlet of the second heat exchanger.
The mobile air conditioner according to claim 27, wherein

The suction pipe is wound around the throttle element.
The mobile air conditioner according to claim 27 or 28, wherein

A fourth heat insulation member is provided at the suction pipe, and the suction pipe is insulated by the fourth heat insulation member.
The mobile air conditioner according to any one of claims 27 to 29, wherein

The mobile air conditioner further includes a regenerator connected to the suction pipe and a refrigerant outlet of the second heat exchanger.