WO2023040281A1

WO2023040281A1 - Liquid distributor, heat exchanger, refrigeration cycle system, and air conditioner

Info

Publication number: WO2023040281A1
Application number: PCT/CN2022/089796
Authority: WO
Inventors: 国德防; 王飞; 吴洪金; 李阳; 张心怡; 丁爽; 袁俊军; 蒋骏; 许文明
Original assignee: 青岛海尔空调器有限总公司; 青岛海尔空调电子有限公司; 海尔智家股份有限公司
Priority date: 2021-09-19
Filing date: 2022-04-28
Publication date: 2023-03-23
Also published as: WO2023040315A1; CN113932487A; CN113932488A; WO2023040295A1; CN113899116A; CN114838531B; CN113899121A; CN113932484A; CN113899122A; CN113899120A; WO2023040282A1; CN113932497A; WO2023040347A1; CN114838532B; WO2023040280A1; CN113932498A; CN113932491A; CN114838532A; WO2023040317A1; WO2023040681A1

Abstract

Provided is a liquid distributor, comprising a housing, a first liquid distribution branch pipe (251), and a second liquid distribution branch pipe (252). A liquid distribution cavity is formed inside the housing, and a first liquid distribution port and a second liquid distribution port are formed on the housing; the first liquid distribution branch pipe (251) is communicated with the liquid distribution cavity by means of the first liquid distribution port; the second liquid distribution branch pipe (252) is communicated with the liquid distribution cavity by means of the second liquid distribution port; and the inner diameter of the first liquid distribution branch pipe (251) is greater than the inner diameter of the second liquid distribution branch pipe (252). According to the provided liquid distributor, the amounts of refrigerants flowing into the two liquid distribution branch pipes are different. Further provided are a heat exchanger, a refrigeration cycle system, and an air conditioner.

Description

Liquid separator, heat exchanger, refrigeration cycle system, air conditioner

This application is based on a Chinese patent application with application number 202111102392.9 and a filing date of September 19, 2021, and claims the priority of this Chinese patent application. The entire content of this Chinese patent application is hereby incorporated by reference into this application.

This application is based on a Chinese patent application with application number 202111102583.5 and a filing date of September 20, 2021, and claims the priority of this Chinese patent application. The entire content of this Chinese patent application is hereby incorporated by reference into this application.

This application is based on a Chinese patent application with application number 202111310195.6 and a filing date of November 3, 2021, and claims the priority of this Chinese patent application. The entire content of this Chinese patent application is hereby incorporated by reference into this application.

technical field

The present application relates to the technical field of air conditioning, for example, to a liquid separator, a heat exchanger, a refrigeration cycle system, and an air conditioner.

Background technique

The liquid separator used on the existing heat exchanger, such as a flattened three-way liquid separator, is connected with a liquid branch pipe on the two liquid distribution ports of the liquid separator, and a confluence pipe is connected to the confluence nozzle of the liquid separator. Tube. The other end of each liquid branch pipe is respectively connected with a refrigerant outlet of the heat exchanger, so that the refrigerant flows out through the two liquid branch pipes after passing through the confluence pipe.

In the existing liquid distributor, the liquid distributor includes a first liquid distribution port, a second liquid distribution port and a confluence nozzle, and the first liquid distribution port and the second liquid distribution port are respectively connected with a first liquid distribution branch pipe and a second liquid distribution port. The liquid branch pipe is provided with a first liquid branch pipe bending part on the first liquid branch pipe, and a second liquid branch pipe bending part is arranged on the second liquid branch pipe. By setting bending parts on the two liquid branch pipes respectively, the resistance formed by the bending parts can be used to provide the pressure loss when the refrigerant flows, so as to adjust the flow rate and flow rate of the refrigerant in the liquid branch pipes, thereby eliminating the problems caused by the connection of the liquid branch pipes. The upper and lower settings of the refrigerant outlet of the heat exchanger lead to the problem of uneven refrigerant flow and flow velocity caused by different lengths of straight pipe sections.

In the process of implementing the embodiments of the present disclosure, it is found that at least the following problems exist in related technologies:

The existing liquid separator is improved to improve the uniformity of the refrigerant flowing out of each liquid branch pipe, and no solution is given on how to make the refrigerant flow out of each liquid branch pipe different.

Contents of the invention

In order to provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is presented below. The summary is not intended to be an extensive overview nor to identify key/important elements or to delineate the scope of these embodiments, but rather serves as a prelude to the detailed description that follows.

Embodiments of the present disclosure provide a liquid separator, a heat exchanger, a refrigeration cycle system, and an air conditioner, so as to solve the problem of how to make the flow rate of refrigerant flowing out of each liquid branch pipe of the liquid separator different.

An embodiment of the present disclosure provides a liquid dispenser, including: a housing with a liquid dispensing cavity inside, the housing is provided with a first liquid dispensing port and a second dispensing port; a first liquid distributing branch pipe passes through the first A liquid distribution port communicates with the liquid separation chamber; and, a second liquid distribution branch pipe communicates with the liquid distribution chamber through the second liquid distribution port; wherein, the inner diameter of the first liquid distribution branch pipe is larger than the The inside diameter of the second branch.

An embodiment of the present disclosure provides a heat exchanger, including the aforementioned liquid separator.

An embodiment of the present disclosure provides a refrigeration cycle system, including the foregoing heat exchanger.

An embodiment of the present disclosure provides an air conditioner, including the aforementioned refrigeration cycle system.

Embodiments of the present disclosure provide a liquid separator, a heat exchanger, a refrigeration cycle system, and an air conditioner, which can achieve the following technical effects:

An embodiment of the present disclosure provides a liquid distributor, including a housing, a first liquid branch pipe and a second liquid branch pipe. The first liquid branch pipe communicates with the liquid distribution chamber inside the housing through the first liquid distribution port, and the second liquid distribution branch pipe communicates with the liquid distribution chamber inside the housing through the second liquid distribution port. Wherein, the inner diameter of the first liquid branch pipe is larger than the inner diameter of the second liquid branch pipe. In this way, the amount of refrigerant flowing into the first liquid branch pipe in the liquid distribution chamber is greater than the amount of refrigerant flowing into the second liquid branch pipe, which meets the requirement that the refrigerant flows into the first liquid branch pipe and the second liquid branch pipe are different.

The foregoing general description and the following description are exemplary and explanatory only and are not intended to limit the application.

Description of drawings

One or more embodiments are exemplified by the corresponding drawings, and these exemplifications and drawings do not constitute a limitation to the embodiments, and elements with the same reference numerals in the drawings are shown as similar elements, The drawings are not limited to scale and in which:

Fig. 1 is a schematic structural diagram of a heat exchanger provided by an embodiment of the present disclosure;

Fig. 2 is a partial schematic diagram of a one-way valve provided by an embodiment of the present disclosure;

Fig. 3 is a schematic structural diagram of another heat exchanger provided by an embodiment of the present disclosure;

Fig. 4 is a schematic structural diagram of another heat exchanger provided by an embodiment of the present disclosure;

Fig. 5 is a schematic structural diagram of another heat exchanger provided by an embodiment of the present disclosure;

Fig. 6 is a schematic diagram of a heat exchange flow path when a heat exchanger is used as an evaporator according to an embodiment of the present disclosure;

Fig. 7 is a schematic diagram of a heat exchange flow path in the case where a heat exchanger is used as a condenser according to an embodiment of the present disclosure;

Fig. 8 is a schematic diagram of the distribution of heat exchange tubes of a heat exchanger provided by an embodiment of the present disclosure;

Fig. 9 is a schematic diagram of the distribution of heat exchange tubes of another heat exchanger provided by an embodiment of the present disclosure;

Fig. 10 is a schematic structural view of other parts of the heat exchanger provided by the embodiment of the present disclosure except the heat exchange tube;

Fig. 11 is a schematic structural diagram of a liquid dispenser provided by an embodiment of the present disclosure with an inclined arrangement;

Fig. 12 is a schematic structural diagram of a heat exchanger in the form of a three-branch variable split flow provided by an embodiment of the present disclosure;

Fig. 13 is a schematic diagram of the end face of the liquid dispenser provided by the embodiment of the present disclosure;

Fig. 14 is a schematic structural diagram of another liquid dispenser provided by an embodiment of the present disclosure;

Fig. 15 is a schematic structural view of another liquid dispenser provided by an embodiment of the present disclosure;

Fig. 16 is a schematic structural diagram of another liquid dispenser provided by an embodiment of the present disclosure;

Fig. 17 is a schematic structural view of another liquid dispenser provided by an embodiment of the present disclosure;

Fig. 18 is a schematic structural view of another liquid dispenser provided by an embodiment of the present disclosure;

Fig. 19 is a schematic structural view of another liquid dispenser provided by an embodiment of the present disclosure;

Fig. 20 is a schematic structural diagram of another liquid dispenser provided by an embodiment of the present disclosure;

Fig. 21 is a schematic structural diagram of another liquid dispenser provided by an embodiment of the present disclosure;

Fig. 22 is a simulation diagram of refrigerant flow distribution in a liquid separator provided by an embodiment of the present disclosure;

Fig. 23 is a simulation diagram of refrigerant flow distribution in another liquid separator provided by an embodiment of the present disclosure;

Fig. 24 is a schematic diagram of refrigerant flow distribution in a liquid separator provided by an embodiment of the present disclosure;

Fig. 25 is a perspective view of a dispenser provided by an embodiment of the present disclosure;

Fig. 26 is a perspective view of another liquid dispenser provided by an embodiment of the present disclosure;

Fig. 27 is a schematic front view of the dispenser provided in the embodiment of Fig. 26;

Fig. 28 is a sectional view along A-A of Fig. 27;

Fig. 29 is a cross-sectional view of another liquid dispenser provided by an embodiment of the present disclosure;

Fig. 30 is a simulation effect diagram of a splitter effect provided by an embodiment of the present disclosure;

Fig. 31 is a comparison chart of non-uniformity when mesh members of different meshes are divided according to an embodiment of the present disclosure;

Fig. 32 is a comparison chart of instability when mesh members of different meshes are divided according to an embodiment of the present disclosure;

Fig. 33 is a schematic cross-sectional view of a one-way valve provided by an embodiment of the present disclosure;

Fig. 34a is a schematic cross-sectional view of another one-way valve provided by an embodiment of the present disclosure;

Fig. 34b is a schematic cross-sectional view of another one-way valve provided by an embodiment of the present disclosure;

Fig. 35 is a schematic diagram of a check valve spool provided by an embodiment of the present disclosure;

Fig. 36 is a perspective view of another check valve spool provided by an embodiment of the present disclosure;

Fig. 37a is a cross-sectional view of another check valve spool provided by an embodiment of the present disclosure;

Fig. 37b is a cross-sectional view of another check valve spool provided by an embodiment of the present disclosure;

Fig. 37c is a cross-sectional view of another check valve spool provided by an embodiment of the present disclosure;

Fig. 37d is a cross-sectional view of another check valve spool provided by an embodiment of the present disclosure;

Fig. 37e is a cross-sectional view of another check valve core provided by an embodiment of the present disclosure.

Reference signs:

100: heat exchanger; 200: liquid separator; 300: one-way valve; 110: refrigerant inlet and outlet; 120: heat exchange branch; 130: heat exchange flow path; 140: heat exchange tube; 151: first bypass tube 152: Second bypass pipeline; 220: Housing; 230: Dispensing cavity; 240: Confluence pipe; 250: Distributing branch; 260: Mesh piece; 320: Valve housing; : valve seat; 111: the first refrigerant inlet and outlet; 112: the second refrigerant inlet and outlet; 121: the first heat exchange branch; 122: the second heat exchange branch; 123: the third heat exchange branch; 124: the fourth exchange Hot branch; 211: first liquid separator; 212: second liquid separator; 213: third liquid separator; 214: fourth liquid separator; 221: liquid separator; 222: confluence port; 231: first 232: the second liquid storage chamber; 233: the channel of the liquid storage chamber; 234: the confluence cavity; 235: the first branch cavity; 236: the second branch cavity; 240: the confluence pipe; 241: the first branch cavity A pipe section; 242: the second pipe section; 251: the first liquid branch pipe; 252: the second liquid branch pipe; 253: the third liquid branch pipe; 311: the first one-way valve; 312: the second one-way valve; 321 : valve inlet; 322: valve outlet; 323: valve channel; 324: valve body throat; 331: first end; 332: second end; 333: valve core body; 334: stable block; 335: hollow groove; 336 : hollow cavity; 400, tee pipe.

Detailed ways

In order to understand the characteristics and technical content of the embodiments of the present disclosure in more detail, the implementation of the embodiments of the present disclosure will be described in detail below in conjunction with the accompanying drawings. The attached drawings are only for reference and description, and are not intended to limit the embodiments of the present disclosure. In the following technical description, for purposes of explanation, numerous details are set forth in order to provide a thorough understanding of the disclosed embodiments. However, one or more embodiments may be practiced without these details. In other instances, well-known structures and devices may be shown simplified in order to simplify the drawings.

The terms "first", "second" and the like in the description and claims of the embodiments of the present disclosure and the above drawings are used to distinguish similar objects, and are not necessarily used to describe a specific sequence or sequence. It should be understood that the data so used may be interchanged under appropriate circumstances so as to facilitate the embodiments of the disclosed embodiments described herein. Furthermore, the terms "comprising" and "having", as well as any variations thereof, are intended to cover a non-exclusive inclusion.

In the embodiments of the present disclosure, the orientations or positional relationships indicated by the terms "upper", "lower", "inner", "middle", "outer", "front", "rear" etc. are based on the orientations or positional relationships shown in the drawings. Positional relationship. These terms are mainly used to better describe the embodiments of the present disclosure and their implementations, and are not used to limit that the indicated devices, elements or components must have a specific orientation, or be constructed and operated in a specific orientation. Moreover, some of the above terms may be used to indicate other meanings besides orientation or positional relationship, for example, the term "upper" may also be used to indicate a certain attachment relationship or connection relationship in some cases. Those skilled in the art can understand the specific meanings of these terms in the embodiments of the present disclosure according to specific situations.

In addition, the terms "setting", "connecting" and "fixing" should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection, or an electrical connection; it can be a direct connection, or an indirect connection through an intermediary, or two devices, components or Internal connectivity between components. Those skilled in the art can understand the specific meanings of the above terms in the embodiments of the present disclosure according to specific situations.

Unless stated otherwise, the term "plurality" means two or more.

In the embodiments of the present disclosure, the character "/" indicates that the preceding and following objects are an "or" relationship. For example, A/B means: A or B.

The term "and/or" is an associative relationship describing objects, indicating that there can be three relationships. For example, A and/or B means: A or B, or, A and B, these three relationships.

The embodiments of the present disclosure relate to the values in the disclosed tables, the units corresponding to indoor working conditions and outdoor working conditions are °C, the units corresponding to heating capacity, cooling capacity and power are all W, and the units corresponding to energy efficiency and APF are W/W .

It should be noted that, in the case of no conflict, the embodiments and the features in the embodiments of the present disclosure may be combined with each other.

The refrigeration cycle system includes a heat exchanger 100 and a one-way valve 300 , and the one-way valve 300 is arranged in the heat exchanger 100 .

In some embodiments, when the cooling/heating power set by the user is different during the use of the air conditioner, the flow rate and pressure of the refrigerant discharged by the compressor also change accordingly, so that the state of the refrigerant flowing through the heat exchanger is not complete. Consistent, for example, the pressure of the refrigerant is higher in the high power state, and the refrigerant pressure is lower in the low power state; at the same time, the temperature of the environment where the heat exchanger is located can also affect the degree of change in the temperature and pressure state of the refrigerant in the heat exchanger . Affected by the above factors, in some cases, when the refrigerant flows through the check valve, the pressure difference on both sides of the valve core is relatively small, which is prone to the valve core not opening normally, still blocked at the throat of the valve body or the opening range Abnormal problems affect the normal use of the check valve.

In order to solve the problem that the pressure difference between the two sides of the one-way valve 300 is too small to open normally, optionally, the one-way valve 300 in the embodiment of the present disclosure satisfies the following relationship:

L ₃ ⁴ *R≤Z1,

As shown in Figure 2, where _L3 is the throat diameter of the valve body of the one-way valve, in cm, R is the equivalent radius of the spool of the one-way valve, in cm; Z1 is the set value.

In the embodiment shown in Fig. 2, the throat of the valve body of the check valve 300 is in the form of a cylindrical throat of equal width, and the value of L ₃ is the diameter length value of the cylindrical throat; and in some other embodiments Among them, the valve body throat of the one-way valve 300 is in the form of a tapered throat, as shown in FIG. 33 , and corresponding to this form, L ₃ is taken as the maximum width of the tapered throat.

Optionally, the value range of Z1 is 2<Z1<20.

Optionally, Z1 is determined according to the rated cooling capacity Q of the refrigeration cycle system. In this embodiment, different from the type selection method of the check valve used in the air conditioner in the prior art, the size design of the check valve selected in this application can make the valve core work with the refrigeration cycle system to apply a single The pressure difference between the inlet and outlet of the check valve is matched, so that the check valve can still work normally under a small pressure difference; this enables the air conditioner to switch the refrigerant flow direction (such as cooling flow direction and heating flow direction) accurately. Open or block the one-way valve, so that the heat exchanger can normally perform the switching operation of different flow paths.

In some embodiments, a relationship between Z1 and the rated cooling capacity Q is constructed, and the optional forms include a one-to-one relationship table between Z1 and Q, etc., corresponding to air conditioner models with different rated cooling capacities, the selected unidirectional The relationship between the specification form of the valve and the rated cooling capacity of the model satisfies the relationship.

Optionally, in the above correlation, there is a positive correlation between Z1 and the rated cooling capacity Q, that is, the larger the rated cooling capacity Q of the refrigeration cycle system is, the larger Z1 is.

In some other embodiments, the relationship between Z1 and the rated cooling capacity Q can also be expressed by a formula. Optionally, the formula for determining Z1 according to the rated cooling capacity Q of the refrigeration cycle system is as follows:

Among them, λ is the local resistance coefficient, and z ₂ is the weighting coefficient. The rho _agent is the refrigerant density, and the unit is kg/ ^m3 , and the rho _core is the valve core density of the check valve, and the unit is kg/ ^m3 .

Optionally, the local resistance coefficient λ ranges from 0.3 to 0.55.

Optionally, z ₂ =1.5*10 ⁵ .

Optionally, difluoromethane is selected as the refrigerant, and the corresponding refrigerant density is 0.8-1.1 g/cm3.

Optionally, the density of the spool of the one-way valve is 0.94-0.96 kg/m ³ .

Then the relationship satisfied by the one-way valve 300 in the embodiment of the present disclosure can be expressed as

Among them, m is the refrigerant flow rate.

Here, the derivation process of the above formula is as follows:

The local resistance Δp between the inflow/outflow ends of the check valve can be expressed as

The force bearing area of the spool is 4R ² , so the force of the spool is 4R ² *△P;

At the same time, the volume of the spool is 0.5*(13/6)*π*R ³ , so the gravity on the spool is 0.5*(13/6)*π*R ³ *g; among them, (13/6) is It is obtained by adding the coefficients in the volume of a semicircle and the volume of a cylinder, specifically 13/6=2/3+3/2; g is the gravity constant, and the value for this calculation is 950;

The one-way valve in the embodiment of the present disclosure is placed vertically, and the flow direction of the one-way valve in the conducting state is from bottom to top, so the force state that the valve core needs to satisfy when the one-way valve is open can be expressed by the following formula :

4R ² *△P≥0.5*(13/6)*π*R ³ *g;

After finishing the above inequalities, the relationship between the above-mentioned rated cooling capacity Q and the check valve can be obtained:

Here, take the air conditioner models with rated cooling capacity of 3.5KW, 5.0KW and 7.2KW as examples, and substitute the above formula for calculation; assume that the environmental parameters and air conditioner status parameters are as follows,

Environmental parameters: the outdoor ambient temperature is 35°C, and the indoor ambient temperature is 27°C;

Air conditioner status parameters:

The condensation temperature is 45°C, the condensation pressure is 2.7948MPa, and the subcooling degree is 5°C;

The evaporation temperature is 17°C, the evaporation pressure is 1.3559MPa, and the degree of superheat is 5°C;

The heat exchanger inlet enthalpy value is 275; the heat exchanger outlet enthalpy value is 524;

For an air conditioner with a rated cooling capacity of 3.5KW, the total refrigerant flow rate is 0.014kg/s, and the check valve refrigerant flow rate is 0.010kg/s;

For the air conditioner model with a rated cooling capacity of 5.0KW, the total refrigerant flow rate is 0.019kg/s, and the refrigerant flow rate of the check valve is 0.014kg/s;

For the air conditioner model with a rated cooling capacity of 7.2KW, the total refrigerant flow rate is 0.027kg/s, and the refrigerant flow rate of the check valve is 0.020kg/s;

Bringing the specific values of the above parameters into the equation gives:

For air conditioners with a rated cooling capacity of 3.5KW: L ₃ ⁴ *R≤2.8;

For air conditioners with a rated cooling capacity of 5.0KW: L ₃ ⁴ *R≤5.7;

For air conditioners with a rated cooling capacity of 7.2KW: L ₃ ⁴ *R≤11.9;

Here, taking an air conditioner model with a rated cooling capacity of 7.2kW as an example, the check valve applied to this application calculated according to the above formula satisfies the relationship L ₃ ⁴ *R≤Z1=11.9, and other models Compared with the one-way valve (L ₃ ⁴ *R≤Z1=6), the test data in the two states of rated heating and low temperature heating are shown in Table 1 below:

Table 1

It can be seen that, under the two heating states, the pressure loss of the one-way valve with the limited dimensional relationship in the scheme of this application is significantly lower than that of the one-way valve with other dimensional relationships, and the technical scheme of the application can achieve a lower Flow resistance, reducing pressure loss.

Optionally, as shown in FIG. 1 and FIG. 3 , the heat exchanger 100 includes a heat exchanger body and a check valve 300 .

The main body of the heat exchanger is provided with a first refrigerant inlet and outlet 111 and a second refrigerant inlet and outlet 112 . When the heat exchanger is used as an evaporator, the refrigerant flows in through the first refrigerant inlet and outlet 111 and flows out through the second refrigerant inlet and outlet 112; A refrigerant outlet 111 flows out.

The flow direction of the one-way valve 300 is limited to conduction when the heat exchanger acts as an evaporator, and to block when the heat exchanger acts as a condenser.

Optionally, the one-way valve 300 is disposed at the first refrigerant inlet and outlet 111 and/or the second refrigerant inlet and outlet 112 .

Optionally, as shown in FIG. 4 , the first refrigerant inlet and outlet 111 and the second refrigerant inlet and outlet 112 are communicated through w heat exchange branches 120 . Wherein, w is an integer greater than 1. In this way, a plurality of heat exchange branches 120 are set between the first refrigerant inlet and outlet 111 and the second refrigerant inlet and outlet 112, so that the refrigerant can pass through the heat exchange branches 120 in different forms, so that the circulation of the refrigerant has diversity, and the refrigeration equipment can be improved. Heat transfer efficiency under different working conditions of cooling or heating.

Optionally, each heat exchange branch 120 includes n1 heat exchange tubes 140 communicating with each other, where n1≤8. In this way, setting the number of heat exchange tubes 140 on each heat exchange branch 120 within a range of less than or equal to 8 can avoid the excessive length of heat exchange tubes 140 on each heat exchange branch 120 causing pressure. The drop rate changes too quickly to avoid the reduction of energy efficiency of the refrigeration equipment.

Optionally, the w heat exchange branches 120 are connected between the first refrigerant inlet and outlet 111 and the second refrigerant inlet and outlet 112 through the liquid separator 200 . In this way, the liquid separation function of the liquid separator 200 can be used to divide the refrigerant flow along the heat exchange branch 120 to form multiple flow channels to make the circulation of the refrigerant more reasonable. When the heat exchanger is used as an evaporator or a condenser High heat transfer efficiency can be maintained under all conditions.

Optionally, the dispenser 200 includes: a first dispenser 211 , a second dispenser 212 , a third dispenser 213 and a fourth dispenser 214 . The first liquid distributor 211 communicates with the first refrigerant inlet and outlet 111; the second liquid distributor 212 communicates with the first liquid distributor 211 through the first one-way valve 311, and the flow direction of the first one-way valve 311 is toward the second liquid distributor 212; the third liquid distributor 213 communicates with the first liquid distributor 211 and the second liquid distributor 212; the fourth liquid distributor 214 communicates with the second refrigerant inlet and outlet 112, and a split port passes through the second one-way valve 312 and The third liquid distributor 213 communicates, and the remaining flow openings communicate with the second liquid distributor 212 . In this way, the refrigerant that flows through is separated by a plurality of separators 200, and the circulation of the refrigerant is controlled in combination with the first one-way valve 311 and the second one-way valve 312, so that the forward and reverse directions of the refrigerant can be circulated so as to have different The circulation path can maintain high heat exchange efficiency when the heat exchanger is used as an evaporator or a condenser.

Optionally, as shown in FIG. 5 , the first liquid distributor 211 communicates with the first refrigerant inlet and outlet 111 through n2 heat exchange tubes 140 . In this way, the heat exchange tube 140 provided at the first refrigerant inlet and outlet 111 is used as a subcooling section, which can further liquefy the refrigerant flowing through and increase the liquefaction rate of the refrigerant.

Optionally, n2≤5. In this way, the number of heat exchange tubes 140 used as the subcooling section is limited to less than or equal to 5, which can prevent the increase in resistance caused by the excessive length of the subcooling section when the heat exchanger is used as an evaporator. The pressure drop is too high, which affects the heat transfer efficiency of the heat exchanger.

More specifically, n2=2, or, n2=3, or, n2=4.

Optionally, as shown in FIG. 21 , when the heat exchanger is used as an evaporator, n heat exchange tubes 140 form N heat exchange channels 130 . When the heat exchanger is used as an evaporator, the number N of heat exchange channels 130 composed of heat exchange tubes 140 is determined according to the total number n of all heat exchange tubes 140 . In this way, the flow paths of the heat exchange tubes 140 of the heat exchanger can be reasonably allocated to prevent too many or too few heat exchange tubes 140 in a single heat exchange flow path 130, resulting in insufficient evaporation or condensation, which can improve the efficiency of heat transfer. heat transfer efficiency of the heater.

Wherein, n=w*n1, or, n=w*n1+n2. n2 is the number of heat exchange tubes 140 communicating between the first liquid separator 211 and the first refrigerant inlet and outlet 111 .

Optionally, n/a≤N≤n/b, a and b are weighting coefficients. In this way, when n and N satisfy the formula, the pressure drop of the overall heat exchanger can be avoided from being too high, and the heat exchange efficiency can be improved.

Optionally, INT(n/a)≦N≦INT(n/b), INT is a function that rounds a value down to the nearest integer.

Optionally, a=5 or 6, b=2 or 3. In this way, limiting the value ranges of a and b to this area can make the number of heat exchange channels 130 composed of n heat exchange tubes 140 more reasonable when the heat exchanger is used as an evaporator, which is beneficial to the evaporator. The evaporation efficiency of the internal refrigerant is improved, thereby improving the heat exchange efficiency of the heat exchanger.

More specifically, a=5, and b=3.

Optionally, as shown in Figures 6 and 7, when the heat exchanger is used as an evaporator, n heat exchange tubes 140 form N heat exchange channels 130. When the heat exchanger is used as a condenser, n heat exchange tubes 140 form M heat exchange channels 130 . where N≠M. In this way, when the heat exchanger is used as an evaporator and when the heat exchanger is used as a condenser, its operating principle is different. Using the same number of heat exchange channels 130 for the two cannot take into account the heat exchange efficiency of the two, so the When the heat exchanger is used as an evaporator and when the heat exchanger is used as a condenser, the number of heat exchange channels 130 through which the refrigerant circulates is different, which can meet the different needs of evaporation and condensation, and improve heat transfer. Efficiency when the heat exchanger acts as an evaporator and when the heat exchanger acts as a condenser.

Optionally, when the heat exchanger is used as an evaporator, all the heat exchange tubes 140 form N heat exchange channels 130 . When the heat exchanger is used as a condenser, all the heat exchange tubes 140 form M heat exchange channels 130 . Among them, N>M. In this way, when the heat exchanger is used as an evaporator, the internal refrigerant changes from a liquid state to a gas state, and the volume of the refrigerant will increase, so more heat exchange channels 130 are required, and the heat exchanger acts as a condensing In the case of a heat exchanger, the internal refrigerant is in the process of changing from gas to liquid, and the volume of the refrigerant will decrease. At this time, fewer heat exchange channels 130 can accommodate the refrigerant. Therefore, setting N to be greater than M can make the exchange When the heater is used as an evaporator or as a condenser, the refrigerant can pass through the refrigerant smoothly, reducing the resistance of the refrigerant flow, that is, reducing the pressure drop and improving the heat exchange efficiency.

Optionally, 30%≤M/N≤70%. Preferably, 50%≤M/N≤70%, in this way, the energy efficiency of the refrigeration equipment can be greatly improved, especially in the low-temperature intermediate refrigeration stage, the energy efficiency can be significantly improved, the energy efficiency level of the product can be improved, and the energy saving and environmental protection can be improved at the same time. Commercial value, enhance the competitiveness of products.

Taking M/N=50% as an example compared with M=N, its energy efficiency performance at each stage is as follows:

In the case of M=N, the energy efficiency of each stage is shown in Table 2 below:

Table 2

In the case of M/N=50%, the energy efficiency of each stage is shown in Table 3 below:

table 3

From the comparison of the data in the above two tables, it can be seen that in the low-temperature intermediate refrigeration stage, the heat exchanger with M/N=50% can greatly improve the energy efficiency of the product, and can improve the energy efficiency level of the product.

More specifically, M/N=1/2, or, M/N=1/3, or, M/N=2/3, or, M/N=3/5 or M/N=4/7. Preferably, M/N=1/2 or M/N=4/7.

Optionally, a heat exchanger with M/N=1/2 is used in the 3.5KW model. In this way, the setting of the number of heat exchange channels can better meet the use conditions of the 3.5KW model and improve the energy efficiency ratio of the product.

The energy efficiency performance of the 3.5KW model under different ratios of M and N is as follows:

In the case of the preferred solution M/N=1/2 in this embodiment, the energy efficiency performance of the product is shown in Table 4 below:

Table 4

In the case of M=N, the energy efficiency performance of the product is shown in Table 5 below:

table 5

In the case of the preferred scheme M/N=1/4 of this embodiment, the energy efficiency performance of the product is shown in Table 6 below:

Table 6

In the case of the preferred scheme M/N=3/4 in this embodiment, the energy efficiency performance of the product is shown in Table 7 below:

Table 7

Based on the above table, it can be seen that for the 3.5KW model, when the heating branch N is equal to 4, the optimal cooling branch M is 2, and the maximum APF is 5.10. At this time, M/N=1/2, if M drops to 1, the APF will drop to 4.99. On the contrary, if M increases to 3, the APF will drop to 4.62. It can be seen that using M/N=1/2 in the 3.5KW model can greatly improve energy efficiency, and is more energy-saving and environmentally friendly.

Optionally, a heat exchanger with M/N=4/7 is used in the 7.2KW model. In this way, the setting of the number of heat exchange channels can better meet the use conditions of the 7.2KW model and improve the energy efficiency ratio of the product.

The energy efficiency performance of the 7.2KW model under different ratios of M and N is shown in the following table:

In the case of the preferred scheme M/N=4/7 in this embodiment, the energy efficiency performance of the product is shown in Table 8 below:

Table 8

In the case of M=N, the energy efficiency performance of the product is shown in Table 9 below:

Table 9

In the case of the preferred scheme M/N=3/7 in this embodiment, the energy efficiency performance of the product is shown in Table 10 below:

Table 10

In the case of the preferred scheme M/N=2/7 in this embodiment, the energy efficiency performance of the product is shown in Table 11 below:

Table 11

In the case of the preferred scheme M/N=5/7 in this embodiment, the energy efficiency performance of the product is shown in Table 12 below:

Table 12

Based on the above table, it can be seen that for the 7.2KW model, when the heating branch N is equal to 7, the optimal cooling branch is 4, and the maximum APF is 4.56. At this time, M/N=0.57. If M is reduced to 3, then APF drops to 4.45. If M drops to 2, APF drops to 4.32. Conversely, if M increases to 5, APF drops to 4.35. It can be seen that using M/N=4/7 in a 7.2KW model can greatly improve energy efficiency and make it more Energy saving and environmental protection.

Optionally, N-M≥2. In this way, when the heat exchanger is used as an evaporator and when the heat exchanger is used as a condenser, widening the gap in the number of flow paths can accelerate the cycle and increase the heat transfer coefficient.

Optionally, n heat exchange tubes 140 are arranged in m rows, where m≤5.

Optionally, m is 1, 2 or 3.

Optionally, the value of m is determined by the corresponding relationship between the number n of heat exchange tubes 140 , the capacity section of the refrigeration equipment, and the diameter of the heat exchange tubes 140 . In this way, when the capacity section of the refrigeration equipment is determined, the space size of the position is generally determined. At this time, the heat exchange tube 140 can be determined according to the diameter of the heat exchange tube 140 and the number n of the heat exchange tube 140. The 140 always needs to occupy a space, so that the heat exchange tubes 140 can be arranged in a reasonable arrangement so that the occupied space can be kept within a reasonable range, which is convenient for installation and use.

More specifically, the corresponding relationship between the number m of rows of heat exchange tubes 140 and the number n of heat exchange tubes 140, the capacity section of the refrigeration equipment and the diameter of the heat exchange tubes 140 is shown in Table 13 below:

Table 13

Optionally, as shown in Figures 8 and 9, when the n heat exchange tubes 140 on the heat exchanger 100 are evenly distributed to the w heat exchange branches 120 in integers and there are more than h heat exchange tubes 140, the The h heat exchange tubes 140 are drawn out, or the h heat exchange tubes 140 are connected to the first refrigerant inlet and outlet 111 as a subcooling section, or the h heat exchange tubes 140 are evenly distributed to the h heat exchange branches 120, wherein h <w. In this way, the number of heat exchange tubes 140 on each heat exchange branch 120 can be kept as close as possible, so that the resistance of each heat exchange branch 120 is similar, so as to prevent the flow rate of refrigerant from being different due to different resistances, which in turn leads to the overall heat exchange of the heat exchanger. Not even enough.

More specifically, in the case of w=3, n=10, one heat exchange tube 140 is extracted, and three heat exchange tubes 140 are installed on each heat exchange branch 120, or three heat exchange tubes 140 are installed on each heat exchange branch 120. One heat exchange tube 140, one heat exchange tube 140 communicates with the first refrigerant inlet and outlet 111 as a subcooling section, or as shown in Figure 8, three heat exchange tubes 140 are arranged on three heat exchange branches 120, and the other one Four heat exchange tubes 140 are arranged on the heat exchange branch 120 .

More specifically, in the case of w=5, n=22, 2 heat exchange tubes 140 are extracted, and 4 heat exchange tubes 140 are set on each heat exchange branch 120, or 4 heat exchange tubes 140 are set on each heat exchange branch 120. Two heat exchange tubes 140, two heat exchange tubes 140 communicate with the first refrigerant inlet and outlet 111 as a subcooling section, or as shown in Figure 9, five heat exchange tubes 140 are arranged on two heat exchange branches 120, and the other three Four heat exchange tubes 140 are arranged on the heat exchange branch 120 .

Optionally, the second liquid distributor 212 is connected to the manifold connected with the refrigerant inlet and outlet and a plurality of liquid distribution ports 221 communicated with the plurality of heat exchange branches 120 one by one; wherein the second liquid distributor 212 is vertically arranged so that the distribution The liquid port 221 is facing upwards and the confluence pipe is facing downwards, as shown in FIG. 10 ; and when the heat exchanger 100 is used as a condenser, at least one liquid inlet and at least one liquid outlet in the liquid distribution port 221;

The first one-way valve 311 is arranged at the refrigerant inlet and outlet 110, and its flow direction is limited to conducting when the heat exchanger 100 is used as an evaporator, and blocking and making the second The liquid separator 212 is confluent and liquid storage.

Optionally, the number of liquid separation ports 221 is 3, and when the heat exchanger 100 is used as a condenser, 2 of them are liquid-inlet and 1 is liquid-outlet.

Yet another option, as shown in FIG. 11 , the second liquid distributor 212 is arranged obliquely, the liquid dispensing port 221 is arranged obliquely upward, and the confluence pipe 240 is arranged obliquely downward, which can also realize the liquid storage function of the liquid distributor, and the When the heater 100 is used as a condenser, at least one liquid inlet and at least one liquid outlet of the liquid distribution port 221 are used.

Optionally, when the second liquid distributor 212 is arranged obliquely, the inclination angle ∠α≤β with respect to the vertical direction, where β is a preset angle value.

Optionally, the value range of β is 10-45°.

Optionally, the value range of β is 10-20°.

Optionally, as shown in FIGS. 1 and 3 , the heat exchanger 100 includes a heat exchanger body, a liquid separation and storage device, and a one-way conduction device.

The heat exchanger body includes a first refrigerant inlet and outlet 111, a second refrigerant inlet and outlet 112, and w heat exchange branches connected between the first refrigerant inlet and outlet 111 and the second refrigerant inlet and outlet 112. w is an integer greater than 1.

The liquid separation and storage device includes a confluence pipe connected with the first refrigerant inlet and outlet 111 or the second refrigerant inlet and outlet 112 , and a plurality of liquid distribution ports 221 connected with part of the heat exchange branches one by one. The liquid separation and storage device is configured to divide the refrigerant delivered by the refrigerant inlet and outlet to multiple heat exchange branches 120 when the heat exchanger 100 is used as an evaporator, and when the heat exchanger 100 is used as a condenser Lower confluence and storage.

Optionally, the liquid separation and storage device includes a liquid dispenser 200 . Optionally, the dispenser 200 is the first dispenser 211 , the second dispenser 212 , the third dispenser 213 or the fourth dispenser 214 .

Optionally, in this embodiment, the liquid distributor 200 includes a liquid separation chamber 230 , and a confluence pipe 240 and a plurality of liquid distribution ports 221 respectively communicating with the liquid separation chamber 230 . In the case where the heat exchanger 100 is used as a condenser, at least one liquid inlet and at least one liquid outlet of the liquid separation port 221 are used for confluence through the liquid separator and make the liquid separation chamber 230 store part of the refrigerant.

The one-way communication device is communicated between the first refrigerant inlet and outlet 111 and the manifold 240 , or communicated between the second refrigerant inlet and outlet 112 and the manifold 240 . The flow direction of the one-way conduction device is limited to conduction when the heat exchanger 100 serves as an evaporator, and is blocked when the heat exchanger 100 serves as a condenser.

Optionally, the one-way conducting device includes a one-way valve or an electronically controlled valve. It should be understood that the type of the one-way valve shown in the technical solution of the present application is only an optional exemplary description, and does not limit the protection scope of the solution. Functional parts or components can also be used as optional alternatives of this example, and should also be covered within the scope of protection of this application.

Optionally, in this embodiment, the one-way valve 300 is disposed on the manifold 240 . The flow direction of the one-way valve 300 is restricted to conduct when the heat exchanger 100 acts as an evaporator, and to block and allow the liquid separation chamber 230 to store liquid when the heat exchanger 100 acts as a condenser.

The one-way valve 300 includes a valve outlet 322 connected to the manifold and a valve inlet 321 connected to the corresponding refrigerant inlet and outlet. When the refrigerant flows from the valve inlet 321 to the valve outlet 322, the one-way valve is in a conducting state, and the refrigerant flows from the valve outlet 322 to When the valve inlet is 321, the one-way valve is in blocking state.

The electronically controlled valve is configured to be controlled to open when the heat exchanger 100 is used as an evaporator, and controlled to be closed when the heat exchanger 100 is used as a condenser.

Exemplarily, as shown in FIG. 3 , taking the second liquid separator 212 as an example, when the heat exchanger is used as a condenser, the second refrigerant inlet and outlet 112 is used as the refrigerant inlet, and the first refrigerant inlet and outlet 111 is used as the refrigerant inlet and outlet. After the refrigerant flows into the heat exchanger from the second refrigerant inlet and outlet 112, the refrigerant is divided into the first heat exchange branch 121 and the second heat exchange branch 122 respectively. At this time, the first one-way valve 311 and the second The one-way valves are all blocked, and the flow out to the first heat exchange branch 121 and the second heat exchange branch 122 continues to flow into the second liquid distributor 212 for confluence, and the converging refrigerant is connected from the second liquid distributor 212 A liquid distribution port of the third heat exchange branch 123 flows out. Since the liquid distribution ports of the second liquid distributor 212 are all set upwards, in this state, part of the refrigerant can be stored in the second liquid distribution port under the action of gravity. The liquid storage function of the second liquid distributor 212 is realized in the liquid distribution chamber of the liquid distribution device 212 and part of the pipe section from the liquid distribution chamber to the one-way valve.

The heat exchanger provided by the embodiments of the present disclosure can store part of the refrigerant through the cooperation of the split liquid storage device and the one-way conduction device, so that the heat exchanger can also have a certain liquid storage function. There is an air conditioner that only uses the accumulator to store liquid. This embodiment can expand the refrigerant storage range of the air conditioner, especially in the low-load state, can reduce the heat circulation of excess refrigerant, so that the actual refrigerant circulation of the air conditioner can be compared with the current The working performance is compatible, which improves the adjustment range of the air conditioner to the refrigerant circulation amount under different operating conditions.

Here, the description will be continued by taking the outdoor heat exchanger of the air conditioner as an example. Generally speaking, for a given air conditioner and operating conditions, there is an optimal refrigerant charge, which can make the air conditioner perform optimally; usually, the optimal refrigerant for heating operation The charging amount is slightly larger than that during cooling operation, so during cooling operation, the excess refrigerant is generally "stored" in the air conditioner in liquid form; in this scheme, the outdoor heat exchanger is used as " Condenser", so the internal volume of the liquid separator in the outdoor heat exchanger can be used to realize the function of "liquid storage".

At the same time, for the air conditioner, when the air conditioner is turned on and off, it is affected by the balance between high and low pressure, and the refrigerant will flow from the low pressure side to the high pressure side; in this embodiment, most of the refrigerant (60 % or more) is stored in the outdoor unit; most (60% or more) of the refrigerant (60% or more) is stored in the indoor unit in the shutdown state.

When the air conditioner is running in heating mode, the outdoor heat exchanger is used as an "evaporator". The heat exchanger is used as a "condenser". When the air conditioner is turned on, the amount of refrigerant stored in the liquid separator is more than when it is turned off. When the air conditioner is shut down, some refrigerant is stored in the indoor and outdoor heat exchangers, compressor cavity, gas-liquid separator and other components.

Under the APF test standard, there are 100% load and part load test conditions in both the cooling and heating operation of the air conditioner. When greater than 100% load.

Exemplarily, an air conditioner using a liquid distributor with a common shunt design without a liquid storage function is compared with an air conditioner with a liquid distributor with a variable shunt design and a one-way valve with a liquid storage function, and the capabilities, Power and energy efficiency, the test data are shown in Table 14 below:

Table 14

It can be seen from the above table that since the variable split flow achieves a better refrigeration flow path and the liquid separator cooperates with the one-way valve with the liquid storage function, this application uses the variable split flow design liquid separator with the one-way valve with the liquid storage function The energy efficiency that the air conditioner can achieve during operation is obviously better than that of the air conditioner with the liquid separator without the liquid storage function of the ordinary split flow design.

At the same time, for the same air conditioner, this application uses two different liquid separators in the heat exchanger to test the energy efficiency of the air conditioner with/without liquid storage function. The volume of the liquid separator in the scheme ② is obviously larger than the volume of the liquid distributor in the scheme ①. The test conditions are operating under rated cooling conditions, the indoor wet and dry bulb temperature is 27°C/19°C, and the outdoor dry and wet bulb temperature is 35°C/24°C. The test results are compared as shown in Table 15:

Table 15

the	能力ability	功率power	能效efficiency
方案①Scheme ①	3440W3440W	861W861W	4.004.00
方案② Scheme ②	3445W3445W	858W858W	4.024.02

From the comparison of the data in the above table, it can be seen that in the prior art, the form of the liquid separator is generally only considered for the "splitting" function, so in the case of satisfying the "shunting" function, the liquid separator is generally designed to be as small as possible. , in order to reduce the occupation of space volume and manufacturing cost; and this application uses a liquid separator with a larger volume liquid distribution chamber, which can realize the liquid storage function in the cooling mode, and can improve the liquid separation of the application of this liquid storage function. The energy efficiency of the air conditioner with a liquid separator in the actual operation process is better than that of an air conditioner with a common liquid separator.

Further, the manifold 240 of the liquid separator 200 communicates with the first refrigerant inlet and outlet 111 or the second refrigerant inlet and outlet 112 , and the plurality of liquid distribution ports 221 correspond to the plurality of heat exchange branches one by one.

In order to realize the liquid storage function of the liquid separator 200, avoid the problem of excessive liquid storage due to the excessive volume of the liquid separator cavity, and also to adapt to the liquid storage requirements of different air conditioner models, optionally, V ≤f2*Q, f2 is the preset multiple, V is the volume of the liquid separation chamber in cm ³ , Q is the rated cooling capacity in kW.

Optionally, there are two types of heat exchangers with variable flow splits, including the four-branch variable flow split shown in FIG. 3 and the three-branch variable split flow shown in FIG. 12 .

Optionally, for the four-branch variable-split heat exchanger, the value of f2 ranges from 8 to 12.

Optionally, the value of f2 is 10, that is, V≤10Q.

In this embodiment, for the four-branch variable-split heat exchanger, the relationship between the rated capacity of the unit and the charging volume is roughly: m=160Q; the normal heating mode requires a higher refrigerant charging volume than the cooling mode 10% to 15%, and the compressor gas-liquid separator can generally store 5% to 10% of the refrigerant, so the liquid separator actually needs to store 5% of the total refrigerant charge, if the actual storage capacity of the liquid separator exceeds this Filling 5% of the total amount may affect the actual refrigerant circulation of the air conditioner, so the liquid separator needs to store liquid m=160Q*5%=8Q at most.

Optionally, the type of refrigerant is difluoromethane (R32), and the density of the refrigerant is about 0.8-1.1g/cm3 in the actual operating temperature range. Calculated based on the upper limit of the density of the refrigerant of 0.8g/cm3, the volume of the liquid separation chamber itself cannot exceed 8Q/0.8=10Q, Q is calculated by kW.

For example, for an air conditioner with a rated cooling capacity of 3.5KW, the volume of the liquid separator of the selected liquid separator needs to meet V≤f2*Q=10*3.5=35, that is, the volume of the liquid separator should be Less than or equal to 35cm ³ .

Here, for the heat exchanger in the form of four-branch variable split flow, the application tested the operating performance of the same air conditioner under the conditions of f2 values of 8/10/12/14, etc. According to the value of f2) for comparison, the test data is shown in Table 16 below:

Table 16

f2取值f2 value	能力ability	功率power	能效efficiency
88	3446W3446W	857W857W	4.024.02
1010	3451W3451W	855W855W	4.044.04
1212	3440W3440W	856W856W	4.024.02
1414	3423W3423W	861W861W	3.963.96

It can be seen from the test data in the above table that within the range of f2 values (8-12) defined in this application, the value of f2 increases, and the energy efficiency gradually improves; but when f2 is too large (f2 exceeds 12), instead The problem arises of higher power but lower energy efficiency.

In still some optional embodiments, in order to realize the liquid storage function of the liquid distributor 200, avoid the problem of inability to store liquid due to the too small volume of the liquid separator cavity, and also to adapt to the storage capacity of different air conditioner models. Liquid demand, optionally, the liquid dispenser with liquid storage function in the technical solution of this application needs to meet the following conditions:

V≥f1*Q,

f1 is the preset multiple, V is the volume of the liquid separation chamber in cm ³ , Q is the rated cooling capacity in kW.

Optionally, for the heat exchanger in the form of four-branch variable split flow, the lower limit f1 of the volume of the liquid separator and the liquid separator ranges from 0.2 to 4.

Optionally, the value range of f1 is 1-4.

Optionally, the value range of f1 is 2-4.

Preferably, the value of f1 is 3. In this embodiment, the lower limit of the volume of the selected liquid separator mainly depends on the structural constraints. In consideration of reliability, the cross-sectional radius R of the liquid separator is generally about 4 times the radius r of the branch pipe, so as to ensure that the radius of the distributor is not If it is too large (that is, to prevent the radius of the distributor from affecting the space of the heat exchanger), it also ensures that there is a certain distance between the branch pipes, and the distributor still has sufficient strength after welding. That is, in this embodiment, as shown in FIG. 13 , the radius of the dispenser is R=4r, and R=1.4cm in this embodiment.

At the same time, when the liquid distributor 200 is actually processed, the depth of each liquid distribution branch pipe 250 inserted into the liquid distributor 200 must not be less than 3 mm. In addition, when the refrigeration mode is downward, the three liquid branch pipes of the liquid separator 200 are "two in and one out", and the refrigerant fluid needs to be bent at 180° in the liquid chamber of the liquid separator 200 (bottom in and top out). ; For stability considerations, the equivalent length from the lower end face of each liquid branch pipe to the lower end face of the liquid distributor needs to reach the distance requirement of 4r at least, so that the fluid can flow out from the two liquid branch pipes 250 smoothly, and then flow into the other branch pipe. The liquid branch pipe 250, that is, the depth of the entire liquid separator is about 0.3+1.4=1.7cm;

Therefore, the internal volume of the liquid separator must not be less than: π*R^2*1.7=10.455≈3Q.

Here, for the heat exchanger in the form of four-branch variable split flow, the application tested the operating performance of the same air conditioner under the conditions of f1 values of 1/2/3/4, etc. According to the value of f1) for comparison, the test data is shown in Table 17 below:

Table 17

f1取值f1 value	能力ability	功率power	能效efficiency
11	3426W3426W	865W865W	3.963.96
22	3438W3438W	861W861W	3.993.99
33	3442W3442W	860W860W	4.004.00
44	3442W3442W	859W859W	4.014.01

Combining the above table, it can be seen that for liquid dispensers with different volumes, the larger the value of f1, the lower the power and the higher the energy efficiency.

Similarly, for the heat exchanger in the form of three-branch variable split flow, it is used to connect the main circuit and the two branches by using the "one split into two" tee pipe 400 (the dotted box part) shown in Figure 12, Compared with the four-way variable splitter, its size is smaller.

Optionally, for the three-branch variable split flow heat exchanger, V≤f2*Q, and the value of f2 ranges from 0.75 to 1.0.

Still another option, for a three-branch variable-split heat exchanger, V≥f1*Q, and the value of f1 ranges from 0.15 to 0.25.

Considering that this type of liquid separator is relatively fixed and its volume change is small, for air conditioners with different rated cooling capacities, the corresponding relationship between the f value and the rated cooling capacity is shown in Table 18 below:

Table 18

额定制冷量Rated cooling capacity	2.6KW2.6KW	3.5KW3.5KW	5.0KW5.0KW	7.2KW7.2KW
f取值f value	0.720.72	0.530.53	0.370.37	0.250.25

Similarly, for an air conditioner with a rated cooling capacity of 3.5KW, after calculation, the volume of the liquid separator of the selected liquid separator needs to satisfy V≤f*Q=0.53*3.5≈1.86cm ³ .

Optionally, the dispenser 200 further includes a cylindrical housing 220 . Correspondingly, the liquid separation chamber 230 is formed inside the housing 220 and configured as a cylindrical cavity. When the heat exchanger is used as a "condenser", the refrigerant flows in/out from a plurality of liquid distribution ports, and the liquid separation cavity 230 serves as a space for storing part of the refrigerant.

Optionally, the liquid branch pipes 250 connected by the plurality of heat exchange branches 120 are arranged on one end surface of the housing 220 of the liquid distributor 200, and are arranged along the same circumferential line of the end surface, and the plurality of liquid branch pipes 250 are evenly arranged On the end surface of the liquid distributor 200 , the adjacent liquid distribution branch pipes 250 have the same spacing, so that the liquid distributor 200 can evenly distribute the refrigerant to the liquid distribution branch pipes 250 .

Optionally, each liquid distribution branch pipe 250 extends into the liquid separation chamber 230 through the end surface.

Optionally, the extension length of the liquid branch pipe 250 is 2-5 mm.

In this embodiment, the number of liquid branch pipes 250 is three.

Optionally, the inner diameter of the liquid separation chamber 230 is 3 to 5 times the outer diameter of the liquid separation branch pipe 250 . This can not only ensure that the radius of the liquid distributor is not too large (the radius of the liquid distributor affects the space of the heat exchanger), but also ensure that there is a certain distance between the liquid branch pipes, and the liquid distributor still has sufficient strength after welding.

Optionally, the heat exchanger further includes a liquid separator, as shown in FIGS. 14-24 .

Optionally, the liquid distributor includes a housing, a confluence pipe 240 , a first liquid branch pipe 251 and a second liquid branch pipe 252 . A liquid separation chamber is opened inside the housing, and the housing is provided with a first liquid distribution port and a second liquid distribution port. The second liquid branch pipe 252 communicates with the liquid chamber through the second liquid port.

Optionally, the liquid separation cavity includes a confluence cavity 234, a first branch cavity 235 and a second branch cavity 236, the first liquid distribution branch pipe 251 communicates with the first branch cavity 235 through the first liquid separation port, and the second branch cavity 235 communicates with the first branch cavity 235. The liquid branch pipe 252 communicates with the second branch cavity 236 through the second liquid port.

Optionally, the manifold 240 includes a bent and connected first pipe section 241 and a second pipe section 242, and the first pipe section 241 directly communicates with the liquid separation chamber.

The plane where the axes of the first pipe section 241 and the second pipe section 242 lie is the first plane. The plane where the axes of the first liquid branch pipe 251 and the second liquid branch pipe 252 are located is the second plane. Optionally, the first plane is non-perpendicular to the second plane.

The manifold 240 includes a first pipe section 241 and a second pipe section 242 , the plane where the axes of the first pipe section 241 and the second pipe section 242 lie is a first plane, and the angle between the first plane and the second plane is e. As shown in Figure 21. The first plane and the second plane are non-perpendicular, which means that the angle e between the first plane and the second plane is less than 90°. Optionally, the included angle between the first plane and the second plane is measured as an acute angle formed by the two planes. The first plane is not perpendicular to the second plane, so that the amount of refrigerant entering the first liquid branch pipe 251 and the second liquid branch pipe 252 through the first pipe section 241 is different. For example, when the angle between the first plane and the second plane is on the side of the first liquid branch pipe 251, under the action of gravity, the flow rate of the refrigerant flowing to the second liquid branch pipe 252 is greater than the flow rate to the first liquid branch pipe 251 . Similarly, when the angle between the first plane and the second plane is on the side of the second liquid branch pipe 252, under the action of gravity, the flow rate of the refrigerant flowing to the first liquid branch pipe 251 is greater than the flow rate of the second liquid branch pipe 252 .

Optionally, the liquid distributor provided in the embodiment of the present disclosure can be used as the first liquid distributor 211 of the heat exchanger as shown in FIG. 3 . In the heat exchanger shown in Figure 3, when the heat exchanger is used as an evaporator, the refrigerant flows into four parallel heat exchange branches after being divided by the first liquid separator 211, that is, the first heat exchange branch 121, The second heat exchange branch 122 , the third heat exchange branch 123 and the fourth heat exchange branch 124 . Wherein, in the direction shown in FIG. 3 , the refrigerant only flows into the fourth heat exchange branch 124 after passing through the liquid branch pipe on the left side of the first liquid distributor 211, and the refrigerant flows through the branch pipe on the right side of the first liquid distributor 211. The liquid branch pipe then flows into three heat exchange branches, namely the first heat exchange branch 121 , the second heat exchange branch 122 and the third heat exchange branch 123 . It can be seen that after the refrigerant passes through the first liquid separator 211 , the amount of refrigerant required by the two liquid branch pipes of the first liquid separator 211 is different. In the heat exchanger shown in Figure 3, the amount of refrigerant required by the liquid branch pipe on the right is about three times that of the liquid branch pipe on the left. The liquid separator provided by the embodiment of the present disclosure utilizes the gravitational force of the refrigerant in the flow process, passes through the first plane where the axes of the first pipe section 241 and the second pipe section 242 of the confluence pipe 240 are located, and the first liquid branch pipe 251 and the second branch pipe 251. The setting of the included angle between the second planes where the axes of the two liquid branch pipes 252 are located realizes the different amounts of refrigerant flowing out from different liquid branch pipes of the liquid separator, and satisfies the requirements of different amounts of refrigerant required by the liquid branch pipes. The heat exchange efficiency of the heat exchanger is improved.

Optionally, the embodiment of the present disclosure does not limit the number of liquid distribution ports opened on the housing, and the number of liquid distribution branch pipes corresponding to the liquid distribution ports. For example, the number of liquid distribution ports can be 3, 4, 5 or even more, correspondingly, the number of liquid branch pipes can also be 3, 4, 5 or even more.

Optionally, the included angle between the first plane and the second plane is less than 90 degrees. Optionally, the included angle between the first plane and the second plane is 0 degree, 30 degree, 60 degree, 70 degree or 80 degree or the like. The included angle between the first plane and the second plane is less than 90 degrees, so that after the refrigerant flows through the first pipe section 241 of the confluence pipe 240, it realizes a biased flow under the action of gravity, and then flows into the first liquid branch pipe 251 and the second branch pipe 251. The cooling capacities of the two branch pipes 252 are different.

Optionally, the inner diameter of the first pipe section 241 of the confluence pipe 240 is greater than the inner diameter of the first liquid branch pipe 251 .

Optionally, the inner diameter of the first liquid branch pipe 251 is larger than the inner diameter of the second liquid branch pipe 252 . In the liquid distributor provided in the embodiment of the present disclosure, an angle is set between the first plane where the axes of the first pipe section 241 and the second pipe section 242 of the confluence pipe 240 are located and the second plane where the axes of the two liquid branch pipes are located, And further cooperate with the inner diameter difference between the two liquid distribution branch pipes, further increase the difference in the amount of refrigerant flowing into the two liquid distribution branch pipes. Optionally, the first pipe segment 241 of the confluence pipe 240 is inclined to the side of the second liquid branch pipe 252, then, under the action of gravity, further matching that the inner diameter of the first liquid branch pipe 251 is larger than the inner diameter of the second liquid branch pipe 252, Making more refrigerant flow into the first liquid branch pipe 251 further increases the refrigerant flow difference between the two liquid branch pipes.

Only by limiting the difference in inner diameter between the first liquid branch pipe 251 and the second liquid branch pipe 252 , it is difficult to achieve a refrigerant flow rate difference of 2:1 between the first liquid branch pipe 251 and the second liquid branch pipe 252 . The reason is that, in the actual preparation process of the heat exchanger, the diameters of the copper tubes used in the heat exchanger all have certain specifications, that is, the diameters of the pipes cannot be selected arbitrarily, so it is usually impossible to find exactly the diameter of the two separation liquids. The pipe diameter scheme with the flow ratio of the branch pipe is 2:1; if the difference in the flow rate of the refrigerant separation liquid is realized by other means such as the difference in the length of the liquid separation branch pipe, bending, etc., it is not universal for mass-produced products. Therefore, only through the difference in the inner diameters of the first branch liquid pipe 251 and the second branch liquid pipe 252 , the refrigerant distribution with a refrigerant flow ratio of 2:1 cannot be accurately realized between the two branch liquid pipes.

Only by limiting the difference in inner diameter between the first liquid branch pipe 251 and the second liquid branch pipe 252, it is difficult to achieve a refrigerant distribution ratio of 3:1 between the first liquid branch pipe 251 and the second liquid branch pipe 252 or even greater Refrigerant distribution with poor refrigerant flow. The reason is that the inner diameter of the liquid branch pipe has a minimum limit. For example, the inner diameter of the liquid branch pipe cannot be lower than 3mm, or even not lower than 3.36mm. The copper tube with a lower diameter has actually become a capillary, and the capillary has a larger The flow resistance will form a throttling and pressure-reducing effect on the flow of refrigerant, which will increase the power of the compressor and reduce the performance of the system; it will even cause serious frosting on the outdoor heat exchanger when the air conditioner is running in heating mode, which will affect the performance of the system. Safety and reliability. Due to the limitation of the minimum inner diameter of the liquid branch pipe, in order to achieve the refrigerant distribution with a flow ratio of 3:1, the diameter of the other liquid branch pipe must be greater than 7mm. Optionally, 7mm here can be the outer diameter. Generally, The outer diameter is 1.4mm larger than the inner diameter. However, this obviously exceeds the inner diameter of the actual heat exchange tube used in the heat exchanger. The general tube diameter of the heat exchanger is 7mm, such as a tube-fin heat exchanger. Therefore, only by limiting the inner diameter difference between the first liquid branch pipe 251 and the second liquid branch pipe 252, it is difficult to realize the first liquid branch pipe 251 and the second liquid branch pipe 252 within the range allowed by the diameter of the heat exchange tube in the heat exchanger. The flow ratio of the second liquid branch pipe 252 is 3:1 for refrigerant distribution or even for refrigerant distribution with a larger refrigerant flow difference.

An included angle is set between the first plane where the axes of the first pipe section 241 and the second pipe section 242 passing through the manifold 240 are located and the second plane where the axes of the two branch pipes are located, and the two branches are further matched. The technical scheme of the inner diameter difference between the two liquid branch pipes can realize the refrigerant flow ratio of the two liquid branch pipes within the allowable range of the heat exchange tube diameter of the heat exchanger to be 2:1-7:1, or even more Large-scale refrigerant distribution requirements, such as 2:1, 3:1, 4:1, 5:1, 6:1, 7:1. In the refrigerant distribution scheme that achieves a larger flow rate ratio provided by the embodiments of the present disclosure, the inner diameter of the second liquid branch pipe 252 does not need to be designed too thin, and the flow rate of the refrigerant in the first liquid branch pipe 251 can also be much larger than that of the second liquid branch pipe. The flow rate of the refrigerant in the branch pipe 252. Therefore, the refrigerant distribution scheme of the liquid separator provided by the embodiment of the present disclosure avoids the problem of excessive total pressure drop of the liquid distribution branch pipe and the heat exchanger when the refrigerant distribution of the two liquid distribution branch pipes is relatively large.

Optionally, the angle between the first plane where the axes of the first pipe section 241 and the second pipe section 242 of the confluence pipe 240 are located and the second plane where the axes of the two liquid branch pipes are located is greater than or equal to 50 degrees, and less than Or equal to 70 degrees. The difference of refrigerant flow in the first liquid branch pipe 251 and the second liquid branch pipe 252 is improved. Optionally, the inner diameter of the first liquid branch pipe 251 is greater than or equal to 5.1 mm and less than or equal to 6.1 mm; the inner diameter of the second liquid branch pipe 252 is greater than or equal to 3.1 mm and less than or equal to 3.7 mm. Optionally, the second pipe section 242 of the confluence pipe 240 is arranged obliquely to the side of the second liquid branch pipe 252 .

When the air conditioner is running in heating mode, when the heat exchanger is used as an evaporator, the heat exchanger can exert the most ideal heat exchange capacity in the following situations: when heating, it continuously absorbs the heat in the surrounding ambient air from the low-temperature liquid state, As the temperature rises and reaches the gas-liquid two-phase state, the temperature remains at the evaporation temperature at this time, but the phase transition from liquid to gas occurs continuously, and the liquid refrigerant becomes less and less, and the gas refrigerant becomes more and more. At the outlet of the heat exchange branch, all of them just turn into a gaseous state and the temperature is 1-2°C higher than the evaporation temperature. This is because when the outlet temperature of the heat exchange branch is overheated, all of them are gaseous refrigerants, and the gaseous refrigerant has a small enthalpy difference and low heat transfer capacity, and when the superheat is too large, the heat transfer temperature difference between the refrigerant and the ambient temperature is small, such as when the evaporation temperature When the temperature is about 0-1°C, if the superheat is greater than 3°C, the temperature is above 4°C, and the ambient temperature in winter is only about 7°C, the heat transfer temperature difference is very small, and it is even more difficult to exert the heat transfer capacity of the heat exchanger.

The better the uniformity, the easier it is for each heat exchange branch to have a suitable heat exchange. If it is not uniform, it is easy for some branches to be overheated seriously, and the next few hairpin tubes have no heat exchange effect, while some heat exchange branches There is too much refrigerant in the circuit, and there is still a lot of low-temperature liquid refrigerant flowing through the entire heat exchange branch without exchanging the cooling capacity. In this way, under the same refrigerant flow rate, the heat exchange effect of the entire heat exchanger is poor, and the capacity of the air conditioner is very low. . Therefore, the empirical judging method for good shunting during heating is: the temperature difference at the outlet of each branch is within 2°C, and the outlet superheat is about 1°C. In this case, shunting is better.

Table 19

Table 20

Optionally, when the air conditioner is running in heating mode, the heat exchanger is used as an evaporator, and the first heat exchange branch, the second heat exchange branch and the third heat exchange branch are connected in parallel with the first liquid separation When the branch pipes 251 are connected, and the fourth heat exchange branch is connected with the second liquid distribution branch pipe 252, as shown in FIG. Among them, Table 19 shows that when the angle between the first plane and the second plane is 90 degrees, under the different inner diameters of the first liquid branch pipe 251 and the second liquid branch pipe 252, the maximum heat exchange branch of the fourth heat exchange branch and the first three branches temperature difference and the heating capacity of the air conditioner. As can be seen from the data in Table 19, when the inner diameter of the first liquid branch pipe 251 is 5.6mm, and when the inner diameter of the second liquid branch pipe 252 is 3.36mm, the fourth heat exchange branch of the heat exchanger is the same as the first three The maximum temperature difference of the branch is the smallest, which is 3.4°C, and the heating capacity of the air conditioner is the largest, which is 4855.2W under this inner diameter. Table 20 shows that when the inner diameter of the first liquid branch pipe 251 is 5.6 mm, and the inner diameter of the second liquid branch pipe 252 is 3.36 mm, the angles between the first plane and the second plane are different angles, the fourth heat exchange branch The maximum temperature difference between the road and the first three branches and the heating capacity of the air conditioner. It can be seen from Table 20 that when the angle between the first plane and the second plane is 60 degrees, the maximum temperature difference between the fourth heat exchange branch and the first three branches is the smallest, which is 1.2°C. The heater has the largest heating capacity of 5016.1W.

It can be seen from the data in Table 19 and Table 20 that when the number of heat exchange branches connected with the first liquid branch pipe 251 in the heat exchanger is three, the heat exchange branch connected with the second liquid branch pipe 252 The number of branches is 1, such as the heat exchanger shown in Figure 3, the inner diameter of the first liquid branch pipe 251 is 5.6mm, the inner diameter of the second liquid branch pipe 252 is 3.36mm, and the first plane and the first plane When the angle between the two planes is 60 degrees, the maximum temperature difference between the fourth heat exchange branch and the first three branches is the smallest, and the heat exchange capacity uniformity of the refrigerant in each heat exchange branch is the best. Maximum heat capacity. That is, the ratio of the amount of refrigerant in the first branch liquid pipe 251 to the amount of refrigerant in the second branch liquid pipe 252 is 3:1.

Similarly, the angle between the first plane and the second plane is greater than or equal to 50 degrees and less than or equal to 70 degrees, and the inner diameter of the first liquid branch pipe 251 is greater than or equal to 5.1 mm and less than or equal to 6.1 mm. When the inner diameter of the second liquid branch pipe 252 is greater than or equal to 3.1 mm and less than or equal to 3.7 mm, the ratio of the amount of refrigerant in the first liquid branch pipe 251 to that in the second liquid branch pipe 252 can be preferably 3 :1. The temperature difference achieved by other inner diameters and included angles and the heating capacity of the air conditioner in this embodiment are similar to the data in Table 2 and Table 3, and will not be repeated here.

Similarly, the angle between the first plane and the second plane is greater than or equal to 50 degrees and less than or equal to 70 degrees, and the inner diameter of the first liquid branch pipe 251 is greater than or equal to 5.1 mm and less than or equal to 6.1 mm. When the inner diameter of the second liquid branch pipe 252 is greater than or equal to 3.1mm and less than or equal to 3.7mm, the ratio of the amount of refrigerant in the first liquid branch pipe 251 to that in the second liquid branch pipe 252 can also be preferably 2. :1. The temperature difference achieved by other inner diameters and included angles and the heating capacity of the air conditioner in this embodiment are similar to the data in Table 2 and Table 3, and will not be repeated here. Optionally, the angle between the first plane and the second plane is greater than or equal to 50 degrees and less than or equal to 70 degrees, and the inner diameter of the first liquid branch pipe 251 is greater than or equal to 5.1 mm and less than or equal to 6.1 mm, When the inner diameter of the second liquid branch pipe 252 is greater than or equal to 3.1 mm and less than or equal to 3.7 mm, the ratio of the amount of refrigerant in the first liquid branch pipe 251 to that in the second liquid branch pipe 252 can be preferably 2 :1-3:1.

Optionally, the angle between the first plane and the second plane is greater than or equal to 30 degrees and less than or equal to 60 degrees, the inner diameter of the first liquid branch pipe 251 is greater than or equal to 5.1 mm and less than or equal to 6.1 mm, the second branch The inner diameter of the liquid branch pipe 252 is greater than or equal to 3.1 mm and less than or equal to 3.7 mm. Optionally, the second pipe section 242 of the confluence pipe 240 is arranged obliquely to the side of the second liquid branch pipe 252 .

Table 21

Table 22

Optionally, when the air conditioner is running in heating mode, the heat exchanger is used as an evaporator, and the first heat exchange branch, the second heat exchange branch, the third heat exchange branch, and the fourth heat exchange branch are connected in parallel When the branch and the fifth heat exchange branch are connected to the first liquid branch pipe 251, and the sixth heat exchange branch is connected to the second liquid branch pipe 252, the refrigerant temperature at the outlet of each heat exchange branch is shown in Table 21 and Table 22. Among them, Table 21 shows that when the included angle between the first plane and the second plane is 90 degrees, under different inner diameters of the first liquid branch pipe 251 and the second liquid branch pipe 252, the maximum heat exchange branch of the sixth heat exchange branch and the first five branches temperature difference and the heating capacity of the air conditioner. As can be seen from the data in Table 21, when the inner diameter of the first liquid branch pipe 251 is 5.6 mm, and when the inner diameter of the second liquid branch pipe 252 is 3.36 mm, the sixth heat exchange branch of the heat exchanger is the same as the first five The maximum temperature difference of the branch circuit is the smallest, which is 3.1℃, and the heating capacity of the air conditioner is the largest, which is 7287.6W under this inner diameter. Table 22 shows that when the inner diameter of the first liquid branch pipe 251 is 5.6 mm, and the inner diameter of the second liquid branch pipe 252 is 3.36 mm, the angle between the first plane and the second plane is different, and the sixth heat exchange branch The maximum temperature difference between the road and the first five branches and the heating capacity of the air conditioner. It can be seen from Table 22 that when the angle between the first plane and the second plane is 45 degrees, the maximum temperature difference between the sixth heat exchange branch and the first five branches is the smallest, which is 1.0°C. The heater has the largest heating capacity of 7383.7W.

It can be seen from the data in Table 21 and Table 22 that when the number of heat exchange branches connected with the first liquid branch pipe 251 in the heat exchanger is five, the heat exchange branch connected with the second liquid branch pipe 252 The number of branches is 1, the inner diameter of the first branch pipe 251 is 5.6 mm, the inner diameter of the second branch pipe 252 is 3.36 mm, and the angle between the first plane and the second plane is 45 degrees , the maximum temperature difference between the sixth heat exchange branch and the first five branches is the smallest, the heat transfer capacity uniformity of the refrigerant in each heat exchange branch is the best, and the heating capacity of the air conditioner is the largest. That is, the ratio of the amount of refrigerant in the first branch liquid pipe 251 to the amount of refrigerant in the second branch liquid pipe 252 is 5:1.

Similarly, the angle between the first plane and the second plane is greater than or equal to 30 degrees and less than or equal to 60 degrees, and the inner diameter of the first liquid branch pipe 251 is greater than or equal to 5.1 mm and less than or equal to 6.1 mm. When the inner diameter of the second liquid branch pipe 252 is greater than or equal to 3.1 mm and less than or equal to 3.7 mm, the ratio of the amount of refrigerant in the first liquid branch pipe 251 to that in the second liquid branch pipe 252 can be preferably 5 :1. The temperature difference achieved by other inner diameters and included angles and the heating capacity of the air conditioner in this embodiment are similar to the data in Table 21 and Table 22, and will not be repeated here.

Similarly, the angle between the first plane and the second plane is greater than or equal to 30 degrees and less than or equal to 60 degrees, and the inner diameter of the first liquid branch pipe 251 is greater than or equal to 5.1 mm and less than or equal to 6.1 mm. When the inner diameter of the second liquid branch pipe 252 is greater than or equal to 3.1 mm and less than or equal to 3.7 mm, the ratio of the amount of refrigerant in the first liquid branch pipe 251 to that in the second liquid branch pipe 252 can also be preferably 4 :1. The temperature difference achieved by other inner diameters and included angles and the heating capacity of the air conditioner in this embodiment are similar to the data in Table 21 and Table 22, and will not be repeated here. Optionally, the angle between the first plane and the second plane is greater than or equal to 30 degrees and less than or equal to 60 degrees, and the inner diameter of the first liquid branch pipe 251 is greater than or equal to 5.1 mm and less than or equal to 6.1 mm, When the inner diameter of the second liquid branch pipe 252 is greater than or equal to 3.1mm and less than or equal to 3.7mm, the ratio of the amount of refrigerant in the first liquid branch pipe 251 to that in the second liquid branch pipe 252 can be preferably 4 :1-5:1.

Optionally, the angle between the first plane and the second plane is less than or equal to 10 degrees, the inner diameter of the first liquid branch pipe 251 is greater than or equal to 7.1 mm and less than or equal to 8.1 mm, and the inner diameter of the second liquid branch pipe 252 is greater than or equal to Or equal to 3.1mm, and less than or equal to 3.7mm. Optionally, the second pipe section 242 of the confluence pipe 240 is arranged obliquely to the side of the second liquid branch pipe 252 .

Table 23

Table 24

Optionally, when the air conditioner is running in heating mode, the heat exchanger is used as an evaporator, and the first heat exchange branch, the second heat exchange branch, the third heat exchange branch, and the fourth heat exchange branch are connected in parallel Branch, the fifth heat exchange branch and the sixth heat exchange branch are connected with the first liquid branch pipe 251, and when the seventh heat exchange branch is connected with the second liquid branch pipe 252, the outlets of each heat exchange branch The refrigerant temperature at the location is shown in Table 23 and Table 24. Among them, Table 23 shows that when the angle between the first plane and the second plane is 90 degrees, under the different inner diameters of the first liquid branch pipe 251 and the second liquid branch pipe 252, the maximum heat exchange branch of the seventh heat exchange branch and the first six branches temperature difference and the heating capacity of the air conditioner. As can be seen from the data in Table 23, when the inner diameter of the first liquid branch pipe 251 is 7.6mm, and when the inner diameter of the second liquid branch pipe 252 is 3.36mm, the seventh heat exchange branch of the heat exchanger and the first six The maximum temperature difference of the branch circuit is the smallest, which is 5.9℃, and the heating capacity of the air conditioner is the largest, which is 9268.4W under this inner diameter. Table 24 shows that when the inner diameter of the first liquid branch pipe 251 is 7.6mm, and the inner diameter of the second liquid branch pipe 252 is 3.36mm, the angle between the first plane and the second plane is different, and the seventh heat exchange branch The maximum temperature difference between the road and the first six branches and the heating capacity of the air conditioner. It can be seen from Table 24 that when the angle between the first plane and the second plane is 0 degrees, the maximum temperature difference between the seventh heat exchange branch and the first six branches is the smallest, which is 1.5°C. The heater has the largest heating capacity of 9544.5W.

It can be seen from the data in Table 23 and Table 24 that when the number of heat exchange branches connected with the first liquid branch pipe 251 in the heat exchanger is 6, the heat exchange branch connected with the second liquid branch pipe 252 The number of branches is 1, the inner diameter of the first branch pipe 251 is 7.6 mm, the inner diameter of the second branch pipe 252 is 3.36 mm, and the angle between the first plane and the second plane is 0 degrees , the maximum temperature difference between the seventh heat exchange branch and the first six branches is the smallest, the heat exchange capacity uniformity of the refrigerant in each heat exchange branch is the best, and the heating capacity of the air conditioner is the largest. That is, the ratio of the amount of refrigerant in the first branch liquid pipe 251 to the amount of refrigerant in the second branch liquid pipe 252 is 6:1.

Similarly, the angle between the first plane and the second plane is less than or equal to 10 degrees, the inner diameter of the first liquid branch pipe 251 is greater than or equal to 7.1 mm, and less than or equal to 8.1 mm, and the inner diameter of the second liquid branch pipe 252 is When it is greater than or equal to 3.1 mm and less than or equal to 3.7 mm, the ratio of the amount of refrigerant in the first liquid branch pipe 251 to that in the second liquid branch pipe 252 can be preferably 6:1. The temperature difference achieved by other inner diameters and included angles in this embodiment and the heating capacity of the air conditioner are similar to the data in Table 23 and Table 24, and will not be repeated here.

Similarly, the angle between the first plane and the second plane is less than or equal to 10 degrees, the inner diameter of the first liquid branch pipe 251 is greater than or equal to 7.1 mm, and less than or equal to 8.1 mm, and the inner diameter of the second liquid branch pipe 252 is When it is greater than or equal to 3.1 mm and less than or equal to 3.7 mm, the ratio of the amount of refrigerant in the first branch liquid pipe 251 to the amount of refrigerant in the second liquid branch pipe 252 can be preferably 7:1. The temperature difference achieved by other inner diameters and included angles in this embodiment and the heating capacity of the air conditioner are similar to the data in Table 23 and Table 24, and will not be repeated here. Optionally, the angle between the first plane and the second plane is less than or equal to 10 degrees, the inner diameter of the first liquid branch pipe 251 is greater than or equal to 7.1 mm and less than or equal to 8.1 mm, and the inner diameter of the second liquid branch pipe 252 is When the inner diameter is greater than or equal to 3.1mm and less than or equal to 3.7mm, the ratio of the amount of refrigerant in the first liquid branch pipe 251 to that in the second liquid branch pipe 252 can be preferably 6:1-7:1.

Optionally, the first plane is coplanar with the second plane. The first plane and the second plane are coplanar, and it can be understood that the angle between the first plane and the second plane is 0 degree. Optionally, the inner diameter of the first liquid branch pipe 251 is larger than the inner diameter of the second liquid branch pipe 252, and the second pipe section 242 of the confluence pipe 240 is inclined to the second liquid branch pipe 252, so that more refrigerant is The flow down to the first liquid branch pipe 251 increases the flow difference of the refrigerant in the first liquid branch pipe 251 and the second liquid branch pipe 252 .

Optionally, the inner diameter of the first liquid branch pipe 251 is larger than the inner diameter of the second liquid branch pipe 252 . The inner diameter of the first liquid branch pipe 251 is larger than the inner diameter of the second liquid branch pipe 252, so that the refrigerant is unevenly distributed in the liquid separator, and the amount of refrigerant flowing into the first liquid branch pipe 251 is greater than that of the second liquid branch pipe 252. Refrigerant volume.

Optionally, the second pipe section 242 is disposed toward the side of the second liquid branch pipe 252 . The second pipe section 242 of the confluence pipe 240 is disposed toward the side of the second liquid branch pipe 252 . Optionally, the inner diameter of the second liquid branch pipe 252 is smaller than the inner diameter of the first liquid branch pipe 251 . The flow difference of the refrigerant in the first branch pipe 251 and the branch pipe 252 is further increased by the inner diameter difference of the two branch pipes and the biased arrangement of the second pipe section 242 .

Optionally, the length of the first pipe segment 241 is less than or equal to 10 cm. Optionally, the length of the first pipe segment 241 is 3cm, 4cm, 5cm, 6cm, 7cm, 8cm or 9cm, etc. When the length of the first pipe section 241 is small, the refrigerant entering the first pipe section 241 from the second pipe section 242 tends to be biased towards the first liquid distribution port due to centrifugal force, which in turn helps to realize that the liquid distribution of the first liquid distribution port is larger than that of the first liquid distribution port. The liquid volume requirement of the second liquid port. If the length of the first pipe section 241 is greater than 10 cm, then because the flow distance is too long, the tendency of the refrigerant in the above to be biased towards the first liquid distribution port due to centrifugal force is weakened or even disappears, which is not conducive to realizing the liquid distribution of the first liquid distribution port greater than 10 cm. The liquid volume requirement of the second liquid port.

Optionally, the length of the first pipe segment 241 is less than or equal to 5 cm. Optionally, the length of the first pipe section 241 may be 2cm, 2.5cm, 3cm, 3.5cm, 4cm, 4.2cm, 4.5cm or 5cm and so on. When the length of the first pipe section 241 is less than or equal to 5 cm, the tendency of the refrigerant entering the first pipe section 241 from the second pipe section 242 to the first liquid distribution port due to centrifugal force is more obvious, which is more helpful to realize the first liquid distribution port. The dispensing volume of the second dispensing port is greater than the requirement of the dispensing volume of the second dispensing port.

Optionally, the inner diameter of the second liquid branch pipe 252 is greater than or equal to 3mm. Optionally, the inner diameter of the second liquid branch pipe 252 is 3mm, 3.36mm, 5mm, 10mm, 12mm and so on. As mentioned above, the inner diameter of the liquid branch pipe has a minimum limit. For example, the inner diameter of the liquid branch pipe cannot be lower than 3mm, or even 3.36mm. The copper tube with a lower diameter has actually become a capillary, and the capillary has a larger The flow resistance will form a throttling and pressure-reducing effect on the flow of refrigerant, which will increase the power of the compressor and reduce the performance of the system; it will even cause serious frosting on the outdoor heat exchanger when the air conditioner is running in heating mode, which will affect the performance of the system. Safety and reliability. In the embodiment of the present disclosure, the inner diameter of the second liquid branch pipe 252 is greater than or equal to 3 mm, which reduces the flow resistance of the refrigerant in the second liquid branch pipe 252 and improves the performance of the air conditioning system.

Optionally, the ratio of the cross-sectional area of the first liquid branch pipe 251 to the cross-sectional area of the second liquid branch pipe 252 is less than or equal to x. Wherein, x is a preset value. Optionally, x may be determined according to the number of heat exchange branch pipes respectively communicating with the first liquid branch pipe 251 and the second liquid branch pipe 252 .

Optionally, the value range of x is: 1.3≤x≤1.7. Optionally, the value of x may be 1.4, 1.5, 1.6 or 1.7, etc. Optionally, the ratio of the number of heat exchange branches communicating with the first liquid branch pipe 251 and the second liquid branch pipe 252 is less than 2. Optionally, the number of heat exchange branches communicated with the first liquid branch pipe 251 is 3, and the number of heat exchange branches communicated with the second liquid branch pipe 252 is 2; 251 communicates with the number of heat exchange branches is 4, and the number of heat exchange branches communicated with the second liquid branch pipe 252 is 3; optionally, the number of heat exchange branches communicated with the first liquid branch pipe 251 is 5. The number of heat exchange branches communicated with the second liquid branch pipe 252 is 4; optionally, the number of heat exchange branches communicated with the first liquid branch pipe 251 is 5, and the number of heat exchange branches communicated with the second liquid branch pipe 252 The number of heat transfer branches is 3, etc.

Optionally, the ratio of the cross-sectional area of the first liquid branch pipe 251 to the cross-sectional area of the second liquid branch pipe 252 is greater than x. Wherein, x is a preset value. Optionally, the value range of x is: 1.3≤x≤1.7. Optionally, the value of x may be 1.4, 1.5, 1.6, or 1.7, etc. Optionally, the ratio of the number of heat exchange branch pipes communicating with the first liquid branch pipe 251 and the second liquid branch pipe 252 is greater than or equal to 2. For example, the ratio of the number of heat exchange branch pipes communicated with the first liquid branch pipe 251 and the second liquid branch pipe 252 is 2:1-7:1, such as 2:1, 3:1, 4:1, 5 :1, 6:1 or 7:1 etc.

Optionally, the ratio of the cross-sectional area of the first liquid branch pipe 251 to the cross-sectional area of the second liquid branch pipe 252 is less than or equal to y. Wherein, y is a preset value greater than x.

Optionally, the value range of y is: 2≤y≤15. Optionally, the value of y may be 2, 3, 4, 9, 10, 11, 12, 14 or 15, etc. Optionally, the ratio of the number of heat exchange branch pipes communicating with the first liquid branch pipe 251 and the second liquid branch pipe 252 is greater than or equal to 2. For example, the ratio of the number of heat exchange branch pipes communicated with the first liquid branch pipe 251 and the second liquid branch pipe 252 is 2:1-7:1, such as 2:1, 3:1, 4:1, 5 :1, 6:1 or 7:1 etc. Optionally, as mentioned above, the minimum inner diameter of the two liquid branch pipes should not be less than 3 mm, or even 3.36 mm, and the inner diameter of the copper tube used in the heat exchanger of the air conditioner is generally not more than 10.6 mm. Optionally, in order to better prepare the liquid distributor, the ratio of the cross-sectional area of the first liquid branch pipe 251 to the cross-sectional area of the second liquid branch pipe 252 is less than or equal to 2.

Optionally, the value range of y is: 10≤y≤12. Optionally, the value of y may be 10, 11 or 12, etc.

Optionally, the first pipe section 241 is arranged to be biased toward the side of the second liquid branch pipe 252 .

Optionally, the angle α between the first pipe section 241 and the shell is 30-75 degrees. Optionally, the angle α between the first pipe section 241 and the shell is 30 degrees, 35 degrees, 40 degrees, 45 degrees, 50 degrees, 60 degrees, 70 degrees or 75 degrees. When the included angle between the first pipe section 241 and the shell is 50 degrees, the simulation effect diagram of refrigerant flowing in the liquid separator is shown in FIG. 22 . It can be seen from FIG. 22 that when the angle between the first pipe section 241 and the shell is 50 degrees, the amount of refrigerant flowing into the first liquid branch pipe 251 is much larger than the amount of refrigerant flowing into the second liquid branch pipe 252. The non-uniform distribution between the first branch pipe 251 and the second branch pipe 252 works better. When the included angle between the first pipe section 241 and the housing is 80 degrees, the simulation effect diagram of refrigerant flowing in the liquid separator is shown in FIG. 23 . It can be seen from Fig. 23 that when the angle between the first pipe section 241 and the shell is 80 degrees, the amount of refrigerant flowing into the first liquid branch pipe 251 and the amount of refrigerant flowing into the second liquid branch pipe 252 have little difference .

Optionally, the angle α between the first pipe section 241 and the housing is 45-60 degrees. As shown in Figure 14. Optionally, the angle α between the first pipe section 241 and the shell is 45 degrees, 50 degrees, 55 degrees or 60 degrees.

Optionally, the inner diameter of the manifold 240 is greater than the inner diameter of the first liquid branch pipe 251 . As shown in Figure 15. Optionally, the inner diameter of the confluence pipe 240 is greater than the inner diameter of the first liquid branch pipe 251 , and the inner diameter of the first liquid branch pipe 251 is larger than the inner diameter of the second liquid branch pipe 252 .

Optionally, a first area where the first branch cavity 235 communicates with the confluence cavity 234 is greater than a second area where the second branch cavity 236 communicates with the confluence cavity 234 . In this way, more refrigerant can flow into the first liquid branch pipe 251 through the first branch chamber 235 , which increases the difference in the amount of refrigerant flowing into the two liquid branch pipes.

Optionally, the ratio of the first area to the second area is less than or equal to z. Among them, z is a preset value.

Optionally, the value range of z is: 2≤z≤15. Optionally, the value of z may be 2, 3, 5, 8, 9, 10 or 12, etc. Optionally, the ratio of the number of heat exchange branch pipes communicating with the first liquid branch pipe 251 and the second liquid branch pipe 252 is greater than or equal to 2. For example, the ratio of the number of heat exchange branch pipes communicated with the first liquid branch pipe 251 and the second liquid branch pipe 252 is 2:1-7:1, such as 2:1, 3:1, 4:1, 5 :1, 6:1 or 7:1 etc. Optionally, as mentioned above, the minimum inner diameter of the two liquid branch pipes should not be less than 3mm, or even 3.36mm, and the inner diameter of the copper tube used in the heat exchanger of the air conditioner is generally not more than 10.6mm. Optionally, in order to better prepare the liquid distributor, the ratio of the cross-sectional area of the first liquid branch pipe 251 to the cross-sectional area of the second liquid branch pipe 252 is less than or equal to 2.

Optionally, the value range of z is: 10≤z≤12. Optionally, the value of z may be 10, 11 or 12, etc.

Optionally, the communication area between the manifold 240 and the first branch cavity 235 is larger than the communication area between the manifold 240 and the second branch cavity 236 . In this way, more refrigerant can flow into the first liquid branch pipe 251 through the first branch chamber 235 , which increases the difference in the amount of refrigerant flowing into the two liquid branch pipes.

Optionally, the cross section of the manifold 240 includes a straight line segment. The cross-section of the manifold 240 includes one or more straight sections, and optionally, the straight sections are arranged at a place communicating with the second branch cavity 236 .

Optionally, the manifold 240 is a D-shaped pipe or a triangular pipe, as shown in FIG. 20 . Optionally, the straight section of the D-shaped tube is arranged at the place communicating with the second branch cavity 236 .

Optionally, the confluence pipe 240 is provided with a flow blocking portion towards the inner side of the second branch cavity 236 . The setting of the flow blocking part blocks the flow of the refrigerant into the second branch chamber 236 , thereby reducing the amount of refrigerant flowing into the second liquid branch pipe 252 .

Optionally, the axis of the first liquid branch pipe 251 is not parallel to the centerline of the liquid chamber. It can be understood that the first liquid branch pipe 251 deviates to one side, which reduces the flow of refrigerant into the first liquid branch pipe 251 .

Optionally, the axis of the second liquid branch pipe 252 is not parallel to the centerline of the liquid chamber. It can be understood that the second liquid branch pipe 252 deviates to one side, which reduces the refrigerant flow into the second liquid branch pipe 252 , as shown in FIG. 18 .

Optionally, the axis of the first liquid branch pipe 251 forms a first angle with the center line of the liquid separation chamber, the axis of the second liquid branch pipe 252 forms a second angle with the center line of the liquid separation chamber, and the first angle The angles are not equal to the second included angle. The first included angle is not equal to the second included angle, so that the amount of refrigerant flowing to the first liquid branch pipe 251 and the second liquid branch branch pipe 252 is different.

Optionally, the length of the first liquid distribution branch pipe 251 extending into the liquid separation chamber is shorter than the length of the second liquid distribution branch pipe 252 extending into the liquid separation chamber. As shown in Figure 19. The part of the second branch pipe 252 protruding into the liquid chamber is longer, and the amount of refrigerant flowing into the second branch pipe 252 is reduced, so that the refrigerant flows to the first branch pipe 251 and the second branch pipe 252. different. The flow distribution diagram of the refrigerant in the first liquid branch pipe 251 and the second liquid branch pipe 252 is shown in FIG. 24 .

Optionally, the axis of the manifold 240 is offset from the centerline of the housing. In this way, the confluence pipe 240 is disposed on one side of the shell, so that the flow rates of the refrigerant flowing into the first liquid branch pipe 251 and the second liquid branch pipe 252 are different.

Optionally, the first axis of the manifold 240 is between the second axis of the first liquid branch pipe 251 and the third axis of the second liquid branch pipe 252 . The first axis is between the second axis and the third axis, so that the refrigerant in the manifold 240 can be distributed to the first liquid branch pipe 251 and the second liquid branch pipe 252 at the same time.

Optionally, the first axis, the second axis and the third axis are on the same plane. In this way, the accuracy of the distribution ratio of the refrigerant to the first liquid branch pipe 251 and the second liquid branch pipe 252 is improved.

Optionally, the inner diameter of the first liquid branch pipe 251 is larger than the inner diameter of the second liquid branch pipe 252 . Wherein, the axis of the confluence pipe 240 deviates to the side of the first liquid branch pipe 251 . In this way, the flow rate of the refrigerant flowing into the first liquid branch pipe 251 is greater than the refrigerant flow rate in the second liquid branch pipe 252 .

Optionally, the liquid separator is arranged at the first refrigerant inlet and outlet 111, the confluence pipe 240 of the liquid separator communicates with the first refrigerant inlet and outlet 111, and the number of heat exchange branches communicated by the first liquid branch pipe 251 is the same as that of the second The number of heat exchange branches connected by the liquid branch pipe 252 is different.

Optionally, the number of heat exchange branches communicated with the first liquid branch pipe 251 is greater than the number of heat exchange branches communicated with the second liquid branch pipe 252; or, the number of heat exchange branches communicated with the first liquid branch pipe The ratio of the number to the number of heat exchange branch pipes connected to the second liquid branch pipe is greater than 1 and less than 2; or, the number of heat exchange branch pipes connected to the first liquid branch pipe and the heat exchange branch pipe connected to the second liquid branch pipe The ratio of the number of branch pipes is greater than or equal to 2.

Optionally, the number of heat exchange branches communicating with the first liquid branch pipe 251 of the first liquid distributor 211 is greater than or equal to two. The number of heat exchange branches communicating with the second liquid branch pipe 252 of the first liquid distributor 211 is 1, 2 or 3.

Optionally, as shown in FIG. 3, the heat exchanger includes a first heat exchange branch 121, a second heat exchange branch 122, a fourth heat exchange branch 124, a first bypass pipeline 151 and a first one-way Valve 311. One end of the first heat exchange branch 121 is connected with the second liquid separator 212; one end of the second heat exchange branch 122 is connected with the second liquid separator 212; one end of the fourth heat exchange branch 124 is connected with the first liquid separator. Device 211 is connected; the first bypass line 151 connects the first liquid distributor 211 and the second liquid distributor 212, the first check valve 311 is arranged on the first bypass line 151, and the first check valve 311 The conduction direction is defined as flowing from the first liquid distributor 211 to the second liquid distributor 212 .

Optionally, the heat exchanger includes a gas collector, a first heat exchange branch 121 , a second heat exchange branch 122 , a third heat exchange branch 123 , a fourth heat exchange branch 124 , and a first bypass pipeline 151 , the second bypass line 152 , the first one-way valve 311 and the second one-way valve 312 . The first end of the first heat exchange branch 121 is connected to the first nozzle of the gas collector, and the second end is connected to the second liquid separator 212; the first end of the second heat exchange branch 122 is connected to the second nozzle of the gas collector. The nozzle is connected, and the second end is connected with the second liquid distributor 212; the first end of the third heat exchange branch 123 is connected with the third liquid distributor 213, and the second end is connected with the first liquid distributor 211; the fourth The first end of the heat exchange branch 124 is connected to the third liquid separator 213, and the second end is connected to the first liquid separator 211; the first bypass line 151 is connected to the first liquid separator 211 and the second liquid separator 212; the second bypass pipeline 152 is connected to the third liquid separator 213 and the gas collector; the first check valve 311 is arranged on the first bypass pipeline 151, and the conduction direction of the first check valve 311 is limited to from The first liquid distributor 211 flows to the second liquid distributor 212; the second one-way valve 312 is arranged in the second bypass pipeline 152, and the conduction direction of the second one-way valve 312 is limited to from the third liquid distributor 213 flows to the gas header.

Optionally, the cooling flow is downward, and the flow path of the refrigerant in the heat exchanger is as follows: the refrigerant enters through the collector pipe and is divided into two paths, the first path flows through the first heat exchange branch 121, and the second path flows through the second heat exchange branch 121. The heat exchange branch 122, the two paths converge at the second liquid separator 212, flow through the third heat exchange branch 123, pass through the third liquid separator 213, flow through the fourth heat exchange branch 124, and then flow out of the heat exchanger . It can be seen that, in the heat exchanger provided by the embodiment of the present disclosure, when the cooling flow is downward, due to the setting of the first one-way valve 311 and the second one-way valve 312, the length of the refrigerant path in the downward flow of the cooling flow is increased, and the heat exchange of the refrigerant is extended. The heat exchange time in the device enables the refrigerant to fully exchange heat with the surrounding environment, and the refrigerant flows through fewer shunts and a faster flow rate, which improves the heat exchange effect of the heat exchanger, thereby improving the cooling efficiency of the air conditioner .

Optionally, in the downward direction of the heating flow, the refrigerant is split into four paths. The first branch path passes through the first one-way valve 311 and the second liquid distributor 212, flows through the first heat exchange branch 121, and flows out after passing through the gas collector. ; The second branch passes through the first one-way valve 311, the second liquid distributor 212, flows through the second heat exchange branch 122, and flows out after the gas collecting pipe; the third branch passes through the first one-way valve 311, the second The liquid separator 212 flows through the third heat exchange branch 123, and then flows out after passing through the third liquid separator 213, the second one-way valve 312, and the gas collecting pipe; the fourth branch flows through the fourth heat exchange branch 124, and passes through the The third liquid separator 213, the second one-way valve 312, and the gas collector flow out. It can be seen that in the heat exchanger provided by the embodiment of the present disclosure, due to the setting of the first one-way valve 311 and the second one-way valve 312, the first heat exchange branch 121, the second heat exchange branch 122 and the third heat exchange branch 123 It is connected in parallel with the fourth heat exchange branch 124. At this time, the refrigerant flows through more branches, which avoids the pressure loss problem caused by too long flow path, improves the heat exchange efficiency of the heat exchanger, and thus improves the performance of the air conditioner. Heating efficiency.

Optionally, the number of heat exchange branches communicating with the first liquid branch pipe 251 of the first liquid distributor 211 is 2, 3 or 4. The number of heat exchange branches communicating with the second liquid branch pipe 252 of the first liquid distributor 211 is 1, 2 or 3. Optionally, the ratio of the number of heat exchange branches communicating with the first liquid branch pipe 251 and the second liquid branch pipe 252 of the first liquid distributor 211 is less than 2.

Considering that the liquid branch pipe of the liquid separator needs to have a certain insertion depth, and at the same time, there must be a certain distance between the liquid branch pipe and the shell wall of the liquid separator so as not to hinder the flow of refrigerant; Bend 180° and then flow out from other liquid branch pipes. At this time, it is necessary to ensure that the refrigerant circulation in the liquid distribution chamber is not affected by the bottom of the chamber, so the height of the liquid separator should not be too small. The corresponding diameter of the liquid separator is too large, and it is difficult to arrange the pipeline space of the outdoor unit. The limiting conditions of the two determine that the lower limit of the length-to-diameter ratio of the liquid separator cannot be too small. Therefore, as shown in FIG. 25 , optionally, the length-to-diameter ratio L1/D≥a1 of the liquid separation chamber 230 , where a1 is the first preset ratio value.

Optionally, the value range of a1 is 0.3-0.8.

For the liquid separator in the embodiment of the present disclosure, on the one hand, the liquid branch pipe needs to be inserted into the liquid separator to a certain depth, and the specific depth depends on the actual size of the liquid separator; take the model with a rated cooling capacity of 3.5KW in the embodiment as an example , the insertion depth is generally at least 0.2R; on the other hand, under refrigeration conditions, the refrigerant flows in from the liquid branch pipe, bends 180° and then flows out from the last liquid branch pipe, and the lower end of the liquid branch pipe reaches the liquid chamber The bottom needs to meet a certain length, generally at least about 1R, and the length-to-diameter ratio is at least about 1.2R. At the same time, considering that there may be some differences between units with different capacities and different types of refrigerants, the lower limit of L/D is 0.3 ~0.8.

In this example, the performance data of the liquid separator limited by the lower limit of the aspect ratio above and the liquid separator exceeding the lower limit of the aspect ratio were tested separately in the form of three-way split flow. The test condition was the indoor working condition of 27°C. /19°C, outdoor working condition 35°C/24°C, other operating conditions of the air conditioner are the same, the test data are shown in Table 25 below:

Table 25

长径比aspect ratio	能力ability	功率power	能效efficiency
0.20.2	3379.8W3379.8W	888.7W888.7W	3.803.80
0.50.5	3436.3W3436.3W	863.7W863.7W	3.983.98

It can be seen from the above table that when the aspect ratio is less than the minimum value of the lower limit of 0.3, the air conditioner has lower energy efficiency when the power is higher, and when the aspect ratio is greater than the minimum value of the lower limit of 0.3 The air conditioner can achieve better energy efficiency in operation.

The lower limit of the length-to-diameter ratio of the liquid separator cavity defined in this embodiment can avoid the problem of excessive accumulation of refrigerant inside the liquid separator and affect the refrigerant circulation of the air conditioner, and can effectively reduce power loss at the same time.

Optionally, the length L1 of the liquid separation cavity 230 ≥ b1, where b1 is the first length threshold.

Optionally, the value range of b1 is 1.4-2 cm.

Optionally, the diameter D of the liquid separator is 1.7-7 cm.

In some other embodiments, the space reserved for the height of the liquid separator is usually within 10cm, and the diameter of the liquid separator is generally more than 2cm. Therefore, the limiting conditions of the two determine that the aspect ratio of the liquid separator is generally within 5; in addition, In order to achieve liquid storage, our liquid separator must have a certain volume. According to the same height, the more slender the liquid separator, the smaller the volume. There is another influencing factor. When the liquid separator is too slender, each branch nozzle The distance is very close, and it is easy to interact with each other and finally affect the diversion. In a long and thin space, the refrigerant flows in from above and then flows out from above. This flow process will also be affected by different directions.

When the heat exchanger is used as a condenser, the liquid separator needs to play a liquid storage function. When the height of the liquid separator is constant, the larger the aspect ratio, the smaller the diameter of the liquid separator, the smaller the volume of the liquid separation chamber, and the liquid storage capacity. The less; the larger the length-to-diameter ratio, the more slender the liquid distributor and the closer the distance between the liquid distribution branches, which are easy to influence each other and affect the final shunt effect; at the same time, the refrigerant flows in from the liquid distribution branch pipe, bending 180° and then flow out from other liquid branch pipes. If the liquid distributor is too slender, the flow process will be affected by the side wall of the liquid separation chamber; when the diameter of the liquid distributor is constant, the larger the aspect ratio, the greater the distribution. The greater the height of the device, the larger the space occupied in the tube group, it is difficult to be compatible. Therefore, considering comprehensively, the upper limit a2 of the length-to-diameter ratio of the liquid separation chamber cannot be too large, and the length-to-diameter ratio L1/D of the liquid separation chamber 230 ≤ a2. a2 is a second preset ratio greater than a1.

Optionally, the value range of a2 is 1-3.

Another option,

that is

Optionally, the value range of a2 is 1-3.

Exemplarily, in this embodiment, the performance data of the liquid separator defined by the above-mentioned lower limit of the length-to-diameter ratio and the liquid distributor exceeding the lower limit of the length-to-diameter ratio were tested separately in the form of four-way split flow, and the test conditions were indoor The working condition is 27°C/19°C, the outdoor working condition is 35°C/24°C, and the other operating conditions of the air conditioner are the same. The test data are shown in Table 26 below:

Table 26

长径比aspect ratio	能力ability	功率power	能效efficiency
2.82.8	3421.6W3421.6W	865.1W865.1W	3.963.96
4.34.3	3387.1W3387.1W	905.7W905.7W	3.743.74

It can be seen from the above table that when the aspect ratio is greater than the maximum value of the upper limit 3, the air conditioner has lower energy efficiency when the power is higher, and when the aspect ratio is smaller than the maximum value of the upper limit 3 The air conditioner can achieve better energy efficiency in operation.

Optionally, the length L1 of the liquid separation cavity 230≤b2, wherein b2 is a second length threshold greater than b1.

Optionally, the value range of b2 is 5-6 cm.

Optionally, the diameter D of the liquid separator is 1.7-7 cm.

Optionally, as shown in FIGS. 26 to 28 , the liquid separation chamber 230 includes a first liquid storage chamber 231 connected to the confluence pipe 240 and a second liquid storage chamber 232 connected to the first liquid distribution port and the second liquid distribution port.

Optionally, the first liquid storage chamber 231 and the second liquid storage chamber 232 are connected through a liquid storage chamber channel 233 with a narrow diameter.

The beneficial effect of adopting the design of the above scheme is that: when the heat exchanger is used as a condenser, the refrigerant here is in a gas-liquid two-phase state and occupies a large volume, and the second liquid storage chamber of the liquid separator has both confluence and diversion It is beneficial for the refrigerant to turn back at 180° and reduce pressure loss; the first liquid storage chamber is located below the second liquid storage chamber, and under the action of gravity, the liquid refrigerant gathers at the bottom to play a liquid storage effect. Narrow, reducing the impact of the refrigerant in the second liquid storage chamber, the state of the liquid refrigerant is stable, and can reduce the impact on the one-way valve connected to the first liquid distribution chamber, and the sealing is better; in the heat exchanger as the evaporation When the device is in use, the refrigerant flows in reverse, allowing more refrigerant to participate in the cycle to meet the refrigerant cycle requirements. At the same time, the first liquid storage chamber can also function as a muffler to eliminate refrigerant flow noise.

Optionally, the first liquid storage chamber 231 is greater than or equal to the volume of the second liquid storage chamber 232, which is conducive to storing more liquid refrigerant to increase the liquid storage capacity; at the same time, the first liquid storage chamber is set in a larger volume form, It can also improve the buffering effect on the flow of refrigerant, and use a larger cavity for noise reduction when used as a "muffler".

Optionally, the volume of the first liquid storage chamber 231 is v1=c1*Q, wherein v1 is the volume of the first liquid storage chamber in cm ³ , and Q is the rated cooling capacity in kW.

Optionally, the value range of c1 is 3-10.

Optionally, the volume of the second liquid storage chamber 232 is v2=c2*Q, wherein v2 is the volume of the first liquid storage chamber in cm ³ , and Q is the rated cooling capacity in kW.

Optionally, the value range of c2 is 1.5-5.

In this embodiment, in the case of liquid storage in the liquid separator, the first liquid storage chamber 231 mainly accommodates liquid refrigerant, the density of which is relatively high, and the quality of the refrigerant stored in the same volume is relatively high; the second liquid storage chamber 232 It mainly accommodates gas-liquid mixed state refrigerant, whose refrigerant density is low, and the quality of the refrigerant stored under the same volume is low; in order to meet the capacity requirement of about 5% of the total filling volume for the liquid storage of the aforementioned liquid separator, according to the test When the air conditioner is running at different loads, the density of the refrigerants in the two liquid storage chambers changes, and the volume range ratios of the first liquid storage chamber and the second liquid storage chamber are set respectively, so as to use the first liquid storage chamber 231 to accommodate more The multi-quality refrigerant makes the sum of the refrigerant storage capacity of the first liquid storage chamber 231 and the second liquid storage chamber 232 meet the above capacity requirement.

Optionally, the liquid storage chamber channel 233 includes a circular pipe section, and the two ports of the circular pipe section are configured as tapered mouths whose caliber gradually expands outward. The smoother flow reduces the disturbance caused by the change of the flow area during the flow of the two.

Optionally, the length of the liquid storage cavity channel 233 is less than or equal to 10 mm.

Optionally, the pipe diameter of the liquid storage chamber channel 233 is greater than or equal to the pipe diameter of the manifold 240. In this embodiment, when the heat exchanger is used as an evaporator, the flow of refrigerant through the manifold and liquid separation can be reduced. In order to ensure the heat transfer performance of the heat exchanger, the flow resistance during the liquid separation process of the heat exchanger can be accelerated to speed up the flow of refrigerant.

Exemplarily, in this embodiment, taking an air conditioner with a rated cooling capacity of 7.2Kw as an example, the ordinary liquid separator and the liquid separator to be protected by this application were tested respectively. The performance data in this case, the test data comparison is shown in Table 27 below:

Table 27

From the above data, it can be seen that under the rated cooling condition, the air conditioner of the present application can achieve a higher energy efficiency COP than the test data of the air conditioner using a common liquid separator when the measured power is lower.

Optionally, as shown in FIG. 29 , a mesh member 260 is disposed in the liquid separation chamber 230 for filtering or separating gas and liquid of the refrigerant flowing through the liquid separation chamber 230 .

In this embodiment, as shown in FIG. 30 , the main function of the mesh member 260 is to break up larger liquid droplets and air bubbles to form a turbulence zone, and the gas-liquid two-phase refrigerant mixed after breaking needs to be carried out on the upper part of the mesh structure. Mixing, so as to ensure that the refrigerant entering the branch pipe is evenly distributed, so that the gas-liquid two-phase heterogeneous refrigerant flowing through the confluence pipe is evenly distributed when it flows into the liquid branch pipe.

Optionally, the mesh member 260 is arranged at a position of 1/4˜3/4 of the height of the liquid separation chamber.

Optionally, the mesh member 260 is set at 1/2 of the height of the dispenser.

In some embodiments, the mesh member 260 is a planar mesh structure perpendicular to the axis of the liquid separation chamber 230 . In some other embodiments, the mesh member 260 is an arc-shaped mesh structure with the center concave toward the liquid distribution port.

Table 28 below shows several porosity and corresponding parameters of wire mesh,

Table 28

As shown in the table above, the smaller the number of holes, the larger the diameter of the holes, and the more difficult it is to break up large droplets and air bubbles. If the number of holes is too large, the pressure drop will be too large, which is not conducive to the flow of refrigerant. Therefore, choose 60-120 mesh wire mesh.

At the same time, through the simulation analysis of mesh pieces with different numbers of holes and wire diameters built into the liquid separator of the same specification, the simulation test data are shown in Figures 31 and 32. The unevenness of the fluid flowing through the 80 and 100 mesh mesh pieces , instability are kept at a low level, and lower than the Venturi distributor, so the porosity of the preferred mesh is 100 mesh, the wire diameter is 0.1mm, the unevenness, instability of the mesh are minimum values.

As shown in FIG. 33 , 34 a , and 34 b , an optional one-way valve 300 includes a valve housing 320 and a valve core 330 .

In an embodiment, the valve housing 320 includes a valve outlet 322 , a valve inlet 321 and a valve passage 323 formed inside the valve housing and communicating with the valve outlet 322 and the valve inlet 321 . The spool 330 is movably arranged in the valve channel along the axial direction, thereby realizing the conduction/blocking switch of the one-way valve.

As shown in FIG. 35 , the length between the two ends of the spool 330 is set as L2 , and the equivalent diameter of the end surface of the spool 330 corresponding to the valve outlet 322 is D.

Then optionally, the ratio of L2/D is greater than or equal to e1. e1 is a first preset ratio. By setting a lower limit value for the length-to-diameter ratio of the check valve spool, in order to reduce the occurrence of vibration, collision and noise between the valve core and the inner wall of the valve housing caused by too small a length-to-diameter ratio, the one-way valve defined in this embodiment is adopted. The valve can make the valve core maintain better stability when the refrigerant flows through the one-way valve.

Optionally, the value range of e1 is 0.5-1.

Yet another option, the ratio of L2/D is less than or equal to e2. e2 is a second preset ratio greater than e1. By setting an upper limit to the length-to-diameter ratio of the check valve spool, it can also reduce wall vibration, collision and noise, so that the spool can maintain better stability.

Optionally, the value range of e2 is 1.5-2.

Exemplarily, for the same air conditioner, under the same test conditions, the noise data of the ordinary one-way valve and the one-way valve to be protected by this application were respectively tested. , the upper port is open to the atmosphere, and the noise value is tested at a distance of 1m from the valve body; the test data is shown in Table 29 below:

Table 29

e值e-value	噪音测试结果Noise Test Results
0.450.45	噪音值33.3dB(A)，有轻微阀芯碰撞定位销的异常音The noise value is 33.3dB(A), and there is a slight abnormal sound of the spool hitting the positioning pin
0.50.5	噪音值33.3dB(A)，无异常音Noise value 33.3dB(A), no abnormal sound
1.161.16	噪音值33.1dB(A)，无杂音Noise value 33.1dB(A), no noise
22	噪音值35.3dB(A)，无异常音Noise value 35.3dB(A), no abnormal sound
2.322.32	噪音值35.8dB(A)，有阀芯碰撞管壁的异常音The noise value is 35.8dB(A), and there is an abnormal sound when the spool hits the pipe wall

From the comparison of the above data, it can be seen that when the aspect ratio L2/D (e=0.45) of the spool is less than e1 or L2/D (e=2.32) is greater than e2, there is a slight abnormal sound of the spool colliding with the positioning pin. The noise test results are poor, and when the aspect ratio of the spool is within the range of e1 and e2, the measured noise is relatively low, and low-noise operation can be achieved.

Optionally, as shown in FIGS. 36-37e , the first end of the valve core 330 corresponding to the valve outlet 322 is configured with a hollow structure. The hollow structure at the end of the valve core can increase the contact area between the superheated refrigerant and the end surface of the valve core, and increase the force-bearing area of the valve core; at the same time, the hollow structure is a symmetrical design formed around the center line of the valve core. Store full refrigerant, which can improve the stability of valve core closing

Optionally, as shown in FIG. 36 , 37a and 37b , the hollow structure includes a hollow groove 335 concavely formed from the end face of the first end along the axial direction.

Optionally, the radial section of the hollow groove 335 is circular, rhombus or triangular.

Optionally, the groove bottom of the hollow groove 335 is configured as a plane or a concave cone. .

In some optional embodiments, the design parameters of the hollow groove 335 meet the requirements shown in Table 30 below:

Table 30

Among them, d=D2/D1, D2 is the equivalent diameter of the hollow groove, D1 is the equivalent diameter of the valve core; h=H2/H1, H2 is the equivalent length of the hollow groove, H1 is the equivalent length of the valve core; v=V2/ V1 and V2 are the volumes of the hollow grooves, and V1 is the solid volume of the spool.

In this embodiment, for the same air conditioner, under the same test conditions, two check valves in the prior art in the form of spools (plum blossom-shaped spool, square solid spool) and the one-way valve using the present application were tested respectively. The refrigerant leakage data of the one-way valve designed with a hollow groove is tested under the condition that 0.02MPa nitrogen gas is introduced, and the test data are shown in Table 31 below:

Table 31

阀芯形式Spool form	梅花状阀芯Torx spool	正方体实心阀芯Cube solid spool	带空心槽的阀芯Spool with hollow groove
冷媒泄漏量Refrigerant leakage	257ml/min257ml/min	143ml/min143ml/min	91ml/min91ml/min

It can be seen from the comparison of the above data that the valve core with the hollow groove adopted in the present application has a lower refrigerant leakage and a better sealing effect.

In still some optional embodiments, as shown in FIG. 37 c , the hollow structure includes a closed hollow cavity 336 formed inside the valve core 330 .

Optionally, as shown in FIG. 37c , the main body of the valve core 330 includes a cylindrical section near the outlet side of the valve and a conical section near the inlet side of the valve, wherein the hollow cavity 336 is mainly formed in the cylindrical section.

The hollow cavity 336 can reduce the weight of the cylindrical section of the spool, so that the overall center of gravity of the spool moves down, and more gravity can be concentrated on the tapered section, which is beneficial to keep the spool stable during the sealing process of the spool.

Optionally, the section of the cylindrical section of the spool 330 is square or circular.

Optionally, the radial section of the hollow cavity 336 is circular. Wherein, the value range of the ratio of the radius of the hollow cavity to the radius of the valve core is 1/4˜3/4.

Optionally, the ratio of the axial length of the hollow cavity to the axial length of the cylindrical section of the valve core ranges from 1/5 to 4/5.

In some alternative embodiments, as shown in FIG. 37d and 37e , the valve core 330 includes a valve core body 333 and a stabilizing block 334 , wherein the material density of the valve core body 333 is lower than that of the stabilizing block 334 .

Optionally, the stabilizing block 334 is configured as a tapered end of the valve core body 333 corresponding to the second end of the valve inlet 321, as shown in FIG. 37d, or is packaged inside the valve core body 333 and disposed near the second end. , as shown in Figure 37e.

In this embodiment, because the density of the stabilizing block 334 is higher, it can play the role of adding weight to the tapered end, so that the center of gravity of the valve core as a whole moves down, and the gravity can be more concentrated on the tapered section, which is beneficial to the valve. Keep the valve core stable during the core sealing process.

Optionally, the material of the stabilizing block 334 includes but not limited to iron or copper.

Optionally, the material of the spool body 333 includes but not limited to aluminum or plastic.

The above description and drawings sufficiently illustrate the embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may incorporate structural and other changes. The examples merely represent possible variations. Individual components and functions are optional unless explicitly required, and the order of operations may vary. Portions and features of some embodiments may be included in or substituted for those of other embodiments. Embodiments of the present disclosure are not limited to the structures that have been described above and shown in the drawings, and various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.

Claims

A dispenser, characterized in that it comprises:

The housing has a liquid separation chamber inside, and the housing is provided with a first liquid distribution port and a second liquid distribution port;

A first liquid branch pipe communicates with the liquid chamber through the first liquid port; and,

A second liquid branch pipe communicates with the liquid chamber through the second liquid port;

Wherein, the inner diameter of the first liquid branch pipe is larger than the inner diameter of the second liquid branch pipe.
The dispenser according to claim 1, characterized in that,

The inner diameter of the second liquid branch pipe is greater than or equal to 3mm.
The dispenser according to claim 2, further comprising:

A confluence pipe communicates with the liquid separation chamber, the confluence pipe includes a bent and connected first pipe section and a second pipe section, the first pipe section directly communicates with the liquid separation chamber,

Wherein, the plane where the axes of the first pipe section and the second pipe section are located is the first plane, the plane where the axes of the first liquid branch pipe and the second liquid branch pipe is located is the second plane, and the first plane and The second plane is non-vertical.
The dispenser according to any one of claims 1 to 3, characterized in that,

The ratio of the cross-sectional area of the first liquid branch pipe to the cross-sectional area of the second liquid branch pipe is less than or equal to x, where x is a preset value.
The dispenser according to claim 4, characterized in that,

The value range of x is: 1.3≤x≤1.7.
The dispenser according to any one of claims 1 to 3, characterized in that,

The ratio of the cross-sectional area of the first liquid branch pipe to the cross-sectional area of the second liquid branch pipe is greater than x, where x is a preset value.
The dispenser according to claim 6, characterized in that,

The ratio of the cross-sectional area of the first liquid branch pipe to the cross-sectional area of the second liquid branch pipe is less than or equal to y, wherein y is a preset value greater than x.
A heat exchanger, characterized by comprising the liquid separator according to any one of claims 1-7.
A refrigeration cycle system, characterized in that, comprising:

The heat exchanger according to claim 8.
An air conditioner, characterized in that it comprises:

The refrigeration cycle system as claimed in claim 9.