CN216977258U - Knockout, heat exchanger, refrigeration cycle system, air conditioner - Google Patents

Abstract

The application relates to the technical field of air conditioning, and discloses a knockout is disclosed, include: the liquid separation device comprises a shell, a first liquid separation branch pipe and a second liquid separation branch pipe. The shell is internally provided with a liquid dividing cavity which is provided with a first liquid dividing port and a second liquid dividing port; the first branch liquid separating pipe penetrates through the first liquid separating port to be communicated with the liquid separating cavity, and the second branch liquid separating pipe penetrates through the second liquid separating port to be communicated with the liquid separating cavity. The axis of the first branch liquid-dividing pipe is not parallel to the center line of the liquid-dividing cavity, and/or the axis of the second branch liquid-dividing pipe is not parallel to the center line of the liquid-dividing cavity. The application provides a knockout makes the refrigerant volume that flows into two branch liquid branch pipes different. The application also discloses a heat exchanger, a refrigeration cycle system and an air conditioner.

Description

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

This application claims the priority of the Chinese patent application titled "Separator, Check Valve, Heat Exchanger, Refrigeration Circulation System, Air Conditioner" and application number 202122281454.9 filed on September 19, 2021, by reference in its entirety The content is incorporated herein.

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

When the air conditioner is operating under heating conditions, the outdoor heat exchanger is used as an evaporator, and the throttled refrigerant needs to be distributed to each heat exchange branch through the liquid separator.

The existing distribution and collection device includes a collection pipe, a plurality of distribution pipes and a distributor. Wherein, the liquid collecting pipe is provided with a liquid return port and a plurality of connection ports, and the first ends of the plurality of liquid distribution pipes are correspondingly gap-fitted in the plurality of connecting ports and all face the outside of the liquid collecting pipe. The second ends are respectively connected with the distributor. In this way, the refrigerant can flow through the distributor and the liquid separator for pressure drop during heating, so as to ensure that the refrigerant is evenly distributed to each flow path of the heat exchanger, and to ensure the even distribution of the refrigerant during heating.

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

The existing liquid separator is an improvement to improve the uniformity of the refrigerant flowing out of each liquid branching branch pipe, and does not provide a solution on how to make the refrigerant flowing out of each liquid branching branch pipe different.

Utility model content

In order to provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. This summary is not intended to be an extensive review, nor to identify key/critical elements or delineate the scope of protection 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 of refrigerant flowing out of each liquid separation branch pipe of the liquid separator different.

An embodiment of the present disclosure provides a liquid separator, comprising: a housing with a liquid separation cavity inside, a first liquid separation port and a second liquid separation port are opened; a first liquid separation branch pipe, penetrating the first liquid separation port communicating with the liquid-separating chamber; and, a second liquid-separating branch pipe, passing through the second liquid-separating port and communicating with the liquid-separating chamber; wherein, the axis of the first liquid-separating branch pipe is connected to the axis of the liquid-separating chamber. The center lines are not parallel, and/or the axis of the second branch pipe is not parallel to the center line of the liquid distribution chamber.

Embodiments of the present disclosure provide a heat exchanger, including the aforementioned liquid separator.

Embodiments of the present disclosure provide a refrigeration cycle system including the aforementioned heat exchanger.

Embodiments of the present disclosure provide an air conditioner including the aforementioned refrigeration cycle system.

The 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:

Embodiments of the present disclosure provide a dispenser, including a housing, a first branch pipe, and a second branch pipe. There is a liquid separation chamber inside the shell. The first liquid distribution branch pipe penetrates through the first liquid distribution port of the housing and communicates with the liquid distribution chamber. The second liquid distribution branch pipe passes through the second liquid distribution port of the housing and communicates with the liquid distribution chamber. In this way, the first branch pipe and/or the second branch pipe form an angle with the liquid separation chamber, and after the refrigerant is distributed through the liquid separation chamber, the amount of refrigerant flowing into the first branch pipe and the amount of refrigerant flowing into the second branch pipe The amount of refrigerant is different, and the demand for the amount of refrigerant flowing into different branch pipes is satisfied.

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 accompanying drawings, which are not intended to limit the embodiments, and elements with the same reference numerals in the drawings are shown as similar elements, The drawings do not constitute a limitation of scale, and in which:

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

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

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

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

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

6 is a schematic diagram of a heat exchange flow path in the case where a heat exchanger provided by an embodiment of the present disclosure is used as an evaporator;

7 is a schematic diagram of a heat exchange flow path in the case where a heat exchanger provided by an embodiment of the present disclosure is used as a condenser;

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

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

10 is a schematic structural diagram of other parts of the heat exchanger provided by the embodiment of the present disclosure except for the heat exchange tubes;

11 is a schematic structural diagram of a liquid separator provided in an embodiment of the present disclosure with an inclined arrangement;

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

13 is a schematic diagram of an end surface of a liquid separator provided by an embodiment of the present disclosure;

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

15 is a schematic structural diagram of another dispenser provided by an embodiment of the present disclosure;

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

17 is a schematic structural diagram of another dispenser provided by an embodiment of the present disclosure;

18 is a schematic structural diagram of another dispenser provided by an embodiment of the present disclosure;

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

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

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

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

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

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

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

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

Figure 27 is a schematic front view of the liquid dispenser provided by the embodiment of Figure 26;

Figure 28 is a cross-sectional view taken along the line A-A of Figure 27;

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

FIG. 30 is a simulation effect diagram of the flow splitting effect of a liquid dispenser provided by an embodiment of the present disclosure;

31 is a comparison diagram of unevenness when the meshes of different meshes provided by the embodiment of the present disclosure are divided;

FIG. 32 is a comparison diagram of instability when the mesh members of different mesh numbers provided by the embodiment of the present disclosure are divided;

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

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

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 one-way valve spool provided by an embodiment of the present disclosure;

36 is a perspective view of another one-way valve spool provided by an embodiment of the present disclosure;

37a is a cross-sectional view of another one-way valve spool provided by an embodiment of the present disclosure;

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

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

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

37e is a cross-sectional view of another one-way valve spool provided by an embodiment of the present disclosure.

Reference number:

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 pipe; 151: first bypass pipe Road; 152: Second bypass line; 220: Shell; 230: Dividing chamber; 240: Converging pipe; 250: Dividing branch pipe; : valve seat; 111: first refrigerant inlet and outlet; 112: second refrigerant inlet and outlet; 121: first heat exchange branch; 122: second heat exchange branch; 123: third heat exchange branch; 124: fourth heat exchange Thermal branch; 211: First dispenser; 212: Second dispenser; 213: Third dispenser; 214: Fourth dispenser; 221: Dispenser; 222: Confluence; 231: First a liquid storage cavity; 232: the second liquid storage cavity; 233: the liquid storage cavity channel; 234: the confluence cavity; 235: the first branch cavity; 236: the second branch cavity; 240: the confluence pipe; A pipe section; 242: the second pipe section; 251: the first branch pipe; 252: the second branch pipe; 253: the third branch pipe; 311: the first one-way valve; 312: the second one-way valve; 321 : valve inlet; 322: valve outlet; 323: valve passage; 324: valve body throat; 331: first end; 332: second end; 333: valve core body; 334: stabilizer block; 335: hollow groove; 336 : hollow cavity; 400, three-way pipe.

Detailed ways

In order to understand the features and technical contents 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 with reference to the accompanying drawings, which are for reference only and are not intended to limit the embodiments of the present disclosure. In the following technical description, for the convenience of explanation, numerous details are provided 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-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the data so used may be interchanged under appropriate circumstances for the purposes of implementing the embodiments of the disclosure described herein. Furthermore, the terms "comprising" and "having", and any variations thereof, are intended to cover 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 shown in the drawings or Positional relationship. These terms are primarily used to better describe the embodiments of the present disclosure and embodiments thereof, and are not intended to limit the fact that the indicated device, element, or component must have a particular orientation, or be constructed and operated in a particular orientation. In addition, some of the above-mentioned terms may be used to express other meanings besides orientation or positional relationship. For example, the term "on" may also be used to express a certain attachment or connection relationship in some cases. For those of ordinary skill in the art, the specific meanings of these terms in the embodiments of the present disclosure can be understood according to specific situations.

In addition, the terms "arranged", "connected" and "fixed" should be construed broadly. For example, "connection" may be a fixed connection, a detachable connection, or a unitary construction; it may be a mechanical connection, or an electrical connection; it may be a direct connection, or an indirect connection through an intermediary, or two devices, elements or Internal connectivity between components. For those of ordinary skill in the art, the specific meanings of the above terms in the embodiments of the present disclosure can be understood according to specific situations.

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

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

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

The embodiments of the present disclosure relate to the numerical values in the disclosed tables, the units corresponding to indoor working conditions and outdoor working conditions are ℃, 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 the embodiments in the embodiments of the present disclosure and the features in the embodiments may be combined with each other in the case of no conflict.

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, the cooling/heating power set by the user during the use of the air conditioner is different, and the flow and pressure of the refrigerant discharged from the compressor also change accordingly, so that the refrigerant state is not complete when the refrigerant flows through the heat exchanger. Consistent, for example, the refrigerant pressure 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 one-way valve, the pressure difference between the two sides of the valve core is relatively small, which is likely to cause the valve core to fail to open normally, still block at the throat of the valve body, or open the range. Abnormal problems affect the normal use of the one-way valve.

In order to solve the problem that the pressure difference between the two sides of the one-way valve 300 is too small and cannot be opened normally, optionally, the one-way valve 300 in the embodiment of the present disclosure satisfies the following relationship:

L ₃ ⁴ *R≤Z1,

With reference to 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 valve core 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 one-way valve 300 is in the form of a cylindrical throat of equal width, and L ₃ is the value of the diameter and length of the cylindrical throat; and in other embodiments Among them, the throat of the valve body of the one-way valve 300 is in the form of a conical throat, as shown in FIG. 33 , and corresponding to this form, L ₃ is the maximum width of the conical 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 selection method of the one-way valve applied to the air conditioner in the prior art, the size design of the one-way valve selected in this application can make the valve core and the refrigeration cycle system work with the single-way valve. The pressure difference between the inlet and outlet of the valve is matched, so that the one-way valve can still work normally under a small pressure difference; this allows the air conditioner to accurately guide the refrigerant flow direction (such as cooling flow direction and heating flow direction) when switching. 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 form includes a one-to-one correspondence between Z1 and Q, etc., corresponding to air conditioner models with different rated cooling capacities, the selected unidirectional This relationship is satisfied between the specification form of the valve and the rated cooling capacity of the model.

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

In still 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. ρ _agent is the density of the refrigerant, the unit is kg/m ³ , and the ρ _core is the valve core density of the check valve, the unit is kg/m ³ .

Optionally, the value range of the local resistance coefficient λ is 0.3-0.55.

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 valve core 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.

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

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

The stress area of the spool is 4R ² , then the stress of the spool is 4R ² *△P;

At the same time, the volume of the valve core is 0.5*(13/6)*π*R ³ , then the gravity of the valve core is 0.5*(13/6)*π*R ³ *g; where (13/6) is It is obtained by adding the coefficients in the semicircle volume and the cylinder volume formula, specifically 13/6=2/3+3/2; g is the gravitational constant, and the value of 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 is bottom-up when the one-way valve is turned on. Therefore, the stress state that the valve core needs to satisfy in the open state of the one-way valve can be expressed by the following formula :

4R ² *△P≥0.5*(13/6)*π*R ³ *g;

After arranging the above inequalities, the above relationship between the rated cooling capacity Q and the one-way valve can be obtained:

Here, take the air conditioner models with rated cooling capacity of 3.5KW, 5.0KW and 7.2KW as an example, and substitute the above formula for calculation; it is assumed that the environmental parameters and the state parameters of the air conditioner 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℃, the condensation pressure is 2.7948MPa, and the subcooling degree is 5℃;

The evaporation temperature is 17℃, the evaporation pressure is 1.3559MPa, and the superheat degree is 5℃;

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 is 0.014kg/s, and the one-way valve refrigerant flow is 0.010kg/s;

For an air conditioner with a rated cooling capacity of 5.0KW, the total refrigerant flow is 0.019kg/s, and the one-way valve refrigerant flow is 0.014kg/s;

For an air conditioner with a rated cooling capacity of 7.2KW, the total refrigerant flow is 0.027kg/s, and the one-way valve refrigerant flow is 0.020kg/s;

The specific values of the above parameters are brought into the equation to obtain:

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 one-way valve applied in the present application calculated according to the above formula satisfies the relationship of L ₃ ⁴ *R≤Z1=11.9, then the relationship with other models of Compared with the one-way valve (L ₃ ⁴ *R≤Z1=6), the test data under 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 dimensional relationship defined by the solution of the present application is significantly lower than that of the one-way valve with other dimensional relationships, and the technical solution of the present application can achieve 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 one-way valve 300 .

The heat exchanger body 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 111 and flows out through the second refrigerant inlet 112. When the heat exchanger is used as a condenser, the refrigerant flows in through the second refrigerant inlet 112, and flows through the second refrigerant inlet 112. A refrigerant outlet 111 flows out.

The flow direction of the check valve 300 is limited to conduct when the heat exchanger is used as an evaporator, and to block when the heat exchanger is used as a condenser.

Optionally, the one-way valve 300 is provided 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 arranged 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 refrigerant circulation is diversified, and the refrigeration equipment can be improved in The heat exchange 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, by setting the number of heat exchange tubes 140 on each heat exchange branch 120 within a range of less than or equal to 8, it is possible to avoid excessive length of the heat exchange tubes 140 on each heat exchange branch 120 and cause pressure Changes in cooling are too fast to avoid the reduction of energy efficiency of refrigeration equipment.

Optionally, the w heat exchange branches 120 are connected between the first refrigerant outlet 111 and the second refrigerant inlet 112 through the liquid separator 200 . In this way, the liquid separation function of the liquid separator 200 can be used to form multiple flow channels during the flow of the refrigerant along the heat exchange branch 120 to make the flow of the refrigerant more reasonable. High heat exchange efficiency can be maintained in all cases.

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 separator 211 is communicated with the first refrigerant outlet 111; the second liquid separator 212 is communicated with the first liquid separator 211 through the first one-way valve 311, and the flow direction of the first one-way valve 311 is toward the second liquid separator 212; the third liquid separator 213 is communicated with the first liquid separator 211 and the second liquid separator 212; the fourth liquid separator 214 is communicated with the second refrigerant outlet 112, and a split port is connected with the second one-way valve 312 through the second one-way valve 312. The third liquid separator 213 is in communication, and the other distribution ports are in communication with the second liquid separator 212 . In this way, the refrigerant flowing through is separated by a plurality of liquid 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 refrigerant can be circulated in both positive and negative directions so as to have different The flow path can maintain a 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 separator 211 communicates with the first refrigerant outlet 111 through n2 heat exchange tubes 140 . In this way, the heat exchange tube 140 is provided at the first refrigerant inlet and outlet 111 as a subcooling section, which can further liquefy the refrigerant flowing through and improve 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 a range of less than or equal to 5, which can prevent the resistance from increasing due to the excessively long length of the subcooling section when the heat exchanger is used as an evaporator. The pressure drop is too high, which affects the heat exchange 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 flow paths 130 . When the heat exchanger is used as the evaporator, the number N of the heat exchange flow paths 130 formed by the heat exchange tubes 140 is determined according to the total number n of all the heat exchange tubes 140 . In this way, the flow paths of the heat exchange tubes 140 of the heat exchanger can be reasonably distributed, preventing the number of heat exchange tubes 140 in a single heat exchange flow path 130 from being too large or too small, resulting in insufficient evaporation or condensation, which can improve the heat exchange rate. 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 outlet 111 .

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

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

Optionally, a=5 or 6 and b=2 or 3. In this way, by limiting the value ranges of a and b to this region, when the heat exchanger is used as an evaporator, the number of heat exchange flow paths 130 composed of n heat exchange tubes 140 is more reasonable, which is beneficial to the evaporator. Evaporation efficiency of the internal refrigerant, thereby improving the heat exchange efficiency of the heat exchanger.

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

Optionally, as shown in FIGS. 6 and 7 , when the heat exchanger is used as the evaporator, n heat exchange tubes 140 form N heat exchange flow paths 130 . When the heat exchanger is used as a condenser, n heat exchange tubes 140 form M heat exchange flow paths 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, the operating principles are different, and the same number of heat exchange flow paths 130 cannot be used for both of them. When the heat exchanger is used as an evaporator and when the heat exchanger is used as a condenser, the number of heat exchange flow paths 130 through which the refrigerant circulates is different, which can meet the different needs of the two working conditions of evaporation and condensation, and improve heat exchange. Efficiency when the evaporator is used as an evaporator and the heat exchanger is used as a condenser.

Optionally, when the heat exchanger is used as the evaporator, all the heat exchange tubes 140 form N heat exchange flow paths 130 . When the heat exchanger is used as a condenser, all the heat exchange tubes 140 form M heat exchange flow paths 130 . Among them, N>M. In this way, when the heat exchanger is used as an evaporator, the refrigerant inside is in the process of changing from a liquid state to a gaseous state, and the volume of the refrigerant will increase, so more heat exchange flow paths 130 are required, and the heat exchanger is used as a condenser. In the case of a heat exchanger, the refrigerant inside is in the process of changing from gaseous state to liquid state, and the volume of the refrigerant will decrease. At this time, fewer heat exchange flow paths 130 can accommodate the refrigerant. Therefore, setting N greater than M can replace the refrigerant. The heat exchanger can smoothly pass through the refrigerant when it is used as an evaporator and as a condenser, 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 improved significantly, the energy efficiency level of the product can be increased, and the energy efficiency of the product can be improved while saving environmental protection. commercial value and 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, which 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 paths 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 with different ratios of M and N is as follows:

In the case of the preferred solution M/N=1/2 of 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 solution M/N=1/4 of this embodiment, the energy efficiency performance of the product is shown in Table 6 below:

Table 6

When the preferred solution of this embodiment is M/N=3/4, 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 APF is the maximum value of 5.10. At this time, M/N=1/2. 1, then 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 the use of M/N=1/2 in the 3.5KW model can greatly improve the energy efficiency and be more energy-saving and environmentally friendly.

Optionally, a heat exchanger of M/N=4/7 is used in the 7.2KW model. In this way, the setting of the number of heat exchange paths 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 with different ratios of M and N is shown in the following table:

In the case of the preferred solution of this embodiment, M/N=4/7, 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

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

Table 10

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

Table 11

When the preferred solution of this embodiment is M/N=5/7, 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 APF is the maximum value of 4.56. At this time, M/N=0.57. If M is reduced to 3, then The APF drops to 4.45. If M drops to 2, the APF drops to 4.32. On the contrary, if M increases to 5, the APF drops to 4.35. It can be seen that the use of M/N=4/7 in the 7.2KW model can greatly improve the energy efficiency. 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, the difference in the number of flow paths can accelerate the circulation and increase the heat transfer coefficient.

Optionally, the 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 number n of the heat exchange tubes 140 , the capacity segment of the refrigeration equipment, and the corresponding relationship between the pipe diameters of the heat exchange tubes 140 . In this way, when the capacity segment of the refrigeration equipment is determined, the space size of the location is generally determined. At this time, the heat exchange tubes can be determined according to the diameter of the heat exchange tubes 140 and the number n of the heat exchange tubes 140. The space 140 needs to be occupied by the heat exchange tube 140, according to the reasonable arrangement and arrangement of the heat exchange tubes 140, 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 heat exchange tubes 140 and the number n of heat exchange tubes 140, the capacity segment 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 FIGS. 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 by integers and then there are more 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 equally divided into h heat exchange branches 120, where 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 different resistances from causing different refrigerant flow, which in turn leads to the overall heat exchange of the heat exchanger Not uniform enough.

More specifically, in the case of w=3 and n=10, one heat exchange tube 140 is extracted, and three heat exchange tubes 140 are arranged on each heat exchange branch 120 , or three heat exchange tubes 140 are arranged on each heat exchange branch 120 . There are two heat exchange tubes 140, one heat exchange tube 140 is connected with the first refrigerant inlet and outlet 111 as a subcooling section, or as shown in FIG. 8, three heat exchange tubes 140 are set 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 and n=22, two heat exchange tubes 140 are extracted, and four heat exchange tubes 140 are arranged on each heat exchange branch 120 , or four heat exchange tubes 140 are arranged on each heat exchange branch 120 . 2 heat exchange tubes 140, 2 heat exchange tubes 140 are connected with the first refrigerant inlet and outlet 111 as subcooling sections, or as shown in FIG. 9, 5 heat exchange tubes 140 are arranged on the 2 heat exchange branches 120, and the other 3 Four heat exchange tubes 140 are arranged on the heat exchange branch 120 .

Optionally, the second liquid separator 212 is connected with a manifold that communicates with the refrigerant inlet and outlet and a plurality of liquid separation ports 221 communicated with the plurality of heat exchange branches 120 one by one; wherein the second liquid separator 212 is vertically arranged, so that the separation The liquid port 221 faces upward and the confluence pipe faces downward, 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 separation port 221 are used;

The first one-way valve 311 is provided at the refrigerant inlet and outlet 110, and its flow direction is restricted to conduct when the heat exchanger 100 is used as an evaporator, and to block when the heat exchanger 100 is used as a condenser to allow the second The dispenser 212 confluences and stores liquid.

Optionally, the number of the liquid separation ports 221 is 3, and in the case where the heat exchanger 100 is used as a condenser, 2 liquid inlets and 1 liquid outlet.

Another option, as shown in FIG. 11 , the second liquid distributor 212 is arranged obliquely, the liquid distribution 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 When the heater 100 is used as a condenser, at least one liquid inlet and at least one liquid outlet in the liquid separation port 221 are provided.

Optionally, when the second liquid separator 212 is inclined, the inclination angle ∠α≤β with the vertical direction, where β is a preset angle value.

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

Optionally, the value range of β is 10° to 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 main body includes a first refrigerant inlet 111 , a second refrigerant inlet 112 , and w heat exchange branches connected between the first refrigerant inlet 111 and the second refrigerant inlet 112 . w is an integer greater than 1.

The liquid separation and storage device includes a manifold that communicates with the first refrigerant outlet 111 or the second refrigerant inlet 112 , and a plurality of liquid separation ports 221 that communicate with some of the heat exchange branches one by one. The liquid-separating and accumulating device is configured to divide the refrigerant delivered by the refrigerant inlet and outlet to the plurality of 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 manifold and reservoir.

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

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

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

Optionally, the one-way conduction 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. Those skilled in the art can know that other types of one-way conduction can be realized in the field. Functional parts or assemblies can also be used as optional alternatives to this example, and should also be included within the scope of protection of the present 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 limited to conduct when the heat exchanger 100 is used as an evaporator, and block and allow the liquid separation chamber 230 to store liquid when the heat exchanger 100 is used as a condenser.

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

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

Exemplarily, as shown in FIG. 3 , taking the second liquid separator 212 as an example, in the case where the heat exchanger is used as a condenser, the second refrigerant inlet 112 is used as the inflow port of the refrigerant, and the first refrigerant outlet 111 is used as the inlet and outlet of the refrigerant. The outlet of the refrigerant, after the refrigerant flows into the heat exchanger from the second refrigerant inlet 112, it 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 in the blocking state, and flow out to the first heat exchange branch 121 and the second heat exchange branch 122 and continue to flow into the second liquid separator 212 for confluence, and the refrigerant after the confluence is communicated from the second liquid separator 212 A liquid separation port of the third heat exchange branch 123 flows out. Since the liquid separation ports of the second liquid separator 212 are all set upward, in this state, part of the refrigerant can be stored in the second liquid separation under the action of gravity. The liquid-separating chamber of the second liquid-separator 212 and the part of the pipe section of the one-way valve from the liquid-separating chamber are connected to realize the liquid storage function of the second liquid-separator 212 .

The heat exchanger provided by the embodiment 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. In the form that the air conditioner only uses the accumulator to store the liquid, this embodiment can expand the refrigerant liquid storage range of the air conditioner, especially in the low load state, it can reduce the heat circulation of the excess refrigerant, so that the actual refrigerant circulation volume of the air conditioner can be compared with the current one. The working performance is adapted to improve 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 optimize the performance of the air conditioner; usually, the optimal refrigerant for heating operation The charging amount is slightly larger than that during cooling operation, so during cooling operation, the extra refrigerant is generally "stored" in the air conditioner in liquid form; in this scheme, the outdoor heat exchanger is used as "" Condenser" is used, 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, the air conditioner is affected by the balance of high and low pressure during the process of starting and stopping, 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) most refrigerants (60% or more) are 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", and the amount of refrigerant stored in the liquid separator is larger when the air conditioner is stopped than when it is turned on; and when the air conditioner is running in cooling mode, the outdoor heat exchanger is used. The heat exchanger is used as a "condenser", and the storage capacity of the refrigerant in the liquid separator when the air conditioner is turned on is larger than that when the air conditioner is turned off. When the air conditioner is shut down, some refrigerants are stored in the indoor and outdoor heat exchangers, compressor chambers, gas-liquid separators and other components.

Under the APF test standard, there are 100% load and partial load test conditions for both cooling and heating operation of the air conditioner. Under the partial load state, the refrigerant circulation volume is smaller than that under 100% load, so the liquid storage capacity of the liquid distributor during partial load operation is greater than 100% load.

Exemplarily, an air conditioner using a distributor with a common split flow design without a liquid storage function was compared with an air conditioner with a liquid distributor with a variable split design combined with a one-way valve with a liquid storage function, and the capabilities of the two were tested, respectively. Power and energy efficiency, the test data are shown in Table 14 below:

Table 14

As can be seen from the above table, since the variable diversion achieves a better refrigeration flow path and cooperates with the liquid separator with a one-way valve with a liquid storage function, this application uses a variable diversion design liquid separator with a one-way valve with a 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 distributor without the liquid storage function of the ordinary split flow design.

At the same time, for the same air conditioner, the present application tests the energy efficiency of the air conditioner with and without the liquid storage function by using two different liquid separators in the heat exchanger. The volume of the liquid separator in the scheme ② is significantly larger than the volume of the liquid separator 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 shown in Table 15:

Table 15

ability power efficiency Scheme ① 3440W 861W 4.00 Scheme ② 3445W 858W 4.02

From the data comparison in the above table, it can be seen that since the form of the liquid distributor in the prior art generally only considers the "split" function, the liquid distributor is generally designed to be as small as possible when the "split" function is satisfied. , in order to reduce the occupation of space and volume and the manufacturing cost; and the present application adopts a liquid separator with a larger volume of liquid separation chamber, which can realize the liquid storage function in the refrigeration mode, and can improve the liquid separation using this liquid storage function. The energy efficiency of the air conditioner with the air conditioner in the actual operation process, the measured performance is better than that of the air conditioner using the ordinary liquid separator.

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

In order to realize the liquid storage function of the dispenser 200, avoid the problem of excessive liquid storage due to the excessive volume of the liquid dispenser chamber, and also to meet 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, the unit is cm ³ , Q is the rated cooling capacity, the unit is kW.

Optionally, the heat exchanger applying the variable splitting form shares two forms, including the four-branch variable splitting form shown in FIG. 3 and the three-branch variable splitting form shown in FIG. 12 .

Optionally, for a heat exchanger in the form of four-branch variable split flow, 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 heat exchanger in the form of four-branch variable split flow, the relationship between the rated capacity of the unit and the charging capacity is roughly: m=160Q; the normal heating mode requires higher refrigerant charging capacity than the cooling mode. 10 to 15%, while the compressor gas-liquid separator can generally store 5 to 10% of the refrigerant, the actual refrigerant that needs to be stored in the liquid separator is 5% of the total charge, if the actual storage capacity of the liquid separator exceeds this 5% of the total amount of filling may affect the actual refrigerant circulation volume of the air conditioner, so the liquid distributor needs to store up to m=160Q*5%=8Q.

Optionally, the refrigerant type is difluoromethane (R32), and the refrigerant density is about 0.8 to 1.1 g/cm3 within the actual operating temperature range. Based on the upper limit of the refrigerant density of 0.8 g/cm3, the volume of the separation chamber itself cannot exceed 0.8 g/cm3. 8Q/0.8=10Q, Q is calculated in 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 satisfy V≤f2*Q=10*3.5=35, that is, the volume of the liquid separator 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 has tested the operating performance of the same air conditioner under the conditions of f2 being 8/10/12/14, etc. According to the value of f2) for comparison, the test data are shown in Table 16 below:

Table 16

value of f2 ability power efficiency 8 3446W 857W 4.02 10 3451W 855W 4.04 12 3440W 856W 4.02 14 3423W 861W 3.96

From the test data in the above table, it can be seen that within the range of f2 value (8 to 12) limited by this application, the value of f2 increases, and the energy efficiency gradually improves; but when f2 is too large (f2 exceeds 12), on the contrary, The problem of increased power but decreased energy efficiency occurs.

In some other optional embodiments, in order to realize the liquid storage function of the liquid dispenser 200, avoid the problem of inability to store liquid due to the too small volume of the liquid dispensing chamber of the liquid separator, and also to adapt to the storage capacity of different air conditioner models Liquid requirements, optionally, the liquid dispenser with the 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, the unit is ^cm3 , and Q is the rated cooling capacity, the unit is kW.

Optionally, for the heat exchanger in the form of four-branch variable split flow, the value range of the lower limit f1 of the volume of the liquid separator of the liquid separator is 0.2-4.

Optionally, the value of f1 ranges from 1 to 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 distributor mainly depends on structural constraints. For reliability reasons, the cross-sectional radius R of the liquid distributor is generally about 4 times the radius r of the branch pipe, which can ensure that the distributor radius 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, with reference to FIG. 13 , the radius of the liquid dispenser is R=4r, and in this embodiment, R=1.4cm.

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

Therefore, the inner volume of the dispenser 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 shunt, the application has tested the operating performance of the same air conditioner under the condition that f1 is 1/2/3/4, etc. According to the value of f1) for comparison, the test data is shown in Table 17 below:

Table 17

value of f1 ability power efficiency 1 3426W 865W 3.96 2 3438W 861W 3.99 3 3442W 860W 4.00 4 3442W 859W 4.01

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

Similarly, for a heat exchanger with a three-branch variable splitting form, it is used to connect the main circuit and the two branches using the "one-to-two" three-way pipe 400 shown in FIG. 12 (dotted line frame part), It is smaller in size than a four-way variable split dispenser.

Optionally, for a three-branch variable split 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 changes are 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

Rated cooling capacity 2.6KW 3.5KW 5.0KW 7.2KW value of f 0.72 0.53 0.37 0.25

For an air conditioner with the same 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 casing 220 . Correspondingly, the liquid separation chamber 230 is formed inside the casing 220 and is configured as a cylindrical cavity. When the heat exchanger is used as a "condenser", the refrigerant flows in/out through a plurality of liquid separation ports, and the liquid separation chamber 230 serves as a space for storing part of the refrigerant.

Optionally, the liquid splitting branch pipes 250 communicated with the plurality of heat exchange branches 120 are arranged on one end surface of the shell 220 of the liquid separator 200, and are arranged along the same circumferential line of the end face, and the plurality of liquid splitting branch pipes 250 are evenly arranged. On the end surface of the liquid separator 200 , the distance between adjacent liquid branch branch pipes 250 is the same, so that the liquid separator 200 can distribute the refrigerant to the plurality of liquid branch branch pipes 250 evenly.

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

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

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

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

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

Optionally, the dispenser includes a housing, a confluence pipe 240 , a first branch pipe 251 and a second branch pipe 252 . A liquid separation cavity is opened inside the shell, a first liquid separation port and a second liquid separation port are opened in the shell, the confluence pipe 240 is communicated with the liquid separation cavity, and the first liquid separation branch pipe 251 is connected with the liquid separation cavity through the first liquid separation port The second liquid distribution branch pipe 252 communicates with the liquid distribution chamber through the second liquid distribution 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 separation branch pipe 251 communicates with the first branch cavity 235 through the first liquid separation port, and the second branch cavity 235 The liquid distribution branch pipe 252 communicates with the second branch cavity 236 through the second liquid distribution port.

Optionally, the collecting pipe 240 includes a first pipe section 241 and a second pipe section 242 that are connected by bending, and the first pipe section 241 is in direct communication with the liquid separation chamber.

The plane where the axes of the first pipe section 241 and the second pipe section 242 are located is the first plane. The plane where the axes of the first branch pipe 251 and the second 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 are located is the 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, and it can be understood that the included 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. The first plane is not perpendicular to the second plane, so that the amount of refrigerant entering the first branch pipe 251 and the second 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 branch pipe 251, under the action of gravity, the flow rate of the refrigerant flowing to the second branch pipe 252 is greater than the flow rate to the first branch pipe 251 . Similarly, when the angle between the first plane and the second plane is on the side of the second branch pipe 252, under the action of gravity, the flow rate of the refrigerant flowing to the first branch pipe 251 is greater than the flow rate of the second branch pipe 252 .

Optionally, the liquid separator provided in the embodiment of the present disclosure can be used as the first liquid separator 211 of the heat exchanger shown in FIG. 3 . In the heat exchanger shown in FIG. 3, when the heat exchanger is used as an evaporator, the refrigerant flows into the four parallel heat exchange branches after being split by the first liquid separator 211, namely, the first heat exchange branches 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 branch pipe on the left side of the first liquid separator 211 , and the refrigerant passes through the branch pipe on the right side of the first liquid separator 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 separation branch pipes of the first liquid separator 211 is different. In the heat exchanger shown in Fig. 3, the amount of refrigerant required by the branch pipe on the right is about three times that of the branch pipe on the left. The liquid separator provided by the embodiment of the present disclosure utilizes the gravitational effect of the refrigerant during the flow process to pass through the first plane where the axes of the first pipe section 241 and the second pipe section 242 of the converging pipe 240 are located, and the first branch pipe 251 and the first liquid branch pipe 251 and the first plane. The setting of the included angle between the second planes where the axis of the second branch pipe 252 is located realizes that the amount of refrigerant flowing out of the different branch pipes of the liquid separator is different, and satisfies the different requirements of the amount of refrigerant required by the branch pipe, and further 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 may be 3, 4, 5 or more, correspondingly, the number of the 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 degrees, 30 degrees, 60 degrees, 70 degrees, or 80 degrees. 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, a biased flow is realized under the action of gravity, so that the refrigerant flows into the first branch pipe 251 and the first branch pipe 251. The cooling capacity of the two branch pipes 252 is different.

Optionally, the inner diameter of the first pipe section 241 of the collecting pipe 240 is larger than the inner diameter of the first branch pipe 251 .

Optionally, the inner diameter of the first branch pipe 251 is larger than the inner diameter of the second branch pipe 252 . In the liquid separator provided by the embodiment of the present disclosure, an included angle is set between the first plane where the axes of the first pipe section 241 and the second pipe section 242 of the converging pipe 240 are located and the second plane where the axes of the two branch pipes are located. Furthermore, the difference in inner diameter between the two liquid-separating branch pipes is further matched to further increase the difference in the amount of refrigerant flowing into the two liquid-separating branch pipes. Optionally, the first pipe section 241 of the confluence pipe 240 is inclined to the side of the second branch pipe 252, then, under the action of gravity, the inner diameter of the first branch pipe 251 is further matched to be larger than the inner diameter of the second branch pipe 252, More refrigerant flows into the first branch pipe 251, which further increases the refrigerant flow difference between the two branch pipes.

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

Only by defining the difference in the inner diameters of the first branch pipe 251 and the second branch pipe 252, it is difficult to achieve a refrigerant distribution with a flow ratio of the first branch pipe 251 and the second branch pipe 252 of 3:1 or even greater. Refrigerant distribution with poor refrigerant flow. The reason is that the inner diameter of the branch pipe is limited by the minimum value. For example, the inner diameter of the branch pipe cannot be less than 3mm, or even less than 3.36mm. The flow resistance will form a throttling and depressurizing effect on the flow of the refrigerant, which will increase the power of the compressor and reduce the performance of the system; even when the air conditioner is operating under the heating condition, the outdoor heat exchanger will be seriously frosted, which will affect the performance of the system. Safety and reliability. Due to the limitation of the minimum inner diameter of the branch pipe, in order to achieve refrigerant distribution with a flow ratio of 3:1, the diameter of the other 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 heat exchange tube actually 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 defining the difference in inner diameter of the first branch pipe 251 and the second branch pipe 252, it is difficult to realize the difference between the first branch pipe 251 and the second branch pipe 252 within the allowable range of the pipe diameter of the heat exchange pipe in the heat exchanger. The refrigerant distribution with a flow ratio of the second branch pipe 252 of 3:1 or even greater 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 of the manifold 240 are located and the second plane where the axes of the two branch pipes are located, and is further matched with the two The technical solution of the difference in inner diameter between the two branch pipes, within the allowable range of the heat exchange pipe diameter of the heat exchanger, can realize the refrigerant flow ratio of the two branch pipes to be 2:1-7:1, or even higher. Large proportion of refrigerant distribution requirements, such as 2:1, 3:1, 4:1, 5:1, 6:1, 7:1. In the refrigerant distribution solution provided by the embodiment of the present disclosure to achieve a larger flow ratio, the inner diameter of the second liquid branch pipe 252 does not need to be designed to be too thin, and the flow rate of the refrigerant in the first liquid branch pipe 251 can also be realized to 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 that the total pressure drop of the liquid separator branch pipe and the heat exchanger of the liquid separator is too large when the refrigerant distribution of the two liquid separator branch pipes is relatively large.

Optionally, an included angle is set between the first plane where the axes of the first pipe section 241 and the second pipe section 242 of the manifold 240 are located and the second plane where the axes of the two branch pipes are located is greater than or equal to 50 degrees and less than or equal to 50 degrees. or equal to 70 degrees. The difference in refrigerant flow between the first branch pipe 251 and the second branch pipe 252 is improved. Optionally, the inner diameter of the first 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 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 converging pipe 240 is inclined to the side of the second branch pipe 252 .

When the air conditioner is operating in the heating condition, when the heat exchanger is used as an evaporator, the heat exchanger can exert the most ideal heat exchange capacity under the following conditions: during heating, it continuously absorbs the heat in the surrounding air from the low temperature liquid state, As the temperature rises and reaches the gas-liquid two-phase state, at this time the temperature remains unchanged at the evaporation temperature, but the phase transition from liquid to gas continues to occur, the liquid refrigerant is less and less, and the gaseous refrigerant is more and more. At the outlet of the heat exchange branch, all of them become gaseous 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 the refrigerants are gaseous refrigerants, and the enthalpy difference of the gaseous refrigerants is small, and the heat exchange capacity is low. When the temperature is about 0 to 1 °C, if the superheat degree is greater than 3 °C, the temperature is above 4 °C, and the ambient temperature in winter is about 7 °C.

The better the uniformity, the easier it is for each heat exchange branch to have proper heat exchange. If it is not uniform, it is easy for some branches to be overheated seriously, the latter few hairpin tubes have no heat exchange effect, and 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 cold energy. In this way, under the same refrigerant flow, the heat exchange effect of the entire heat exchanger is poor, and the capacity of the air conditioner is very low. . Therefore, the best judgment method for diversion during heating is as follows: the temperature difference at the outlet of each branch is within 2 °C, and the outlet superheat degree is about 1 °C. In this case, diversion is better.

Table 19

Table 20

Optionally, when the air conditioner is operating in a heating condition, 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 separation 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, and the inner diameters of the first branch pipe 251 and the second branch pipe 252 are different, the maximum value of the fourth heat exchange branch and the first three branches temperature difference and the heating capacity of the air conditioner. It can be seen from the data in Table 19 that when the inner diameter of the first branch pipe 251 is 5.6 mm, and the inner diameter of the second branch pipe 252 is 3.36 mm, the fourth heat exchange branch of the heat exchanger is the same as the first three branches. The maximum temperature difference of the branch is the smallest, which is 3.4°C, and the heating capacity of the air conditioner under this inner diameter is the largest, which is 4855.2W. Table 20 shows that when the inner diameter of the first branch pipe 251 is 5.6 mm, and the inner diameter of the second branch pipe 252 is 3.36 mm, and 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, and at this angle, the air conditioner The heating capacity of the device is the largest, which is 5016.1W.

It can be seen from the data in Table 19 and Table 20 that when the number of heat exchange branches in the heat exchanger communicated with the first branch pipe 251 is 3, the heat exchange branches communicated with the second branch pipe 252 The number of branches is 1. For example, in the heat exchanger shown in FIG. 3 , the inner diameter of the first branch pipe 251 is 5.6 mm, and the inner diameter of the second branch pipe 252 is 3.36 mm. 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 of the refrigerant in each heat exchange branch is the best. maximum thermal capacity. That is, the ratio of the amount of refrigerant in the first branch pipe 251 to the amount of refrigerant in the second branch 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, the inner diameter of the first branch pipe 251 is greater than or equal to 5.1 mm and less than or equal to 6.1 mm, and the first When the inner diameter of the second 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 branch pipe 251 to the amount of refrigerant in the second branch pipe 252 can be better achieved as 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, the inner diameter of the first branch pipe 251 is greater than or equal to 5.1 mm and less than or equal to 6.1 mm, and the first When the inner diameter of the second 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 branch pipe 251 to the amount of refrigerant in the second branch pipe 252 can be better achieved as 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 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 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 branch pipe 251 to the amount of refrigerant in the second branch pipe 252 can be better achieved as 2 :1-3:1.

Optionally, the included 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 branch pipe 251 is greater than or equal to 5.1 mm and less than or equal to 6.1 mm, and the second 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 converging pipe 240 is inclined to the side of the second branch pipe 252 .

Table 21

Table 22

Optionally, when the air conditioner operates in a heating condition, 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 with the first liquid branch pipe 251, and the sixth heat exchange branch is connected with the second liquid branch pipe 252, the refrigerant temperature at the outlet of each heat exchange branch is shown in Table 21. and shown in Table 22. Among them, Table 21 shows that when the angle between the first plane and the second plane is 90 degrees, under the different inner diameters of the first branch pipe 251 and the second branch pipe 252, the maximum value of the sixth heat exchange branch and the first five branches temperature difference and the heating capacity of the air conditioner. It can be seen from the data in Table 21 that when the inner diameter of the first branch pipe 251 is 5.6 mm, and the inner diameter of the second branch pipe 252 is 3.36 mm, the sixth heat exchange branch of the heat exchanger is the same as the first five branches. The maximum temperature difference of the branch is the smallest, which is 3.1℃, and the heating capacity of the air conditioner under this inner diameter is the largest, which is 7287.6W. Table 22 shows that when the inner diameter of the first branch pipe 251 is 5.6 mm, and the inner diameter of the second branch pipe 252 is 3.36 mm, and the angles between the first plane and the second plane are different angles, 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, and at this angle, the air conditioner The heating capacity of the device is the largest at 7383.7W.

It can be seen from the data in Table 21 and Table 22 that when the number of heat exchange branches in the heat exchanger communicated with the first branch pipe 251 is 5, the heat exchange branches communicated with the second branch pipe 252 When 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 uniformity of the heat exchange capacity 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 pipe 251 to the amount of refrigerant in the second branch pipe 252 is 5:1.

Similarly, the included 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 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 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 branch pipe 251 to the amount of refrigerant in the second branch pipe 252 can be better achieved as 5 :1. The temperature differences 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 included 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 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 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 branch pipe 251 to the amount of refrigerant in the second branch pipe 252 can be better achieved as 4 :1. The temperature differences 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 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 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 branch pipe 251 to the amount of refrigerant in the second branch pipe 252 can be better achieved to be 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 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 branch pipe 252 is greater than or equal to 8.1 mm. or equal to 3.1mm and less than or equal to 3.7mm. Optionally, the second pipe section 242 of the converging pipe 240 is inclined to the side of the second branch pipe 252 .

Table 23

Table 24

Optionally, when the air conditioner operates in a heating condition, 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, the fifth heat exchange branch and the sixth heat exchange branch are connected with the first liquid branch pipe 251, and the seventh heat exchange branch is connected with the second liquid branch pipe 252, the outlet of each heat exchange branch The temperature of the refrigerant 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, and the inner diameters of the first branch pipe 251 and the second branch pipe 252 are different, the maximum value of the seventh heat exchange branch and the first six branches temperature difference and the heating capacity of the air conditioner. It can be seen from the data in Table 23 that when the inner diameter of the first branch pipe 251 is 7.6 mm, and the inner diameter of the second branch pipe 252 is 3.36 mm, the seventh heat exchange branch of the heat exchanger is the same as the first six branches. The maximum temperature difference of the branch is the smallest, which is 5.9℃, and the heating capacity of the air conditioner under this inner diameter is the largest, which is 9268.4W. Table 24 shows that when the inner diameter of the first branch pipe 251 is 7.6 mm, and the inner diameter of the second branch pipe 252 is 3.36 mm, and the included angles between the first plane and the second plane are different angles, 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, and at this angle, the air conditioner The heating capacity of the device is the largest at 9544.5W.

It can be seen from the data in Table 23 and Table 24 that when the number of heat exchange branches in the heat exchanger communicated with the first branch pipe 251 is 6, the heat exchange branches communicated with the second 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 uniformity of the heat exchange capacity 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 pipe 251 to the amount of refrigerant in the second branch 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 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 branch pipe 252 When it 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 branch pipe 251 to the amount of refrigerant in the second branch pipe 252 can be better achieved to be 6:1. The temperature differences 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 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 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 branch pipe 252 When it 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 branch pipe 251 to the amount of refrigerant in the second branch pipe 252 can be better achieved to be 7:1. The temperature differences 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 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 branch pipe 251 is greater than or equal to 7.1 mm, and less than or equal to 8.1 mm, and the diameter of the second branch pipe 252 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 branch pipe 251 to the amount of refrigerant in the second branch pipe 252 can be better achieved to be 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 included angle between the first plane and the second plane is 0 degrees. Optionally, the inner diameter of the first branch pipe 251 is larger than the inner diameter of the second branch pipe 252, and the second pipe section 242 of the converging pipe 240 is inclined to the side of the second branch pipe 252, so that more refrigerant acts on the gravity. The flow downward into the first branch pipe 251 increases the flow difference of the refrigerant in the first branch pipe 251 and the second branch pipe 252 .

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

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

Optionally, the length of the first pipe section 241 is less than or equal to 10 cm. Optionally, the length of the first pipe section 241 is 3 cm, 4 cm, 5 cm, 6 cm, 7 cm, 8 cm or 9 cm, or the like. 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 the centrifugal force, thereby helping to realize that the liquid distribution volume of the first liquid distribution port is greater than that of the first liquid distribution port. The demand for the dispensing volume of the second dispensing port. If the length of the first pipe section 241 is greater than 10 cm, because the flow distance is too long, for example, 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 that the liquid distribution volume of the first liquid distribution port is greater than The demand for the dispensing volume of the second dispensing port.

Optionally, the length of the first pipe section 241 is less than or equal to 5 cm. Optionally, the length of the first pipe section 241 may be 2 cm, 2.5 cm, 3 cm, 3.5 cm, 4 cm, 4.2 cm, 4.5 cm, or 5 cm, or the like. When the length of the first pipe section 241 is less than or equal to 5 cm, the refrigerant entering the first pipe section 241 from the second pipe section 242 tends to be deflected to the first liquid separation port due to centrifugal force, which is more conducive to realizing the first liquid separation port. The dispensing volume is greater than the demand for the dispensing volume of the second dispensing port.

Optionally, the inner diameter of the second branch pipe 252 is greater than or equal to 3 mm. Optionally, the inner diameter of the second branch pipe 252 is 3 mm, 3.36 mm, 5 mm, 10 mm, 12 mm, or the like. As mentioned above, the inner diameter of the branch pipe is limited by the minimum value. For example, the inner diameter of the branch pipe cannot be less than 3mm, or even less than 3.36mm. The copper pipe below this inner diameter has actually become a capillary, and the capillary has a larger The flow resistance will form a throttling and depressurizing effect on the flow of the refrigerant, which will increase the power of the compressor and reduce the performance of the system; even when the air conditioner is operating under the heating condition, the outdoor heat exchanger will be seriously frosted, which will affect the performance of the system. Safety and reliability. In the embodiment of the present disclosure, the inner diameter of the second branch pipe 252 is greater than or equal to 3 mm, which reduces the flow resistance of the refrigerant in the second branch pipe 252 and improves the performance of the air conditioning system.

Optionally, the ratio of the cross-sectional area of the first branch pipe 251 to the cross-sectional area of the second branch pipe 252 is less than or equal to x. Among them, x is the default value. Optionally, x may be determined according to the number of the heat exchange branch pipes that communicate with the first branch pipe 251 and the second branch pipe 252 respectively.

Optionally, the numerical 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. Optionally, the ratio of the numbers of the heat exchange branches communicating with the first branch pipe 251 and the second branch pipe 252 respectively is less than 2. Optionally, the number of heat exchange branches communicating with the first branch pipe 251 is 3, and the number of heat exchange branches communicating with the second branch pipe 252 is 2; The number of heat exchange branches communicated with 251 is 4, and the number of heat exchange branches communicated with the second branch pipe 252 is 3; optionally, the number of heat exchange branches communicated with the first branch pipe 251 is 5. The number of heat exchange branches that communicate with the second branch pipe 252 is 4; optionally, the number of heat exchange branches that communicate with the first branch pipe 251 is 5, and the number of branches that communicate with the second branch pipe 252 is 5. The number of heat exchange branches is 3, etc.

Optionally, the ratio of the cross-sectional area of the first branch pipe 251 to the cross-sectional area of the second branch pipe 252 is greater than x. Among them, x is the default value. Optionally, the numerical 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 numbers of the heat exchange branch pipes communicating with the first liquid branching branch pipe 251 and the second liquid branching branch pipe 252 respectively is greater than or equal to 2. For example, the ratio of the number of heat exchange branch pipes communicating with the first branch pipe 251 and the second 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 branch pipe 251 to the cross-sectional area of the second branch pipe 252 is less than or equal to y. Wherein, y is a preset value greater than x.

Optionally, the numerical range of y is: 2≤y≤15. Optionally, the value of y may be 2, 3, 4, 9, 10, 11, 12, 14, or 15. Optionally, the ratio of the numbers of the heat exchange branch pipes communicating with the first liquid branching branch pipe 251 and the second liquid branching branch pipe 252 respectively is greater than or equal to 2. For example, the ratio of the number of heat exchange branch pipes communicating with the first branch pipe 251 and the second 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-part liquid branch pipe shall not be less than 3mm, or even 3.36mm, and the inner diameter of the copper pipe used in the heat exchanger of the current air conditioner generally does not exceed 10.6mm. Optionally, in order to better prepare the dispenser, the ratio of the cross-sectional area of the first branch pipe 251 to the cross-sectional area of the second branch pipe 252 is less than or equal to 2.

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

Optionally, the first pipe section 241 is disposed on the side of the second branch pipe 252 .

Optionally, the included angle α between the first pipe section 241 and the casing is 30-75 degrees. Optionally, the included angle α between the first pipe section 241 and the casing is 30 degrees, 35 degrees, 40 degrees, 45 degrees, 50 degrees, 60 degrees, 70 degrees or 75 degrees. When the angle between the first pipe section 241 and the shell is 50 degrees, the simulation effect diagram of the refrigerant flowing in the liquid separator is shown in FIG. 22 . It can be seen from Figure 22 that when the angle between the first pipe section 241 and the casing is 50 degrees, the amount of refrigerant flowing into the first branch pipe 251 is much larger than the amount of refrigerant flowing into the second branch pipe 252. The effect of uneven distribution between the first branch pipe 251 and the second branch pipe 252 is better. When the angle between the first pipe section 241 and the shell is 80 degrees, the simulation effect diagram of the 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 casing is 80 degrees, the amount of refrigerant flowing into the first branch pipe 251 is not much different from the amount of refrigerant flowing into the second branch pipe 252 .

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

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

Optionally, the first area where the first branch cavity 235 communicates with the confluence cavity 234 is larger than the second area where the second branch cavity 236 communicates with the confluence cavity 234 . In this way, more refrigerant can flow into the first branch pipe 251 through the first branch cavity 235 , thereby increasing the difference in the amount of refrigerant flowing into the two 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 numerical range of z is: 2≤z≤15. Optionally, the value of z may be 2, 3, 5, 8, 9, 10, or 12. Optionally, the ratio of the numbers of the heat exchange branch pipes communicating with the first liquid branching branch pipe 251 and the second liquid branching branch pipe 252 respectively is greater than or equal to 2. For example, the ratio of the number of heat exchange branch pipes communicating with the first branch pipe 251 and the second 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-part liquid branch pipe shall not be less than 3mm, or even 3.36mm, and the inner diameter of the copper pipe used in the heat exchanger of the current air conditioner generally does not exceed 10.6mm. Optionally, in order to better prepare the dispenser, the ratio of the cross-sectional area of the first branch pipe 251 to the cross-sectional area of the second branch pipe 252 is less than or equal to 2.

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

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

Optionally, the cross-section of the manifold 240 includes straight segments. The cross section of the collecting pipe 240 includes one or more straight line segments, optionally, the straight line segments are provided at the place that communicates with the second branch cavity 236 .

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

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

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

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

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

Optionally, the length of the first branch pipe 251 extending into the liquid distribution chamber is smaller than the length of the second branch pipe 252 extending into the liquid distribution chamber. As shown in Figure 19. The part of the second branch pipe 252 that protrudes into the liquid separation chamber is relatively long, and the flow of the refrigerant into the second branch pipe 252 is reduced, so that the amount of refrigerant flowing into the first branch pipe 251 and the second branch pipe 252 is reduced. different. A schematic diagram of the flow distribution of the refrigerant in the first branch pipe 251 and the second 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 converging pipe 240 is disposed on one side of the casing, so that the flow rates of the refrigerant flowing into the first branch pipe 251 and the second branch pipe 252 are different.

Optionally, the first axis of the manifold 240 is between the second axis of the first branch pipe 251 and the third axis of the second 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 branch pipe 251 and the second branch pipe 252 at the same time.

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

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

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

Optionally, the number of heat exchange branches communicated with the first branch pipe 251 is greater than the number of heat exchange branches communicated with the second branch pipe 252; or, the number of heat exchange branches communicated with the first branch pipe The ratio of the number to the number of the heat exchange branch pipes communicated with the second liquid separation branch pipe is greater than 1 and less than 2; 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 branch pipe 251 of the first liquid separator 211 is greater than or equal to two. The number of heat exchange branches communicating with the second branch pipe 252 of the first liquid separator 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 line 151 and a first one-way valve 311. One end of the first heat exchange branch 121 is connected to the second liquid separator 212; one end of the second heat exchange branch 122 is connected to the second liquid separator 212; one end of the fourth heat exchange branch 124 is connected to the first liquid separator The first bypass line 151 is connected to the first liquid separator 211 and the second liquid separator 212, the first one-way valve 311 is arranged in the first bypass line 151, and the first one-way valve 311 The conduction direction is defined to flow from the first dispenser 211 to the second dispenser 212 .

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

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 gas header, and the flow 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, in the downward direction of the cooling flow, due to the arrangement of the first one-way valve 311 and the second one-way valve 312, the length of the downward refrigerant path of the cooling flow is increased, and the length of the cooling medium in the heat exchange is prolonged. The heat exchange time in the heat exchanger enables the refrigerant to fully exchange heat with the surrounding environment, and the refrigerant flows through fewer branches and the flow velocity is faster, which improves the heat exchange effect of the heat exchanger, thereby improving the cooling efficiency of the air conditioner. .

Optionally, when the heating flow is downward, the refrigerant is divided into four paths. The first branch passes through the first one-way valve 311 and the second liquid separator 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 and the second liquid separator 212, flows through the second heat exchange branch 122, and flows out after passing through 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 flows out 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, The third liquid separator 213, the second one-way valve 312, and the gas collecting pipe flow out afterward. It can be seen that in the heat exchanger provided by the embodiment of the present disclosure, due to the arrangement 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 many branches, which avoids the pressure loss problem caused by the long flow path, improves the heat exchange efficiency of the heat exchanger, and further improves the performance of the air conditioner. Heating efficiency.

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

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

Optionally, the value of a1 ranges from 0.3 to 0.8.

For the liquid distributor in the embodiment of the present disclosure, on the one hand, the liquid distribution branch pipe needs to be inserted into the liquid distributor to a certain depth, and the specific depth depends on the actual size of the liquid distributor; take the model of the embodiment with a rated cooling capacity of 3.5KW 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 branch pipe, bends 180°, and then flows out from the last branch pipe, and the lower end of the branch pipe reaches the liquid branch cavity The bottom needs to meet a certain length, generally at least about 1R, and the aspect 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 taken as 0.3 ~0.8.

In this example, the three-way split is used for separation, and the performance data of the liquid distributor with the above-mentioned lower limit of the aspect ratio and the liquid distributor beyond the lower limit of the aspect ratio are tested respectively, and the test condition is indoor working condition 27 ℃ /19°C, outdoor working condition is 35°C/24°C, other operating states of the air conditioner are the same, and the test data is shown in Table 25 below:

Table 25

Aspect ratio ability power efficiency 0.2 3379.8W 888.7W 3.80 0.5 3436.3W 863.7W 3.98

It can be seen from the above table that when the aspect ratio is less than the minimum value 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 In this case, the air conditioner can achieve better operating energy efficiency.

The use of the lower limit of the aspect ratio of the liquid separation chamber defined in this embodiment can avoid the problem of excessive accumulation of refrigerant in the liquid separator and affect the refrigerant circulation of the air conditioner, and can also effectively reduce power loss.

Optionally, the length L1 of the liquid separation chamber 230 is greater than or equal to 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 dispenser is 1.7-7 cm.

In some other embodiments, the height reserved space of the dispenser is usually within 10cm, while the diameter of the dispenser is generally more than 2cm, so the two limiting conditions determine that the length-diameter ratio of the dispenser is generally within 5; in addition, In order to achieve liquid storage, our dispenser must have a certain volume. According to the same height, the longer the dispenser is, the smaller the volume will be. There is also an influencing factor. The distance is very close, and it is easy to influence each other and eventually affect the flow. In a slender 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 separator, and the smaller the liquid storage capacity. The less; the larger the aspect ratio, the more slender the liquid separator is, and the closer the distance between each liquid distribution branch is, it is easy to influence each other and affect the final distribution effect; at the same time, the refrigerant flows from the liquid distribution branch pipe and bends 180° and then flow out from other branch pipes. If the dispenser is too slender, the flow process will be affected by the side wall of the dispenser chamber; and when the diameter of the dispenser is constant, the larger the aspect ratio, the greater the distribution. The higher the height of the device, the more space is occupied in the tube group, and it is difficult to be compatible. Therefore, considering comprehensively, the upper limit a2 of the length-diameter ratio of the liquid-separating chamber cannot be too large, and the length-diameter ratio L1/D≤a2 of the liquid-separating chamber 230 . a2 is a second preset ratio value greater than a1.

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

也即

Another optional,

that is

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

Exemplarily, in this embodiment, the separation is performed in the form of four-way splitting, and the performance data of the liquid distributor defined by the above-mentioned lower limit of the aspect ratio and the liquid distributor exceeding the lower limit of the aspect ratio are respectively tested, and the test conditions are indoors. The working condition is 27°C/19°C, and the outdoor working condition is 35°C/24°C. The other operating conditions of the air conditioner are the same. The test data is shown in Table 26 below:

Table 26

Aspect ratio ability power efficiency 2.8 3421.6W 865.1W 3.96 4.3 3387.1W 905.7W 3.74

It can be seen from the above table that when the aspect ratio is greater than the maximum value of the upper limit value of 3, the air conditioner has lower energy efficiency when the power is larger, and when the aspect ratio is less than the maximum value of the upper limit value of 3 In this case, the air conditioner can achieve better operating energy efficiency.

Optionally, the length L1≤b2 of the liquid separation chamber 230, where 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 dispenser is 1.7-7 cm.

Optionally, as shown in FIGS. 26 to 28 , the liquid distribution chamber 230 includes a first liquid storage chamber 231 communicating with the manifold 240 and a second liquid storage chamber 232 communicating with 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 communicated through a liquid storage chamber channel 233 with a narrowed diameter.

The beneficial effect of adopting the above scheme design is: when the heat exchanger is used as a condenser, the refrigerant 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 a confluence and a split flow 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, which has 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 separation chamber, and the sealing performance is better; in the heat exchanger as an evaporation When the refrigerant is in use, the refrigerant flows in the reverse direction, which can make more refrigerants participate in the circulation and meet the needs of refrigerant circulation. At the same time, the first liquid storage chamber can also function as a silencer to eliminate the noise of refrigerant flow.

Optionally, the volume of 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, so as to increase the liquid storage capacity; meanwhile, the first liquid storage chamber is set in the form of a larger volume, It can also improve the buffering effect on the flow of refrigerant, and use a larger cavity for noise reduction when used as a "silencer".

Optionally, the volume of the first liquid storage chamber 231 is v1=c1*Q, where 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 of c1 ranges from 3 to 10.

Optionally, the volume of the second liquid storage chamber 232 is v2=c2*Q, where 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 of c2 ranges from 1.5 to 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 refrigerant density is higher, and the quality of the refrigerant stored in the same volume is higher; the second liquid storage chamber 232 It mainly accommodates gas-liquid mixed refrigerant, the refrigerant density is low, and the quality of the refrigerant stored in the same volume is low; in order to meet the capacity requirement of the aforementioned liquid separator, the liquid storage needs to reach about 5% of the total filling volume, so according to the test When the air conditioner operates at different loads, the density of the refrigerant in the two liquid storage chambers is changed, and the volume range ratio of the first liquid storage chamber and the second liquid storage chamber is set respectively, so that the first liquid storage chamber 231 can be used to accommodate more Multi-quality refrigerant, so that the sum of the refrigerant storage capacity of the first liquid storage chamber 231 and the second liquid storage chamber 232 can meet the above capacity requirement.

Optionally, the liquid storage cavity channel 233 includes a circular tube section, and the two ports of the circular tube section are configured as conical openings with a diameter gradually expanding outward. The conical opening design can facilitate the refrigerant to pass between the liquid storage cavity channel and the liquid storage cavity. Smoother flow, reducing problems such as turbulence caused by changes in flow area during the flow of the two.

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

Optionally, the pipe diameter of the liquid storage cavity channel 233 is greater than or equal to the pipe diameter of the confluence pipe 240. In this embodiment, when the heat exchanger is used as an evaporator, the refrigerant flowing through the confluence pipe and the liquid separation can be reduced. The flow resistance in the liquid separation process of the heat exchanger is accelerated, and the flow of the refrigerant is accelerated to ensure the heat exchange performance of the heat exchanger.

Exemplarily, in this embodiment, taking an air conditioner with a rated cooling capacity of 7.2Kw as an example, the use of the ordinary liquid separator and the use of the liquid separator to be protected by this application are 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 energy efficiency COP of the air conditioner of the present application is higher than the test data of the air conditioner using the 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 gas-liquid dispersion of the refrigerant flowing through the liquid separation chamber 230 .

In this embodiment, as shown in FIG. 30 , the mesh member 260 is mainly used to break up larger droplets and bubbles to form a turbulent flow area, and the gas-liquid two-phase refrigerant mixed after breaking needs to be processed 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 uneven distribution of the gas-liquid two-phase refrigerant flowing through the converging pipe flows into the liquid-separating branch pipe evenly.

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

Optionally, the mesh 260 is arranged at a position 1/2 of the height of the dispenser.

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

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

Table 28

As shown in the above table, the smaller the number of pores, the larger the pore size, and the more difficult it is to break up large droplets and bubbles, while too many pores will cause the pressure drop to be too large, which is not conducive to the flow of refrigerant. Therefore, 60-120 mesh wire mesh is selected.

At the same time, through the simulation analysis of the mesh parts with different number of holes and wire diameters in the same specification of the dispenser, the simulation test data are shown in Figures 31 and 32, in which the unevenness of the fluid flowing through the mesh parts of 80 and 100 meshes , the instability is kept at a low level, and is lower than the Venturi distributor, so the preferred mesh has a porosity of 100 mesh and a wire diameter of 0.1 mm. are minimum values.

As shown in FIGS. 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 valve core 330 is axially movably disposed in the valve passage, so as to realize on/off switching of the one-way valve.

35, the length between the two ends of the valve core 330 is set as L2, and the equivalent diameter of the end face of the valve core 330 corresponding to one end of the valve outlet 322 is D.

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

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

Still alternatively, 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 for the length-diameter ratio of the one-way valve spool, it can also play the role of reducing wall vibration, collision and noise, so that the spool can maintain good 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 common one-way valve and the one-way valve to be protected by the present application are tested respectively, and the test condition is that 0.05MPa nitrogen gas is introduced into the lower port of the valve core. , 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

From the comparison of the above data, it can be seen that when the length-diameter ratio of the valve core L2/D (e=0.45) is less than e1 or L2/D (e=2.32) is greater than e2, there is a slight abnormal sound of the valve core hitting the positioning pin. The noise test results were poor, while the measured noise was lower when the spool L/D ratio was in the range of e1 and e2, enabling low-noise operation.

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 arranged at the end of the valve core can increase the contact area between the superheated refrigerant and the end face of the valve core, and increase the force 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 of refrigerant, which can improve the stability of valve core closing

Optionally, as shown in FIGS. 36 , 37 a and 37 b , the hollow structure includes a hollow groove 335 formed axially inward from the end face of the first end.

Optionally, the radial cross-section of the hollow groove 335 is circular, rhombic or triangular.

Optionally, the groove bottom of the hollow groove 335 is configured to be planar or concavely conical. .

In some optional embodiments, the design parameters of the hollow slot 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, V2 are the volume of the hollow groove, and V1 is the solid volume of the valve core.

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

Table 31

Spool form plum blossom spool Cube solid spool Spool with hollow groove Refrigerant leakage 257ml/min 143ml/min 91ml/min

From the comparison of the above data, it can be seen that the valve core with the hollow groove used in the present application has lower refrigerant leakage and better sealing effect.

In some other 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 valve outlet side and a conical section near the valve inlet side, wherein the hollow cavity 336 is mainly formed in the cylindrical section.

The hollow cavity 336 can play a role in reducing the weight of the cylindrical section of the valve core, so that the center of gravity of the valve core as a whole moves down, and the gravity can be more concentrated on the conical section, which is conducive to maintaining the stability of the valve core during the sealing process of the valve core.

Optionally, the cross section of the cylindrical section of the valve core 330 is square or circular.

Optionally, the radial cross-section of the hollow cavity 336 is circular. The value range of the ratio of the radius of the hollow cavity to the radius of the valve core is 1/4 to 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 other optional embodiments, as shown in FIGS. 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 smaller than that of the stabilizing block 334.

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

In this embodiment, since the density of the stabilizing block 334 is higher, it can play the role of aggravating 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 is not limited to, iron or copper.

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

The foregoing description and drawings sufficiently illustrate the embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The examples represent only possible variations. Unless expressly required, individual components and functions are optional 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 accompanying 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 (19)

1. a liquid separator, is characterized in that, comprises: The shell has a liquid-separating cavity inside, and is provided with a first liquid-separating port and a second liquid-separating port; a first branch pipe for liquid distribution, which penetrates through the first liquid distribution port and communicates with the liquid distribution chamber; and, a second branch pipe for liquid distribution, which runs through the second liquid distribution port and communicates with the liquid distribution chamber; Wherein, the axis of the first branch pipe is non-parallel to the center line of the liquid distribution chamber, and/or the axis of the second branch pipe is not parallel to the center line of the liquid distribution chamber. 2. The dispenser according to claim 1, characterized in that, The axis of the first branch pipe forms a first included angle with the centerline of the liquid separation chamber, The axis of the second branch pipe forms a second included angle with the centerline of the liquid separation chamber, Wherein, the angles of the first included angle and the second included angle are not equal. 3. The dispenser according to claim 1 or 2, characterized in that, The inner diameter of the first branch pipe is larger than the inner diameter of the second branch pipe. 4. The dispenser of claim 3, further comprising: a manifold, communicated with the liquid separation chamber, Wherein, the inner diameter of the confluence pipe is larger than the inner diameter of the first branch pipe. 5. The dispenser according to claim 4, characterized in that, The collecting pipe includes a first pipe section and a second pipe section that are connected by bending, and the first pipe section is directly communicated 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 branch pipe and the second branch pipe are located is the second plane, and the first plane is the same as the first plane. The second plane is not vertical. 6. The dispenser according to claim 5, characterized in that, The second pipe section is arranged offset to the side of the second branch pipe. 7. The dispenser according to claim 6, characterized in that, The included 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; or, The included 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. 8. The dispenser according to claim 7, characterized in that, The inner diameter of the first branch pipe is greater than or equal to 5.1mm and less than or equal to 6.1mm; The inner diameter of the second branch pipe is greater than or equal to 3.1 mm and less than or equal to 3.7 mm. 9. The dispenser according to claim 6, characterized in that, The included angle between the first plane and the second plane is less than or equal to 10 degrees. 10. The dispenser according to claim 9, characterized in that, The inner diameter of the first branch pipe is greater than or equal to 7.1mm and less than or equal to 8.1mm; The inner diameter of the second branch pipe is greater than or equal to 3.1 mm and less than or equal to 3.7 mm. 11. A heat exchanger, characterized by comprising the liquid separator according to any one of claims 1 to 10. 12. The heat exchanger of claim 11, further comprising: The first refrigerant inlet and outlet; A second refrigerant inlet and outlet; and, A plurality of heat exchange branches connected in parallel are connected between the first refrigerant inlet and outlet and the second refrigerant inlet and outlet, Wherein, when the heat exchanger is used as an evaporator, the refrigerant flows in through the first refrigerant inlet and outlet, and flows out through the second refrigerant inlet and outlet, and the liquid separator is arranged at the first refrigerant inlet and outlet, so The confluence pipe of the liquid separator is communicated with the first refrigerant inlet and outlet, and the number of heat exchange branches communicated with the first liquid split branch pipe is not the same as the number of heat exchange branches communicated with the second liquid split branch pipe. same. 13. The heat exchanger of claim 12, wherein The number of heat exchange branches communicated with the first liquid separation branch pipe is greater than the number of heat exchange branches communicated with the second liquid separation branch pipe. 14. The heat exchanger of claim 12, wherein The ratio of the number of the heat exchange branch pipes communicating with the first liquid-separating branch pipe to the number of the heat-exchanging branch pipes communicating with the second liquid-separating branch pipe is greater than 1 and less than 2. 15. The heat exchanger of claim 12, wherein The ratio of the number of the heat exchange branch pipes communicating with the first liquid-separating branch pipe to the number of the heat-exchanging branch pipes communicating with the second liquid-separating branch pipe is greater than or equal to 2. 16. The heat exchanger according to claim 11, wherein when the liquid separator is used as the first liquid separator, the heat exchanger further comprises: The first heat exchange branch is connected with the second liquid separator at one end; The second heat exchange branch is connected to the second liquid separator at one end; the fourth heat exchange branch, one end is connected with the first liquid separator; The first bypass pipeline is connected to the first liquid separator and the second liquid separator, The first one-way valve is arranged in the first bypass pipeline, and the conduction direction of the first one-way valve is limited to flow from the first liquid separator to the second liquid separator. 17. The heat exchanger according to claim 11, wherein when the liquid separator is used as the first liquid separator, the heat exchanger further comprises: gas collecting pipe; the first heat exchange branch, the first end is connected with the first nozzle of the gas collecting pipe, and the second end is connected with the second liquid separator; The second heat exchange branch, the first end is connected with the second nozzle of the gas collecting pipe, and the second end is connected with the second liquid separator; The third heat exchange branch, the first end is connected with the third liquid separator, and the second end is connected with the first liquid separator; the fourth heat exchange branch, the first end is connected with the third liquid separator, and the second end is connected with the first liquid separator; a first bypass pipeline, connecting the first dispenser and the second dispenser; The second bypass pipeline is connected to the third liquid separator and the gas collecting pipe; a first one-way valve, arranged in the first bypass pipeline, and the conduction direction of the first one-way valve is limited to flow from the first liquid distributor to the second liquid distributor; A second one-way valve is arranged on the second bypass pipeline, and the conduction direction of the second one-way valve is limited to flow from the third liquid separator to the gas collecting pipe. 18. A refrigeration cycle system, comprising: A heat exchanger as claimed in any one of claims 11 to 17. 19. An air conditioner, comprising: The refrigeration cycle system of claim 18.

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