CN216745002U

CN216745002U - Heat exchanger, refrigeration cycle system and air conditioner

Info

Publication number: CN216745002U
Application number: CN202122677123.7U
Authority: CN
Inventors: 国德防; 王飞; 吴洪金; 张鹏; 丁爽; 张心怡; 李阳
Original assignee: Qingdao Haier Air Conditioner Gen Corp Ltd; Qingdao Haier Air Conditioning Electric Co Ltd; Haier Smart Home Co Ltd
Current assignee: Qingdao Haier Air Conditioner Gen Corp Ltd; Qingdao Haier Air Conditioning Electric Co Ltd; Haier Smart Home Co Ltd
Priority date: 2021-09-19
Filing date: 2021-11-03
Publication date: 2022-06-14
Anticipated expiration: 2031-11-03
Also published as: CN216745039U; CN216694092U; CN216716633U; CN216716632U; CN216716652U; CN216745040U; CN216868874U; CN216694094U; CN216745003U; CN216745034U; CN218722422U; CN216814688U; CN216745038U; CN216694093U; CN216745023U

Abstract

The application relates to the technical field of air conditioning, and discloses a heat exchanger, includes: the heat exchanger main body is provided with two refrigerant inlets and outlets and a plurality of heat exchange branches; the liquid separating and storing device is provided with a confluence pipe orifice and a plurality of liquid separating orifices; the one-way conduction device is communicated between the refrigerant inlet and outlet and the confluence pipe orifice, and the flow direction of the one-way conduction device is limited to be conducted under the condition that the heat exchanger is used as an evaporator and blocked under the condition that the heat exchanger is used as a condenser; the flow dividing and liquid storing device is configured to divide the refrigerant conveyed by the refrigerant inlet and outlet to the plurality of heat exchange branches under the condition that the heat exchanger serves as an evaporator, and converge and store the liquid under the condition that the heat exchanger serves as a condenser. The heat exchanger that this disclosed embodiment provided utilizes reposition of redundant personnel stock solution device can store partial refrigerant through the cooperation of reposition of redundant personnel stock solution device and one-way conduction device to make the heat exchanger also can possess certain stock solution function. The application also discloses a refrigeration cycle system and an air conditioner.

Description

Heat exchanger, refrigeration cycle system and air conditioner

The priority of chinese patent application entitled "dispenser, check valve, heat exchanger, refrigeration cycle system, air conditioner," filed in 2021, No. 9/19, application No. 202122281454.9, is hereby incorporated by reference in its entirety.

The priority of the chinese patent application entitled "dispenser, check valve, heat exchanger, refrigeration cycle system, air conditioner," filed on 2021, No. 9/20, application No. 202111102583.5, is incorporated herein by reference in its entirety.

Technical Field

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

Background

Along with the improvement of living standard of people, more and more families can dispose the air conditioner in the house environment, generally, current air conditioner product mostly has the dual-functional mode of refrigeration/heating, and the air conditioner can operate the refrigeration function in summer high temperature weather and discharge the heat in the indoor environment to outdoor environment to and operate the heating function in winter severe cold weather and guide the heat in the outdoor environment to indoor environment, thereby satisfy the indoor environment temperature demand of user under different weather, climatic conditions. The air conditioner realizes the heat transmission between indoor and outdoor environments by taking refrigerants such as alkanes and inorganic compounds as heat storage working media, for example, the refrigerant absorbs heat when flowing through the outdoor side in a refrigeration mode and transmits the heat to the indoor side to release the heat, and the refrigerant absorbs heat when flowing through the indoor side in a heating mode and transmits the heat to the outdoor side to release the heat.

When the air conditioner is used, the refrigerant circulation amounts of the two functional modes for heat circulation are different, and under the normal condition, the refrigerant circulation amount during heating operation is larger than that during refrigerating operation; meanwhile, the actual refrigerant circulation amount is also affected by the air conditioning load in the single function mode, and generally, the refrigerant circulation amount required by the air conditioner in the partial load state is obviously less than that in the 100% full load state.

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:

when the air conditioner operates in different functional modes or different loads, redundant refrigerant which is not used for heat circulation in the air conditioner can only be stored in the liquid accumulator, so that the refrigerant storage capacity of the air conditioner is limited by the volume size of the liquid accumulator, and the adjustment requirement of the air conditioner on the refrigerant circulation capacity in different operating states is influenced.

SUMMERY OF THE UTILITY MODEL

The following presents a simplified summary in order to provide a basic understanding of some aspects of the disclosed embodiments. This summary is not an extensive overview and is intended to neither identify key/critical elements nor delineate the scope of such embodiments, but is intended to be a prelude to the more detailed description that is presented later.

The disclosed embodiment provides a heat exchanger, includes:

the heat exchanger main body is provided with two refrigerant inlets and outlets and a plurality of heat exchange branches communicated between the two refrigerant inlets and outlets;

the liquid separating and storing device is provided with a confluence pipe orifice communicated with a refrigerant inlet and a refrigerant outlet and a plurality of liquid separating ports communicated with the plurality of heat exchange branches one by one;

the one-way conduction device is communicated between the refrigerant inlet and outlet and the confluence pipe orifice, and the flow direction of the one-way conduction device is limited to be conducted under the condition that the heat exchanger is used as an evaporator and blocked under the condition that the heat exchanger is used as a condenser;

the flow dividing and liquid storing device is configured to divide the refrigerant conveyed by the refrigerant inlet and outlet to the plurality of heat exchange branches under the condition that the heat exchanger serves as an evaporator, and converge and store the liquid under the condition that the heat exchanger serves as a condenser.

The disclosed embodiments provide a refrigeration cycle system including a heat exchanger as shown in the above disclosed embodiments.

The embodiment of the present disclosure provides an air conditioner including a heat exchanger or a refrigeration cycle system as shown in the above-described embodiments of the present disclosure.

The embodiment of the utility model provides a heat exchanger, refrigeration cycle system, the air conditioner, wherein the heat exchanger is through the cooperation of reposition of redundant personnel stock solution device and one-way conduction device, utilize reposition of redundant personnel stock solution device can store partial refrigerant, thereby make the heat exchanger also can possess certain stock solution function, compare in the form that current air conditioner only utilized the reservoir stock solution, the refrigerant stock solution scope of air conditioner can be enlarged to this embodiment, especially the heat cycle that can reduce unnecessary refrigerant under the low-load state, make the actual refrigerant circulation volume of air conditioner can with current working property looks adaptation, the air conditioner has been promoted the control range to refrigerant circulation volume under different running state.

The foregoing general description and the following description are exemplary and explanatory only and are not restrictive of the application.

Drawings

One or more embodiments are illustrated by way of example in the accompanying drawings, which correspond to the accompanying drawings and not in limitation thereof, in which elements having the same reference numeral designations are shown as like elements and not in limitation thereof, and wherein:

FIG. 1 is a schematic diagram of a heat exchanger according to an embodiment of the present disclosure;

FIG. 2 is a partial schematic view of a one-way valve provided by embodiments of the present disclosure;

FIG. 3 is a schematic structural diagram of another heat exchanger provided by the disclosed embodiment;

FIG. 4 is a schematic structural diagram of another heat exchanger provided by the disclosed embodiment;

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

FIG. 6 is a schematic diagram of a heat exchange flow path in the case of a heat exchanger as an evaporator according to an embodiment of the present disclosure;

FIG. 7 is a schematic diagram of a heat exchange flow path in the case where one of the heat exchangers provided by the embodiments of the present disclosure is used as a condenser;

FIG. 8 is a schematic diagram illustrating the distribution of heat exchange tubes of a heat exchanger according to an embodiment of the present disclosure;

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

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

FIG. 11 is a schematic diagram of a tilted dispenser according to an embodiment of the present disclosure;

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

FIG. 13 is a schematic end view of a dispenser according to an embodiment of the present disclosure;

FIG. 14 is a schematic structural view of another liquid dispenser provided in an embodiment of the present disclosure;

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

FIG. 16 is a schematic structural view of another liquid distributor provided in the embodiments of the present disclosure;

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

FIG. 18 is a schematic structural view of another dispenser provided in accordance with an embodiment of the present disclosure;

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

FIG. 20 is a schematic structural view of another dispenser provided in accordance with an embodiment of the present disclosure;

FIG. 21 is a schematic structural view of another dispenser provided in accordance with an embodiment of the present disclosure;

fig. 22 is a simulation diagram illustrating a flow distribution of refrigerant in a liquid separator according to an embodiment of the disclosure;

fig. 23 is a simulation view illustrating a flow distribution of a refrigerant in another liquid separator according to an embodiment of the present disclosure;

fig. 24 is a schematic view illustrating the flow distribution of the refrigerant in the liquid separator according to the embodiment of the disclosure;

FIG. 25 is a perspective view of a dispenser according to embodiments of the present disclosure;

fig. 26 is a perspective view of another dispenser provided in accordance with an embodiment of the present disclosure;

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

FIG. 28 is a sectional view taken along line A-A of FIG. 27;

fig. 29 is a cross-sectional view of another dispenser provided in accordance with an embodiment of the present disclosure;

FIG. 30 is a diagram illustrating the effects of a divider according to an embodiment of the present disclosure;

FIG. 31 is a graph illustrating the contrast in non-uniformity when the mesh members of different mesh sizes are split as provided by embodiments of the present disclosure;

FIG. 32 is a graph comparing instability when diverging for mesh with different mesh sizes provided by embodiments of the present disclosure;

FIG. 33 is a schematic cross-sectional view of a one-way valve provided by embodiments of the present disclosure;

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

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

FIG. 35 is a schematic view of a check valve cartridge provided by embodiments of the present disclosure;

FIG. 36 is a perspective view of another check valve cartridge provided by embodiments of the present disclosure;

FIG. 37a is a cross-sectional view of another check valve cartridge provided in accordance with an embodiment of the present disclosure;

FIG. 37b is a cross-sectional view of another check valve cartridge provided in accordance with an embodiment of the present disclosure;

FIG. 37c is a cross-sectional view of another check valve cartridge provided in accordance with an embodiment of the present disclosure;

FIG. 37d is a cross-sectional view of another check valve cartridge provided in accordance with an embodiment of the present disclosure;

fig. 37e is a cross-sectional view of another one-way valve cartridge provided in accordance with an embodiment of the present disclosure.

Reference numerals:

100: a heat exchanger; 200: a liquid separator; 300: a one-way valve; 110: a refrigerant inlet and outlet; 120: a heat exchange branch; 130: a heat exchange flow path; 140: a heat exchange pipe; 151: a first bypass line; 152: a second bypass line; 220: a housing; 230: a liquid separation cavity; 240: a collector pipe; 250: a branch liquid separating pipe; 260: a mesh; 320: a valve housing; 330: a valve core; 340: a valve seat; 111: a first refrigerant inlet and outlet; 112: a second refrigerant inlet and outlet; 121: a first heat exchange branch; 122: a second heat exchange branch; 123: a third heat exchange branch; 124: a fourth heat exchange branch; 211: a first liquid separator; 212: a second liquid separator; 213: a third liquid distributor; 214: a fourth liquid distributor; 221: a liquid separation port; 222: a flow converging port; 231: a first reservoir chamber; 232: a second reservoir chamber; 233: a reservoir channel; 234: a converging cavity; 235: a first branch chamber; 236: a second branch chamber; 240: a collector pipe; 241: a first tube section; 242: a second tube section; 251: a first branch liquid-separating pipe; 252: a second branch pipe; 253: a third liquid distribution branch pipe; 311: a first check valve; 312: a second one-way valve; 321: a valve inlet; 322: a valve outlet; 323: a valve passage; 324: a valve body throat; 331: a first end; 332: a second end; 333: a valve core main body; 334: a stabilizing block; 335: a hollow groove; 336: a hollow cavity; 400. a three-way pipe.

Detailed Description

So that the manner in which the features and elements of the disclosed embodiments can be understood in detail, a more particular description of the disclosed embodiments, briefly summarized above, may be had by reference to the embodiments, some of which are illustrated in the appended drawings. In the following description of the technology, for purposes of explanation, numerous details are set forth in order to provide a thorough understanding of the disclosed embodiments. However, one or more embodiments may be practiced without these details. In other instances, well-known structures and devices may be shown in simplified form in order to simplify the drawing.

The terms "first," "second," and the like in the description and in the claims, and the above-described drawings of embodiments of the present disclosure, are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It should be understood that the data so used may be interchanged under appropriate circumstances such that embodiments of the present disclosure described herein may be made. Furthermore, the terms "comprising" and "having," as well as any variations thereof, are intended to cover non-exclusive inclusions.

In the embodiments of the present disclosure, the terms "upper", "lower", "inner", "middle", "outer", "front", "rear", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings. These terms are used primarily to better describe the disclosed embodiments and their embodiments, and are not used to limit the indicated devices, elements or components to a particular orientation or to be constructed and operated in a particular orientation. Moreover, some of the above terms may be used to indicate other meanings besides the orientation or positional relationship, for example, the term "on" may also be used to indicate some kind of attachment or connection relationship in some cases. The specific meanings of these terms in the embodiments of the present disclosure can be understood by those of ordinary skill in the art as appropriate.

In addition, the terms "disposed," "connected," and "secured" are to be construed broadly. For example, "connected" may be a fixed connection, a detachable connection, or a unitary construction; can be a mechanical connection, or an electrical connection; may be directly connected, or indirectly connected through intervening media, or may be in internal communication between two devices, elements or components. Specific meanings of the above terms in the embodiments of the present disclosure can be understood by those of ordinary skill in the art according to specific situations.

The term "plurality" means two or more unless otherwise specified.

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 represents: a or B.

The term "and/or" is an associative relationship that describes objects, meaning that three relationships may exist. For example, a and/or B, represents: a or B, or A and B.

The numerical values in the disclosed table are both in units corresponding to indoor working conditions and outdoor working conditions, are all in units corresponding to heating capacity, refrigerating capacity and power, and are in units corresponding to energy efficiency and APF (active power filter) W/W.

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

The refrigeration cycle system includes a heat exchanger 100 and a check valve 300, and the check valve 300 is disposed in the heat exchanger 100.

In some embodiments, the air conditioner has different refrigeration/heating powers set by a user during use, and the flow rate and pressure of the refrigerant discharged by the compressor are correspondingly changed, so that the states of the refrigerant flowing through the heat exchanger are not completely consistent, such as the refrigerant has higher pressure in a high-power state and lower pressure in a low-power state; meanwhile, the temperature of the environment where the heat exchanger is located can also influence the change degree of the temperature and pressure state of the cooling medium in the heat exchanger. Under the common influence of the factors, the pressure difference between two sides of the valve core is relatively small when the refrigerant flows through the one-way valve under some conditions, so that the problem that the valve core cannot be normally opened, is still blocked at the throat part of the valve body or is abnormal in opening amplitude easily occurs, and the normal use of the one-way valve is influenced.

To solve the above-mentioned problem that the pressure difference between both sides of the check valve 300 is too small to be opened normally, optionally, the check valve 300 in the embodiment of the present disclosure satisfies the following relationship:

L₃ ⁴*R≤Z1，

shown in conjunction with FIG. 2, wherein L₃The diameter of the throat part of the valve body of the one-way valve is measured in cm, and R is the equivalent radius of the valve core of the one-way valve is measured in cm; z1 is the set value.

In the embodiment shown in FIG. 2, the throat of the check valve 300 is in the form of a cylindrical throat of equal width, L₃The diameter length value of the cylindrical throat part is taken as the value; in yet other embodiments, the throat of the check valve 300 is tapered, as shown in FIG. 33, corresponding to the pattern L₃The value is the maximum width of the throat of the cone.

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

Alternatively, Z1 is determined according to the rated cooling capacity Q of the refrigeration cycle system. In this embodiment, different from the model selection mode for the check valve applied to the air conditioner in the prior art, the size design of the check valve selected in the present application can match the pressure difference applied to the inlet and outlet of the check valve when the valve core and the refrigeration cycle system work, so that the check valve can still work normally under a small pressure difference; therefore, when the air conditioner switches the refrigerant flow direction (such as the cooling flow direction and the heating flow direction), the one-way valve can be accurately conducted or blocked, and the heat exchanger can normally execute switching operation in different flow path modes.

In some embodiments, an association relationship between Z1 and the rated cooling capacity Q is established, and the selectable form includes an association table in which Z1 and Q are in one-to-one correspondence, and the association relationship is satisfied between the specification form of the selected check valve and the rated cooling capacity of the air conditioner model corresponding to different rated cooling capacities.

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

In still other embodiments, the relationship between Z1 and the rated cooling capacity Q can be formulated, and optionally, the formula for determining Z1 according to the rated cooling capacity Q of the refrigeration cycle system is as follows:

wherein λ is a local drag coefficient, z₂Are weighting coefficients. Rho_{Agent for treating cancer}As the density of the refrigerant, in kg/m³Meter, p_CoreThe unit is the valve core density of the one-way valve in kg/m³And (6) counting.

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

Alternatively, z₂＝1.5*10⁵。

Optionally, the refrigerant is difluoromethane, and the density of the corresponding refrigerant is 0.8-1.1 g/cm 3.

Optionally, the valve core density of the one-way valve is 0.94-0.96 kg/m³。

The relationship that the check valve 300 in the disclosed embodiment satisfies may be expressed as

Wherein m is the refrigerant flow.

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

the local resistance Δ p between the inflow/outflow ends of the non-return valve can be expressed as

The stressed area of the valve core is 4R²The stress of the valve core is 4R²*△P；

At the same time, the volume of the valve core is 0.5 (13/6) × π R³Then the gravity force applied to the valve core is 0.5 (13/6) × π R³G; wherein, (13/6) is obtained by adding coefficients in a semicircular volume formula and a cylindrical volume formula, and specifically, 13/6 is 2/3+ 3/2; g is a gravity constant, and the value 950 is calculated at this time;

in the embodiment of the present disclosure, the check valve is vertically disposed, and the flow direction of the check valve in the conducting state is from bottom to top, and then the stress state that the valve core needs to satisfy in order to open the check valve in the open state can be represented by the following formula:

4R²*△P≥0.5*(13/6)*π*R³*g；

the relation between the rated refrigerating capacity Q and the one-way valve can be obtained by arranging the inequalities:

here, taking the model of the air conditioner with rated refrigerating output of 3.5KW, 5.0KW and 7.2KW as an example, the above formula is substituted for calculation; it is assumed that the environmental parameters and the air conditioner state parameters are as follows,

environmental parameters: the outdoor environment temperature is 35 ℃, and the indoor environment temperature is 27 ℃;

air conditioner state parameters:

the condensation temperature is 45 ℃, the condensation pressure is 2.7948MPa, and the supercooling degree is 5 ℃;

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

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

for an air conditioner type with the rated refrigerating capacity of 3.5KW, the total refrigerant flow is 0.014kg/s, and the refrigerant flow of the one-way valve is 0.010 kg/s;

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

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

substituting the specific values of the above parameters into the equation can yield:

for the air conditioner type with the rated refrigerating capacity of 3.5 KW: l is₃ ⁴*R≤2.8；

For the air conditioner type with the rated refrigerating capacity of 5.0 KW: l is₃ ⁴*R≤5.7；

For the air conditioner type with the rated refrigerating capacity of 7.2 KW: l is₃ ⁴*R≤11.9；

Here, taking an air conditioner model with a rated refrigerating capacity of 7.2kW as an example, the relationship satisfied by the check valve applied to the present application calculated according to the above formula is L₃ ⁴R is less than or equal to Z1 is 11.9, and then the valve is connected with other types of one-way valves (L)₃ ⁴R ≦ Z1 ═ 6), test data for both the normal heating and low temperature heating conditions are shown in table 1 below:

TABLE 1

It can be seen that, under two kinds of heating states, the pressure loss of the check valve that adopts this application scheme to prescribe a limit to size relation will obviously be less than the check valve of other size relations, and this application technical scheme can realize the lower flow resistance of check valve, reduces pressure loss.

Alternatively, as shown in connection with fig. 1 and 3, the heat exchanger 100 includes a heat exchanger body and a check valve 300.

The heat exchanger body is provided with a first refrigerant inlet/outlet 111 and a second refrigerant inlet/outlet 112. When the heat exchanger is used as an evaporator, the refrigerant flows in from the first refrigerant inlet/outlet 111 and flows out from the second refrigerant inlet/outlet 112, and when the heat exchanger is used as a condenser, the refrigerant flows in from the second refrigerant inlet/outlet 112 and flows out from the first refrigerant inlet/outlet 111.

The flow direction of the check valve 300 is restricted to be conducted in case the heat exchanger functions as an evaporator and blocked in case the heat exchanger functions as a condenser.

Alternatively, the check valve 300 may be disposed at the first refrigerant inlet/outlet 111 and/or the second refrigerant inlet/outlet 112.

Alternatively, as shown in fig. 4, the first refrigerant inlet and outlet 111 and the second refrigerant inlet and outlet 112 are communicated with each other through w heat exchange branches 120. Wherein w is an integer greater than 1. Thus, the 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, the refrigerant circulation has diversity, and the heat exchange efficiency of the refrigeration equipment under different working conditions of refrigeration or heating is improved.

Optionally, each heat exchange branch 120 comprises n interconnected₁A heat exchange tube 140, n₁Less than or equal to 8. Thus, the number of the heat exchange tubes 140 on each heat exchange branch 120 is set within the range of less than or equal to 8, so that the too large length of the heat exchange tubes 140 on each heat exchange branch 120 can be prevented from causing too fast pressure drop change, and the energy efficiency of the refrigeration equipment is prevented from being reduced.

Optionally, the w heat exchange branches 120 are communicated between the first refrigerant inlet and outlet 111 and the second refrigerant inlet and outlet 112 through the liquid distributor 200. In this way, the liquid separating function of the liquid separator 200 may be utilized to form a plurality of flow channels in a split manner during the process of flowing the refrigerant along the heat exchange branch 120, so that the refrigerant may flow more reasonably, and a higher heat exchange efficiency may be maintained even when the heat exchanger is used as an evaporator or a condenser.

Optionally, the dispenser 200 comprises: 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 inlet and outlet 111; the second liquid separator 212 is communicated with the first liquid separator 211 through a first one-way valve 311, and the flow direction of the first one-way valve 311 faces the second liquid separator 212; the third dispenser 213 is communicated with the first dispenser 211 and the second dispenser 212; the fourth diverging liquid device 214 is connected to the second refrigerant inlet/outlet 112, and one of the diverging ports is connected to the third diverging liquid device 213 through the second check valve 312, and the remaining diverging ports are connected to the second diverging liquid device 212. In this way, the refrigerant flowing through the plurality of liquid separators 200 is separated, and the flow of the refrigerant is controlled by the first check valve 311 and the second check valve 312, so that the refrigerant can flow in both the forward and reverse directions to have different flow paths, and a high heat exchange efficiency can be maintained in both cases where the heat exchanger is used as an evaporator or a condenser.

Alternatively, as shown in fig. 5, the first liquid separator 211 is communicated with the first refrigerant inlet and outlet 111 through n2 heat exchange tubes 140. In this way, the heat exchange tube 140 is disposed at the first refrigerant inlet/outlet 111 to serve as a supercooling section, so that the refrigerant flowing therethrough can be further liquefied, and the liquefaction rate of the refrigerant can be improved.

Alternatively, n2 ≦ 5. Therefore, the number of the heat exchange tubes 140 used as the supercooling section is limited within the range of less than or equal to 5, so that the problem that the heat exchange efficiency of the heat exchanger is influenced due to overhigh pressure drop caused by resistance increase caused by overlong length of the supercooling section under the condition that the heat exchanger is used as an evaporator can be prevented.

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

Alternatively, as shown in fig. 21, in the case of a heat exchanger as an evaporator, N heat exchange tubes 140 constitute N heat exchange flow paths 130. The number N of the heat exchange flow path 130 constituted by the heat exchange tubes 140 in the case of the heat exchanger as an evaporator is determined based on the total number N of the entire heat exchange tubes 140. Therefore, the flow paths of the heat exchange tubes 140 of the heat exchanger can be reasonably distributed, the phenomenon that the evaporation or condensation is not thorough due to the excessive or insufficient number of the heat exchange tubes 140 in a single heat exchange flow path 130 is avoided, and the heat exchange efficiency of the heat exchanger can be improved.

Where n is w n1, or n is w n1+ n 2. n2 represents the number of heat exchange tubes 140 communicating between the first liquid separator 211 and the first refrigerant inlet/outlet 111.

Optionally, N/a ≦ N ≦ N/b, where a and b are weighting coefficients. Therefore, under the condition that N and N meet the formula, the pressure drop of the whole heat exchanger can be improved and avoided to be too high, and the heat exchange efficiency is improved.

Optionally, INT (N/a). ltoreq.N.ltoreq.INT (N/b), INT being a function of rounding the values down to the nearest integer.

Alternatively, a is 5 or 6, b is 2 or 3. Therefore, the value ranges of the a and the b are limited in the area, so that the quantity of the heat exchange flow paths 130 formed by the n heat exchange tubes 140 is more reasonable under the condition that the heat exchanger is used as an evaporator, the evaporation efficiency of a refrigerant in the evaporator is facilitated, and the heat exchange efficiency of the heat exchanger is further improved.

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

Alternatively, as shown in fig. 6 and 7, in the case of the heat exchanger as an evaporator, N heat exchange tubes 140 constitute N heat exchange flow paths 130. In the case of the heat exchanger as a condenser, the n heat exchange tubes 140 constitute M heat exchange flow paths 130. Where N ≠ M. Thus, the operation principle is different between the case that the heat exchanger is used as an evaporator and the case that the heat exchanger is used as a condenser, and the heat exchange efficiency of the heat exchanger cannot be taken into consideration by adopting the same number of heat exchange flow paths 130, so that the number of the heat exchange flow paths 130 for the refrigerant to circulate is different between the case that the heat exchanger is used as an evaporator and the case that the heat exchanger is used as a condenser, different requirements under two working conditions of evaporation and condensation can be met, and the efficiency of the heat exchanger as an evaporator and the heat exchanger as a condenser is improved.

Alternatively, in the case of a heat exchanger as an evaporator, all the heat exchange tubes 140 constitute N heat exchange flow paths 130. In the case of the heat exchanger as a condenser, all the heat exchange tubes 140 constitute M heat exchange flow paths 130. Wherein N > M. Like this, because under the condition of heat exchanger as the evaporimeter, its inside refrigerant is the process that becomes gaseous by liquid, the volume of refrigerant can increase, consequently, the heat transfer flow path 130 that needs is more, and under the condition of heat exchanger as the condenser, its inside refrigerant has gaseous to become liquid process, the volume of refrigerant can reduce, less heat transfer flow path 130 can hold the refrigerant this moment, consequently set up N to be greater than M and can make the heat exchanger can smoothly pass through the refrigerant under the condition as the evaporimeter and under the condition as the condenser, reduce the resistance that the refrigerant flows, reduce the pressure drop promptly, improve heat exchange efficiency.

Optionally, M/N is greater than or equal to 30% and less than or equal to 70%. Preferably, M/N is more than or equal to 50% and less than or equal to 70%, so that the energy efficiency of the refrigeration equipment can be greatly improved, particularly in a low-temperature intermediate refrigeration stage, the energy efficiency is remarkably improved, the energy efficiency grade of a product can be improved, the commercial value of the product is improved while the energy is saved and the environment is protected, and the competitiveness of the product is improved.

Compared with M ═ N, taking M/N ═ 50% as an example, the energy efficiency performance at each stage is as follows:

the energy efficiency at each stage for M ═ N is shown in table 2 below:

TABLE 2

The energy efficiency at each stage for 50% M/N is shown in table 3 below:

TABLE 3

In conclusion, the data comparison in the two tables shows that in the low-temperature intermediate refrigeration stage, the energy efficiency of the product is greatly improved by the heat exchanger with the M/N of 50%, and the energy efficiency grade of the product can be improved.

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.

Alternatively, a heat exchanger of 1/2M/N ═ is used in a 3.5KW model. Therefore, the arrangement of the number of the heat exchange paths can better meet the use conditions of a 3.5KW machine type, and the energy efficiency ratio of a product is improved.

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

the energy efficiency of the product with the preferred embodiment M/N1/2 is shown in table 4 below:

TABLE 4

The product energy efficiency performance in the case of M ═ N is shown in table 5 below:

TABLE 5

The energy efficiency performance of the product in the case of the preferred embodiment M/N-1/4 is shown in table 6 below:

TABLE 6

The energy efficiency of the product with the preferred embodiment M/N3/4 is shown in table 7 below:

TABLE 7

By combining the tables, it can be seen that for a 3.5KW model, when the heating branch N is equal to 4, the optimal cooling branch M is 2, and the APF is 5.10 at the maximum, at this time, M/N is 1/2, if M is decreased to 1, the APF is decreased to 4.99, otherwise, if M is increased to 3, the APF is decreased to 4.62, which means that energy efficiency can be greatly improved by adopting M/N1/2 in the 3.5KW model, and energy saving and environmental protection are more achieved.

Alternatively, a heat exchanger of M/N4/7 is used in 7.2KW models. Therefore, the arrangement of the number of the heat exchange paths can better meet the use conditions of the 7.2KW type, and the energy efficiency ratio of the product is improved.

The energy efficiency performance for different ratios of the 7.2KW models M and N is shown in the table below:

the energy efficiency performance of the product in the case of the preferred embodiment M/N-4/7 is shown in table 8 below:

TABLE 8

The product energy efficiency performance in the case of M ═ N is shown in table 9 below:

TABLE 9

The energy efficiency performance of the product in the case of the preferred embodiment M/N-3/7 is shown in table 10 below:

watch 10

The energy efficiency performance of the product in the case of the preferred embodiment M/N-2/7 is shown in table 11 below:

TABLE 11

The energy efficiency performance of the product in the case of the preferred embodiment M/N-5/7 is shown in table 12 below:

TABLE 12

From 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 4.56, at this time, M/N is 0.57, if M decreases to 3, the APF decreases to 4.45, if M decreases to 2, the APF decreases to 4.32, and if M increases to 5, the APF decreases to 4.35, and it can be seen that the energy efficiency can be greatly improved, and the model is more energy-saving and environment-friendly by adopting M/N4/7 in the 7.2KW model.

Alternatively, N-M.gtoreq.2. Thus, when the heat exchanger is used as an evaporator and when the heat exchanger is used as a condenser, the effect of increasing the heat transfer coefficient by increasing the difference in the number of flow paths can be achieved.

Alternatively, the n heat exchange tubes 140 are arranged in m rows, where m ≦ 5.

Alternatively, 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 section of the refrigeration equipment, and the corresponding relationship between the tube diameters of the heat exchange tubes 140. Therefore, under the condition that the capacity section of the refrigeration equipment is determined, the space size of the position is determined under the general condition, the space occupied by the heat exchange tubes 140 can be determined according to the tube diameters of the heat exchange tubes 140 and the number n of the heat exchange tubes 140, the heat exchange tubes 140 are reasonably arranged in rows, the occupied space can be kept in a reasonable range, and the installation and the use are convenient.

More specifically, the correspondence relationship between the number m of rows of the heat exchange tubes 140 and the number n of the heat exchange tubes 140, the capacity section of the refrigeration equipment, and the tube diameter of the heat exchange tubes 140 is shown in the following table 13:

watch 13

Optionally, as shown in fig. 8 and 9, in the case that n heat exchange tubes 140 of the heat exchanger 100 are averagely distributed to w heat exchange branches 120 in an integer and then h heat exchange tubes 140 are left, h heat exchange tubes 140 are drawn out, or h heat exchange tubes 140 are communicated with the first refrigerant inlet and outlet 111 to serve as subcooling sections, or h heat exchange tubes 140 are evenly distributed to h heat exchange branches 120, where h is less than w. Therefore, the quantity of the heat exchange tubes 140 on each heat exchange branch 120 can be kept close to each other as much as possible, so that the resistance of each heat exchange branch 120 is close to each other, and the situation that the refrigerant circulation is different due to different resistances is prevented, and further the overall heat exchange of the heat exchanger is not uniform enough is avoided.

More specifically, when w is 3 and n is 10, 1 heat exchange tube 140 is drawn out, 3 heat exchange tubes 140 are disposed on each

heat exchange branch

120, or 3 heat exchange tubes 140 are disposed on each heat exchange branch 120, and 1 heat exchange tube 140 is communicated with the first refrigerant inlet and outlet 111 as a supercooling degree section, or as shown in fig. 8, 3 heat exchange tubes 140 are disposed on 3 heat exchange branches 120, and 4 heat exchange tubes 140 are disposed on the other 1 heat exchange branch 120.

More specifically, when w is 5 and n is 22, 2 heat exchange tubes 140 are drawn out, and 4 heat exchange tubes 140 are disposed on each heat exchange branch 120, or 4 heat exchange tubes 140 are disposed on each

heat exchange branch

120, and 2 heat exchange tubes 140 are communicated with the first refrigerant inlet and outlet 111 as supercooling degree sections, or as shown in fig. 9, 5 heat exchange tubes 140 are disposed on 2 heat exchange branches 120, and 4 heat exchange tubes 140 are disposed on the other 3 heat exchange branches 120.

Optionally, the second liquid separator 212 is a manifold communicated 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 disposed such that the liquid separation port 221 is upward and the manifold is downward, as shown in fig. 10; and at least one of the liquid inlet and outlet ports 221 in the case where the heat exchanger 100 is used as a condenser;

the first check valve 311 is disposed at the refrigerant inlet/outlet 110, and restricts a flow direction thereof to be in a conducting state when the heat exchanger 100 is used as an evaporator, and to be in a blocking state when the heat exchanger 100 is used as a condenser, so as to allow the second liquid separator 212 to merge and store the 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 of the liquid separation ports are used as inlet liquid and 1 is used as outlet liquid.

As a further alternative, as shown in fig. 11, the second liquid separator 212 is disposed obliquely, the liquid separating port 221 is disposed obliquely upward, and the collecting pipe 240 is disposed obliquely downward, so that the liquid storage function of the liquid separator can be realized, and at least one of the liquid inlet ports 221 and at least one of the liquid outlet ports are provided in the case where the heat exchanger 100 is used as a condenser.

Optionally, when the second liquid separator 212 is obliquely arranged, the inclination angle α with the vertical direction is less than or equal to β, and 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 fig. 1 and 3, the heat exchanger 100 includes a heat exchanger main body, a liquid-separating and liquid-storing device, and a one-way conduction device.

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

The liquid separating and storing device comprises a collecting pipe communicated with the first refrigerant inlet and outlet 111 or the second refrigerant inlet and outlet 112, and a plurality of liquid separating ports 221 communicated with part of the heat exchange branches one by one. The liquid separating and storing device is configured to be used for separating the refrigerant conveyed by the refrigerant inlet and outlet to the plurality of heat exchanging branches 120 when the heat exchanger 100 is used as an evaporator, and converging and storing the refrigerant when the heat exchanger 100 is used as a condenser.

Optionally, the liquid separating and storing device comprises a liquid separator 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, and a manifold 240 and a plurality of liquid distribution ports 221 respectively connected to the liquid distribution chamber 230. In the case that the heat exchanger 100 is used as a condenser, at least one of the liquid inlets 221 is fed with liquid, and at least one of the liquid outlets is discharged with liquid, so that the liquid is converged by the liquid distributor and the liquid dividing chamber 230 stores part of the refrigerant.

The one-way conduction 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 conduction when the heat exchanger 100 functions as an evaporator and to blocking when the heat exchanger 100 functions as a condenser.

Optionally, the one-way conducting means comprises a one-way valve or an electrically controlled valve. It should be understood that the technical solution of the present application is that the type of the illustrated check valve is only an alternative exemplary illustration, and does not limit the scope of the solution protection, and those skilled in the art can know that other parts or components capable of realizing the function of one-way conduction in the field can be used as alternative solutions of the present application, and should also be covered within the scope of the present application.

Optionally, in this embodiment, the check valve 300 is disposed on the manifold 240. The flow direction of the check valve 300 is limited to be open in case the heat exchanger 100 functions as an evaporator, and to be blocked in case the heat exchanger 100 functions as a condenser and to allow the liquid-dividing chamber 230 to store liquid.

The check valve 300 includes a valve outlet 322 communicating with the manifold and a valve inlet 321 communicating with the corresponding refrigerant inlet and outlet, and is in a conduction state when the refrigerant flows from the valve inlet 321 to the valve outlet 322, and in a blocking state when the refrigerant flows from the valve outlet 322 to the valve inlet 321.

The electrically controlled valve is configured to be controlled to open in the case of the heat exchanger 100 acting as an evaporator and to close in the case of the heat exchanger 100 acting as a condenser.

For example, referring to fig. 3, taking the second liquid separator 212 as an example, when the heat exchanger is used as a condenser, the second refrigerant inlet/outlet 112 serves as an inlet of the refrigerant, the first refrigerant inlet/outlet 111 serves as an outlet of the refrigerant, the refrigerant flows into the heat exchanger from the second refrigerant inlet/outlet 112 and is then respectively divided into the first heat exchange branch 121 and the second heat exchange branch 122, at this time, the first check valve 311 and the second check valve are both in a blocking state, the refrigerant flows out to the first heat exchange branch 121 and the second heat exchange branch 122 and continues to flow into the second liquid separator 212 for confluence, the converged refrigerant flows out from a liquid separating port of the second liquid separator 212 communicating with the third heat exchange branch 123, and since the liquid separating ports of the second liquid separator 212 are both facing upward, in this state, part of the refrigerant can be stored in the liquid separating chamber of the second liquid separator 212 and a part of the pipe section of the liquid separating chamber to the check valve under the action of gravity, the liquid storage function of the second liquid separator 212 is realized.

The heat exchanger that this disclosed embodiment provided is through the cooperation of reposition of redundant personnel stock solution device and one-way conduction device, utilize reposition of redundant personnel stock solution device can store partial refrigerant, thereby make the heat exchanger also can possess certain stock solution function, compare in the form that current air conditioner only utilized the reservoir stock solution, the refrigerant stock solution scope of air conditioner can be enlarged to this embodiment, especially can reduce the heat cycle of unnecessary refrigerant under the low-load state, make the actual refrigerant circulation volume of air conditioner can with current working property looks adaptation, the control range to the refrigerant circulation volume of air conditioner under different running state has been promoted.

Here, the description will be continued by taking an outdoor heat exchanger of an air conditioner as an example. Generally, for a given air conditioner and operating conditions, there is an optimum refrigerant charge that optimizes the air conditioner operating performance; in general, the optimal refrigerant charge amount in heating operation is slightly larger than that in cooling operation, so that the extra refrigerant is generally stored in the air conditioner in a liquid form in the cooling operation; in the scheme, the outdoor heat exchanger is used as a condenser during the refrigeration operation, so that the inner volume of a liquid separator in the outdoor heat exchanger can be utilized to realize the function of liquid storage.

Meanwhile, for the air conditioner, the air conditioner is balanced in high pressure and low pressure in the starting and stopping processes, and a refrigerant flows from the low pressure side to the high pressure side; in the present embodiment, most of the refrigerant (60% or more) of the air conditioner is stored in the outdoor unit when the air conditioner is turned on; most (60% or more) of the refrigerants (60% or more) are stored in the indoor unit in the shutdown state.

When the air conditioner operates in a heating mode, the outdoor heat exchanger is used as an evaporator, and the storage amount of a refrigerant in the liquid distributor is more than that of the refrigerant in the air conditioner during starting up when the air conditioner is stopped; when the air conditioner operates in a refrigeration mode, the outdoor heat exchanger is used as a condenser, and the storage amount of the refrigerant in the liquid distributor is more than that of the refrigerant in the shutdown state when the air conditioner is started. When the air conditioner is stopped, part of refrigerant is stored in the indoor heat exchanger, the outdoor heat exchanger, the compressor cavity, the gas-liquid separator and other parts.

Under the APF test standard, the air conditioner has 100% load and partial load test working conditions in both cooling and heating operation, and the refrigerant circulation volume is smaller than that under 100% load in the partial load state, so that the liquid storage volume of the liquid separator is larger than that under 100% load in the partial load operation.

For example, the air conditioner without liquid storage function using a dispenser with a common flow-splitting design and the air conditioner with liquid storage function using a dispenser with a variable flow-splitting design in combination with a check valve were compared, and the capacity, power and energy efficiency of the two air conditioners were respectively tested, and the test data are shown in table 14 below:

TABLE 14

It can be seen from the table that because variable reposition of redundant personnel has realized better refrigeration flow path and has taken the stock solution function with knockout cooperation check valve, the energy efficiency that this application used variable reposition of redundant personnel design knockout cooperation check valve to take the air conditioner of stock solution function can reach when the operation is obviously superior to the air conditioner that the knockout of ordinary reposition of redundant personnel design does not have the stock solution function.

Meanwhile, for the same air conditioner, the energy efficiency of the air conditioner under the two conditions of the liquid storage function and the liquid storage function is tested by using two different liquid distributors in the heat exchanger, wherein the scheme is that a common liquid distributor is adopted, and the space of a cavity of an internal liquid cavity is narrow; the second scheme adopts a liquid separator with a liquid storage function, and the volume of a liquid separation cavity of the second scheme is obviously larger than that of the first scheme. The test conditions are that the refrigerator operates under a rated refrigeration condition, the indoor dry-wet bulb temperature is 27 ℃/19 ℃, the outdoor dry-wet bulb temperature is 35 ℃/24 ℃, and the test result pair ratio is shown in a table 15:

watch 15

	Capability of	Power of	Energy efficiency
				Scheme I	3440W	861W	4.00
Scheme 2	3445W	858W	4.02

As can be seen from the comparison of the data in the above table, since the form of the liquid separator is generally selected only in consideration of the "flow dividing" function in the prior art, the liquid separator is generally designed to be as small as possible under the condition of satisfying the "flow dividing" function, so as to reduce the occupation of space volume and the manufacturing cost; and this application adopts the knockout in bigger volume branch liquid chamber, and it can realize the stock solution function under the refrigeration mode to can improve the efficiency of the air conditioner of the knockout of using this kind of stock solution function at the actual motion in-process, actual measurement performance has the air conditioner that is superior to adopting ordinary knockout.

Further, the manifold 240 of the liquid separator 200 is connected to the manifold 240 of the first refrigerant inlet/outlet 111 or the second refrigerant inlet/outlet 112, and the plurality of liquid separation ports 221 are in one-to-one correspondence with the plurality of heat exchange branches.

In order to realize the liquid storage function of the liquid separator 200 and avoid the problem of excessive liquid storage caused by the overlarge volume of the liquid separation cavity of the liquid separator and adapt to the liquid storage requirements of different air conditioner models, optionally, V is not less than f2 × Q, f2 is a preset multiple, V is the volume of the liquid separation cavity and is in cm unit³And Q is rated refrigerating capacity and is measured in kW.

Alternatively, the heat exchanger to which the variable split flow form is applied shares two forms, including a four-branch variable split flow form shown in fig. 3 and a three-branch variable split flow form shown in fig. 12, respectively.

Optionally, for the four-branch variable flow splitting type heat exchanger, the value range of f2 is 8-12.

Optionally, f2 takes the value of 10, i.e., V is less than or equal to 10Q.

In this embodiment, for the four-branch heat exchanger in the form of variable split flow, the relationship between the rated capacity of the unit and the charging capacity is approximately: m is 160Q; the normal heating mode is 10-15% higher than the refrigerant filling amount requirement of the cooling mode, while the compressor gas-liquid separator can generally store 5-10% of the refrigerant, the refrigerant actually required to be stored by the liquid separator is 5% of the total filling amount, and if the actual storage amount of the liquid separator exceeds 5% of the total filling amount, the actual refrigerant circulation amount of the air conditioner may be affected, the liquid separator needs to store liquid m which is 160Q by 5% and 8Q at most.

Optionally, the refrigerant type is difluoromethane (R32), the refrigerant density is about 0.8-1.1 g/cm3 in an actual use temperature range, and the volume of the liquid separation cavity itself cannot exceed 8Q/0.8-10Q, calculated by an upper limit of 0.8g/cm3 of the refrigerant density, and Q is calculated according to kW.

For example, for an air conditioner with a rated refrigerating capacity of 3.5KW, the volume of the liquid separating cavity of the selected liquid separator needs to satisfy V ≦ f2 ═ Q ═ 10 ═ 3.5 ═ 35, namely, the volume of the liquid separating cavity of the liquid separator should be less than or equal to 35cm³。

Here, for the four-branch heat exchanger with variable split flow, the operation performance of the same air conditioner is tested under the condition that f2 is 8/10/12/14, and the like, and the operation performance of the same air conditioner is compared for different volume liquid distributors (according to the value of f 2), and the test data is shown in the following table 16:

TABLE 16

Value of f2	Capability of	Power of	Energy efficiency
				8	3446W	857W	4.02
10	3451W	855W	4.04
				12	3440W	856W	4.02
14	3423W	861W	3.96

According to the test data in the table, in the value range (8-12) of f2 defined in the application, the value of f2 is increased, and the energy efficiency is gradually improved; however, if f2 is too large (f2 exceeds 12), the power increases and the energy efficiency decreases.

In still other optional embodiments, in order to implement the liquid storage function of the dispenser 200, avoid the problem of unable liquid storage due to the volume of the liquid separation chamber of the dispenser being too small, and adapt to the liquid storage requirements of different air conditioner models, optionally, the dispenser with the liquid storage function in the technical solution of the present application needs to satisfy the following conditions:

V≥f1*Q，

f1 is a preset multiple, V is the volume of the liquid separation cavity and is measured in cm3, and Q is rated refrigerating capacity and is measured in kW.

Optionally, for the four-branch variable flow-splitting heat exchanger, the value range of the lower limit f1 of the volume of the liquid distributor is 0.2-4.

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

Optionally, f1 has a value in a range of 2-4.

Preferably, f1 has a value of 3. In this embodiment, the lower limit of the volume of the liquid distributor is mainly determined by the structural limitation, and for reliability, the radius R of the cross section of the liquid distributor is generally about 4 times the radius R of the branch pipe, so as to ensure that the radius of the distributor is not too large (i.e. the radius of the distributor is prevented from affecting the space of the heat exchanger), ensure a certain distance between the branch pipes, and ensure that the distributor still has enough strength after welding. That is, in this example, as shown in fig. 13, the radius R of the dispenser is 4R, and in this example, R is 1.4 cm.

Meanwhile, when the dispenser 200 is actually processed, the depth of each branch liquid distribution pipe 250 inserted into the dispenser 200 should not be less than 3 mm. In addition, when the refrigeration mode is downward, three liquid-separating branch pipes of the liquid separator 200 are in two-in one-out states, and the refrigerant fluid needs to be bent for 180 degrees (in a lower-in upper-out state) in the liquid-separating cavity of the liquid separator 200; for stability, the equivalent length from the lower end surface of each branch liquid separator to the lower end surface of the liquid separator needs to reach at least 4r to ensure that the fluid smoothly flows out from two branch liquid separators 250 and flows into the other branch liquid separator 250, i.e. the depth of the whole liquid separator is about 0.3+ 1.4-1.7 cm;

therefore, the internal volume of the liquid separator must not be less than: pi R2 1.7 10.455Q.

Here, for the heat exchanger with four branches in the variable split flow form, the operation performance of the same air conditioner is tested under the condition that f1 is taken as 1/2/3/4, and the like, and the operation performance of the same air conditioner is compared for different volume liquid distributors (taken as f 1), and the test data is shown in the following table 17:

TABLE 17

Value of f1	Capability of	Power of	Energy efficiency
				1	3426W	865W	3.96
2	3438W	861W	3.99
				3	3442W	860W	4.00
4	3442W	859W	4.01

From the above table, it can be seen that for different volumetric dispensers, the higher the value of f1, the lower the power and the higher the energy efficiency.

Similarly, for a three-branch variable split heat exchanger, the three-branch pipe 400 (dashed box) for connecting the main pipe and the two branch pipes is a "one-to-two" three-way pipe 400 shown in fig. 12, and the size is smaller than that of a four-branch variable split liquid separator.

Optionally, for the three-branch variable flow-dividing heat exchanger, V is not more than f2 × Q, and the value range of f2 is 0.75-1.0.

Optionally, for the three-branch variable flow splitting heat exchanger, V is greater than or equal to f1 × Q, and the value range of f1 is 0.15-0.25.

Considering that the liquid separator in this form is relatively fixed and has small volume change difference, the corresponding relationship between the f value and the rated refrigerating capacity of the air conditioner with different rated refrigerating capacities is shown in the following table 18:

watch 18

Rated refrigerating capacity	2.6KW	3.5KW	5.0KW	7.2KW
					Value of f	0.72	0.53	0.37	0.25

The volume of the liquid separating cavity of the selected liquid separator is calculated to meet the requirement that V is not more than f, Q is 0.53, 3.5 and approximately 1.86cm for the air conditioner with the same rated refrigerating capacity of 3.5KW³。

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

Alternatively, the branch liquid pipes 250, through which the plurality of heat exchange branches 120 communicate, are disposed on one end surface of the housing 220 of the liquid separator 200 and are arranged along the same circumferential line of the end surface, the plurality of branch liquid pipes 250 are uniformly disposed on the end surface of the liquid separator 200, and the intervals between the adjacent branch liquid pipes 250 are the same, so that the liquid separator 200 can uniformly distribute the refrigerant to the plurality of branch liquid pipes 250.

Optionally, each branch dispensing tube 250 extends into the dispensing chamber 230 through an end face.

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

In this embodiment, the number of branch liquid distribution pipes 250 is 3.

Optionally, the inner diameter of the liquid separation cavity 230 is 3-5 times of the outer diameter of the branch liquid separation pipe 250. Therefore, the radius of the liquid distributor is not too large (the radius of the liquid distributor affects the space of the heat exchanger), a certain distance is ensured among the liquid distributing branch pipes, and the liquid distributor still has enough strength after welding.

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

Optionally, the dispenser includes a housing, a manifold 240, a first branch manifold 251, and a second branch manifold 252. A liquid separating cavity is formed in the shell, a first liquid separating port and a second liquid separating port are formed in the shell, the collecting pipe 240 is communicated with the liquid separating cavity, the first liquid separating branch pipe 251 is communicated with the liquid separating cavity through the first liquid separating port, and the second liquid separating branch pipe 252 is communicated with the liquid separating cavity through the second liquid separating port.

Optionally, the liquid separating cavity comprises a converging cavity 234, a first branch cavity 235 and a second branch cavity 236, the first branch pipe 251 is communicated with the first branch cavity 235 through a first liquid separating port, and the second branch pipe 252 is communicated with the second branch cavity 236 through a second liquid separating port.

Optionally, the manifold 240 includes a first pipe segment 241 and a second pipe segment 242 in bending communication, and the first pipe segment 241 is in direct communication with the liquid separation chamber.

The plane in which the axes of the first and

second tube sections

241, 242 lie is a first plane. The plane in which the axes of the first branch 251 and the second branch 252 lie is the second plane. Optionally, the first plane is non-perpendicular to the second plane.

The collecting pipe 240 comprises a first pipe segment 241 and a second pipe segment 242, the plane of the axes of the first pipe segment 241 and the second pipe segment 242 is a first plane, and the included angle between the first plane and the second plane is e. As shown in fig. 21. The first plane is non-perpendicular to the second plane, it being understood that the angle e between the first plane and the second plane is less than 90 °. Optionally, the angle between the first plane and the second plane is measured as the acute angle formed by the two. The first plane is non-perpendicular to the second plane, so that the amount of refrigerant entering the first branch refrigerant pipe 251 and the second branch refrigerant pipe 252 through the first pipe section 241 is different. For example, when the included angle between the first plane and the second plane is on the side of the first branch liquid-dividing pipe 251, the flow rate of the refrigerant flowing to the second branch liquid-dividing pipe 252 is greater than the flow rate flowing to the first branch liquid-dividing pipe 251 under the action of gravity. Similarly, when the included angle between the first plane and the second plane is on the side of the second branch liquid distribution pipe 252, the flow rate of the refrigerant flowing to the first branch liquid distribution pipe 251 is greater than the flow rate of the refrigerant flowing to the second branch liquid distribution pipe 252 under the action of gravity.

Alternatively, the liquid separator provided by the embodiment of the present disclosure may be used as the first liquid separator 211 of the heat exchanger as shown in fig. 3. As shown in fig. 3, when the heat exchanger is used as an evaporator, the refrigerant is divided by the first liquid separator 211 and then flows into four heat exchange branches connected in parallel, that is, the first heat exchange branch 121, the second heat exchange branch 122, the third heat exchange branch 123 and the fourth heat exchange branch 124. In the direction shown in fig. 3, the refrigerant flows through the branch liquid pipe on the left side of the first liquid separator 211 and then flows into only the fourth heat exchange branch 124, and the refrigerant flows through the branch liquid pipe on the right side of the first liquid separator 211 and 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 refrigerant amount required by the two branch liquid separating pipes of the first liquid separator 211 is different. In the heat exchanger shown in fig. 3, the refrigerant amount required for the right branch liquid dividing pipe is approximately 3 times the refrigerant amount required for the left branch liquid dividing pipe. The knockout that this disclosure provided utilizes the coolant at the action of gravity of flow in-process, through the setting of the contained angle between the first plane at the axis place of first pipeline section 241 of collecting pipe 240 and second pipeline section 242 and the second plane at the axis place of first branch liquid pipe 251 and second branch liquid pipe 252, realized that the coolant volume that different branch liquid pipes of knockout flow is different, satisfied the different demands of the required coolant volume of branch liquid pipe, and then improved the heat exchange efficiency of heat exchanger.

Optionally, the number of the liquid distribution ports formed in the housing and the number of the liquid distribution branch pipes corresponding to the liquid distribution ports are not limited in the embodiment of the present disclosure, for example, the number of the liquid distribution ports may be 3, 4, 5 or more, and correspondingly, the number of the liquid distribution branch pipes may also be 3, 4, 5 or more.

Optionally, an angle between the first plane and the second plane is less than 90 degrees. Optionally, the included angle between the first plane and the second plane is 0 degree, 30 degrees, 60 degrees, 70 degrees, 80 degrees, or the like. The included angle between the first plane and the second plane is smaller than 90 degrees, so that the refrigerant can bias under the action of gravity after flowing through the first pipe section 241 of the collecting pipe 240, and further the cold amount flowing into the first branch liquid dividing pipe 251 and the second branch liquid dividing pipe 252 is different.

Optionally, the first pipe segment 241 of the manifold 240 has an inner diameter greater than the inner diameter of the first branch 251.

Optionally, the inner diameter of first branch knock out leg 251 is greater than the inner diameter of second branch knock out leg 252. According to the liquid distributor provided by the embodiment of the disclosure, an included angle is formed between a first plane where the axes of the first pipe section 241 and the second pipe section 242 of the collecting pipe 240 are located and a second plane where the axes of the two liquid distributing branch pipes are located, and the difference of the refrigerant amount flowing into the two liquid distributing branch pipes is further increased by further matching with the inner diameter difference between the two liquid distributing branch pipes. Optionally, the first pipe section 241 of the collecting pipe 240 is inclined toward the second branch liquid pipe 252, and under the action of gravity, the inner diameter of the first branch liquid pipe 251 is further matched to be larger than the inner diameter of the second branch liquid pipe 252, so that more refrigerant flows into the first branch liquid pipe 251, and the refrigerant flow rate difference between the two branch liquid pipes is further increased.

It is difficult to achieve a refrigerant flow rate difference of 2:1 in the flow rate ratio of the first branch liquid dividing pipe 251 to the second branch liquid dividing pipe 252 only by limiting the difference in the inner diameters of the first branch liquid dividing pipe 251 and the second branch liquid dividing pipe 252. The reason is that in the actual preparation process of the heat exchanger, the pipe diameters of copper pipes used in the heat exchanger have certain specifications, namely, the pipe diameters cannot be selected randomly, so that a pipe diameter scheme that the flow ratio of two liquid separating branch pipes is 2:1 can not be found normally; if the refrigerant separating flow rate difference is realized by other means such as the separating branch pipe length difference and bending, the universality is not provided for the mass production products. Therefore, the refrigerant distribution of the refrigerant flow rate ratio of 2:1 of the two branch liquid distribution pipes cannot be accurately realized only by the difference in the inner diameters of the first branch liquid distribution pipe 251 and the second branch liquid distribution pipe 252.

It is difficult to achieve refrigerant distribution with a refrigerant flow difference of 3:1 or more in the flow ratio of the first branch liquid dividing pipe 251 to the second branch liquid dividing pipe 252 only by limiting the difference in the inner diameters of the first branch liquid dividing pipe 251 and the second branch liquid dividing pipe 252. The reason is that the inner diameter of the branch liquid-separating pipe is limited to the minimum value, for example, the inner diameter of the branch liquid-separating pipe cannot be less than 3mm, even not less than 3.36mm, the copper pipe below the inner diameter actually becomes a capillary pipe, the capillary pipe has larger flow resistance, and forms a throttling and pressure reducing effect on the flow of the refrigerant, so that the power of the compressor can be increased, and the performance of the system can be reduced; even when the air conditioner operates in a heating working condition, the outdoor heat exchanger is frosted seriously, and the safety and reliability of the system are affected. Due to the limitation of the minimum value of the inner diameters of the branch liquid-separating pipes, in order to realize refrigerant distribution with a flow ratio of 3:1, the pipe diameter of the other branch liquid-separating pipe needs to be larger than 7mm, and optionally, the 7mm can be an outer diameter which is 1.4mm larger than the inner diameter, however, the pipe diameter obviously exceeds the inner diameter of a heat exchange pipe which is actually used in the heat exchanger, and the general pipe diameter of the heat exchanger is 7mm, such as a pipe fin type heat exchanger. Therefore, it is difficult to achieve refrigerant distribution with a refrigerant flow rate difference of 3:1 or even larger for the flow rate ratio of the first branch liquid dividing pipe 251 to the second branch liquid dividing pipe 252, within a range not exceeding the allowable pipe diameter of the heat exchange pipe in the heat exchanger, only by limiting the difference in the inner diameters of the first branch liquid dividing pipe 251 and the second branch liquid dividing pipe 252.

According to the technical scheme that an included angle is formed between a first plane where axes of a first pipe section 241 and a second pipe section 242 of a collecting pipe 240 are located and a second plane where axes of two liquid separating branch pipes are located, and the technical scheme is further matched with the inner diameter difference between the two liquid separating branch pipes, the refrigerant distribution requirements that the refrigerant flow ratio of the two liquid separating branch pipes is 2:1-7:1 and even a larger proportion can be achieved within the range allowed by the pipe diameter of a heat exchange pipe of a heat exchanger, such as 2:1, 3:1, 4:1, 5:1, 6:1 and 7: 1. According to the refrigerant distribution scheme for realizing the large flow ratio, the inner diameter of the second branch liquid distribution pipe 252 does not need to be designed to be too small, and the flow rate of the refrigerant in the first branch liquid distribution pipe 251 is far larger than that of the refrigerant in the second branch liquid distribution pipe 252. Therefore, the refrigerant distribution scheme of the liquid separator provided by the embodiment of the disclosure avoids the problem of overlarge total pressure drop of the liquid separating branch pipes and the heat exchanger of the liquid separator when the refrigerant distribution ratio of the two liquid separating branch pipes is large.

Optionally, an included angle between a first plane where the axes of the first pipe segment 241 and the second pipe segment 242 of the collecting pipe 240 are located and a second plane where the axes of the two branch liquid pipes are located is greater than or equal to 50 degrees and less than or equal to 70 degrees. The difference in the flow rates of the refrigerant in the first branch refrigerant pipe 251 and the second branch refrigerant pipe 252 is increased. Alternatively, the inner diameter of the first branch liquid-dividing pipe 251 is greater than or equal to 5.1mm and less than or equal to 6.1 mm; the second branch liquid take-off 252 has an inner diameter of 3.1mm or more and 3.7mm or less. Optionally, the second pipe segment 242 of the collecting pipe 240 is disposed obliquely to the second branch liquid pipe 252 side.

When the air conditioner operates in a heating working condition and the heat exchanger is used as an evaporator, the heat exchanger can exert the optimal heat exchange capacity under the following conditions: when heating, constantly absorb the heat in the surrounding environment air from low temperature liquid state, reached gas-liquid two-phase state along with the temperature rise, the temperature keeps unchanged at evaporating temperature this time, only constantly takes place the liquid phase change to gaseous state, and liquid refrigerant is less and less, and gaseous refrigerant is more and more, just all becomes gaseous state and the temperature is higher than evaporating temperature 1 ~ 2 ℃ when the export of whole heat transfer branch road. The reason is that when the outlet temperature of the heat exchange branch is overheated, all the gas-state refrigerants are gaseous refrigerants, the enthalpy difference of the gaseous refrigerants is small, the heat exchange capacity is low, and when the superheat degree is overlarge, the heat exchange temperature difference between the refrigerants and the ambient temperature is small, for example, when the evaporation temperature is about 0-1 ℃, if the superheat degree is greater than 3 ℃, the temperature is above 4 ℃, and the ambient temperature in winter is about 7 ℃, the heat exchange temperature difference is small, and the heat exchange capacity of the heat exchanger is more difficult to be exerted.

The better the uniformity is, the easier each heat exchange branch has a proper heat exchange, if not uniform, some branches are too hot, the back hairpin tubes have no heat exchange effect, some heat exchange branch refrigerants are too many, and the whole heat exchange branch still has a lot of low-temperature liquid refrigerants to exchange cold energy, so that the heat exchange effect of the whole heat exchanger is poor under the same refrigerant flow, and the capacity of the air conditioner is very low. Therefore, the method for judging good shunting of experience in heating comprises the following steps: the temperature difference of the outlets of the branches is within 2 ℃, the superheat degree of the outlets is about 1 ℃, and the shunting is better under the condition.

Watch 19

Watch 20

Optionally, the air conditioner is operated in a heating working condition, the heat exchanger is used as an evaporator, and the first heat exchange branch and the second heat exchange branch are connected in parallel

When the heat exchange branch and the third heat exchange branch are communicated with the first branch liquid-dividing pipe 251 and the fourth heat exchange branch is communicated with the second branch liquid-dividing pipe 252, as shown in fig. 3, the refrigerant temperatures at the outlets of the heat exchange branches are shown in tables 19 and 20. In table 19, when the included angle between the first plane and the second plane is 90 degrees, the maximum temperature difference between the fourth heat exchange branch and the first three branches and the heating capacity of the air conditioner are different under the inner diameters of the first liquid dividing branch 251 and the second liquid dividing branch 252. As can be seen from the data in table 19, when the inner diameter of the first branch 251 is 5.6mm, and the inner diameter of the second branch 252 is 3.36mm, the maximum temperature difference between the fourth heat exchange branch and the first three branches of the heat exchanger is 3.4 ℃ which is the smallest, and the heating capacity of the air conditioner is 4855.2W which is the largest at this inner diameter. Table 20 shows that when the inner diameter of the first branch liquid distribution pipe 251 is 5.6mm, and the inner diameter of the second branch liquid distribution pipe 252 is 3.36mm, the included angle between the first plane and the second plane is different, the maximum temperature difference between the fourth heat exchange branch and the first three branches is equal to the heating capacity of the air conditioner. As can be seen from table 20, when the included 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 minimum and is 1.2 ℃, and at this angle, the heating capacity of the air conditioner is maximum and is 5016.1W.

As can be seen from the data in tables 19 and 20, when the number of the heat exchange branches in the heat exchanger, which are communicated with the first liquid-dividing branch pipe 251, is 3, and the number of the heat exchange branches in the heat exchanger, which are communicated with the second liquid-dividing branch pipe 252, is 1, for example, the heat exchanger shown in fig. 3, the inner diameter of the first liquid-dividing branch pipe 251 is 5.6mm, the inner diameter of the second liquid-dividing branch pipe 252 is 3.36mm, and the included angle between the first plane and the second plane is 60 degrees, the maximum temperature difference between the fourth heat exchange branch pipe and the first three branch pipes is the smallest, the uniformity of the heat exchange capacity of the refrigerant in each heat exchange branch pipe is the best, and the heating capacity of the air conditioner is the largest. That is, the ratio of the amount of refrigerant in the first branch liquid-dividing pipe 251 to the amount of refrigerant in the second branch liquid-dividing pipe 252 is 3: 1.

Similarly, when 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, the inner diameter of the first branch liquid dividing pipe 251 is greater than or equal to 5.1mm and less than or equal to 6.1mm, and the inner diameter of the second branch liquid dividing pipe 252 is greater than or equal to 3.1mm and less than or equal to 3.7mm, the ratio of the refrigerant quantity in the first branch liquid dividing pipe 251 to the refrigerant quantity in the second branch liquid dividing pipe 252 can be better realized to be 3: 1. The temperature difference realized by other inner diameters and included angles and the heating capacity of the air conditioner in the embodiment are similar to the data in tables 2 and 3, and are not repeated here.

Similarly, when 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, the inner diameter of the first branch liquid dividing pipe 251 is greater than or equal to 5.1mm and less than or equal to 6.1mm, and the inner diameter of the second branch liquid dividing pipe 252 is greater than or equal to 3.1mm and less than or equal to 3.7mm, the ratio of the refrigerant quantity in the first branch liquid dividing pipe 251 to the refrigerant quantity in the second branch liquid dividing pipe 252 can be better realized to be 2: 1. The temperature difference realized by other inner diameters and included angles and the heating capacity of the air conditioner in the embodiment are similar to the data in tables 2 and 3, and are not repeated here. Optionally, when 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, the inner diameter of the first branch liquid dividing pipe 251 is greater than or equal to 5.1mm and less than or equal to 6.1mm, and the inner diameter of the second branch liquid dividing pipe 252 is greater than or equal to 3.1mm and less than or equal to 3.7mm, the ratio of the amount of refrigerant in the first branch liquid dividing pipe 251 to the amount of refrigerant in the second branch liquid dividing pipe 252 can be better realized to be 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, the inner diameter of the first branch liquid dividing pipe 251 is greater than or equal to 5.1mm and less than or equal to 6.1mm, and the inner diameter of the second branch liquid dividing pipe 252 is greater than or equal to 3.1mm and less than or equal to 3.7 mm. Optionally, the second pipe segment 242 of the collecting pipe 240 is disposed obliquely to the second branch liquid pipe 252 side.

TABLE 21

Optionally, when the air conditioner operates in a heating condition, the heat exchanger serves as an evaporator, and the first heat exchange branch, the second heat exchange branch, the third heat exchange branch, the fourth heat exchange branch, and the fifth heat exchange branch connected in parallel are communicated with the first liquid-dividing branch 251, and the sixth heat exchange branch is communicated with the second liquid-dividing branch 252, the refrigerant temperatures at the outlets of the heat exchange branches are as shown in tables 21 and 22. In table 21, when the included angle between the first plane and the second plane is 90 degrees, the maximum temperature difference between the sixth heat exchange branch and the first five branches and the heating capacity of the air conditioner are different under the inner diameters of the first liquid dividing branch 251 and the second liquid dividing branch 252. As can be seen from the data in table 21, when the inner diameter of the first branch 251 is 5.6mm, and the inner diameter of the second branch 252 is 3.36mm, the maximum temperature difference between the sixth heat exchange branch and the first five branches of the heat exchanger is the smallest, which is 3.1 ℃, and the heating capacity of the air conditioner is the largest at the inner diameter, which is 7287.6W. Table 22 shows that when the inner diameter of the first branch liquid dividing pipe 251 is 5.6mm, and the inner diameter of the second branch liquid dividing pipe 252 is 3.36mm, the included angle between the first plane and the second plane is different, the maximum temperature difference between the sixth heat exchange branch and the first five branches, and the heating capacity of the air conditioner. As can be seen from table 22, when the included 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 minimum and is 1.0 ℃, and the heating capacity of the air conditioner is maximum at this angle and is 7383.7W.

As can be seen from the data in tables 21 and 22, when the number of the heat exchange branches in the heat exchanger, which are communicated with the first branch liquid pipes 251, is 5, the number of the heat exchange branches in the heat exchanger, which are communicated with the second branch liquid pipes 252, is 1, the inner diameter of the first branch liquid pipes 251 is 5.6mm, the inner diameter of the second branch liquid pipes 252 is 3.36mm, and the included 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, a ratio of 5:1 of the amount of refrigerant in the first branch liquid-separating pipe 251 to the amount of refrigerant in the second branch liquid-separating pipe 252 is achieved.

Similarly, when 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, the inner diameter of the first branch liquid dividing pipe 251 is greater than or equal to 5.1mm and less than or equal to 6.1mm, and the inner diameter of the second branch liquid dividing pipe 252 is greater than or equal to 3.1mm and less than or equal to 3.7mm, the ratio of the refrigerant quantity in the first branch liquid dividing pipe 251 to the refrigerant quantity in the second branch liquid dividing pipe 252 can be better realized to be 5: 1. The temperature difference realized by other inner diameters and included angles and the heating capacity of the air conditioner in this embodiment are similar to the data in tables 21 and 22, and are not described herein again.

Similarly, when 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, the inner diameter of the first branch liquid dividing pipe 251 is greater than or equal to 5.1mm and less than or equal to 6.1mm, and the inner diameter of the second branch liquid dividing pipe 252 is greater than or equal to 3.1mm and less than or equal to 3.7mm, the ratio of the refrigerant quantity in the first branch liquid dividing pipe 251 to the refrigerant quantity in the second branch liquid dividing pipe 252 can be better realized to be 4: 1. The temperature difference realized by other inner diameters and included angles and the heating capacity of the air conditioner in this embodiment are similar to the data in tables 21 and 22, and are not described herein again. Optionally, when 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, the inner diameter of the first branch liquid dividing pipe 251 is greater than or equal to 5.1mm and less than or equal to 6.1mm, and the inner diameter of the second branch liquid dividing pipe 252 is greater than or equal to 3.1mm and less than or equal to 3.7mm, the ratio of the amount of refrigerant in the first branch liquid dividing pipe 251 to the amount of refrigerant in the second branch liquid dividing pipe 252 can be better realized to be 4:1-5: 1.

Optionally, the included angle between the first plane and the second plane is less than or equal to 10 degrees, the inner diameter of the first branch liquid-dividing pipe 251 is greater than or equal to 7.1mm and less than or equal to 8.1mm, and the inner diameter of the second branch liquid-dividing pipe 252 is greater than or equal to 3.1mm and less than or equal to 3.7 mm. Optionally, the second pipe segment 242 of the collecting pipe 240 is disposed obliquely to the second branch liquid pipe 252 side.

TABLE 23

Watch 24

Optionally, when the air conditioner operates in a heating condition, the heat exchanger serves as an evaporator, and the first heat exchange branch, the second heat exchange branch, the third heat exchange branch, the fourth heat exchange branch, the fifth heat exchange branch and the sixth heat exchange branch connected in parallel are communicated with the first liquid-dividing branch pipe 251, and the seventh heat exchange branch is communicated with the second liquid-dividing branch pipe 252, the refrigerant temperatures at the outlets of the heat exchange branches are as shown in tables 23 and 24. The maximum temperature difference between the seventh heat exchange branch and the first six branches and the heating capacity of the air conditioner are shown in table 23 when the included angle between the first plane and the second plane is 90 degrees, and the inner diameters of the first branch liquid distribution pipe 251 and the second branch liquid distribution pipe 252 are different. As can be seen from the data in table 23, when the inner diameter of the first branch 251 is 7.6mm, and the inner diameter of the second branch 252 is 3.36mm, the maximum temperature difference between the seventh heat exchange branch and the first six branches of the heat exchanger is minimum, 5.9 ℃, and the heating capacity of the air conditioner is maximum at the inner diameter, 9268.4W. Table 24 shows that when the inner diameter of the first branch liquid distribution pipe 251 is 7.6mm, and the inner diameter of the second branch liquid distribution pipe 252 is 3.36mm, the included angle between the first plane and the second plane is different, the maximum temperature difference between the seventh heat exchange branch and the first six branches and the heating capacity of the air conditioner are different. As can be seen from table 24, when the included angle between the first plane and the second plane is 0 degree, the maximum temperature difference between the seventh heat exchange branch and the first six branches is minimum and is 1.5 ℃, and at this angle, the heating capacity of the air conditioner is maximum and is 9544.5W.

As can be seen from the data in tables 23 and 24, when the number of the heat exchange branches in the heat exchanger, which are communicated with the first branch liquid pipes 251, is 6, the number of the heat exchange branches in the heat exchanger, which are communicated with the second branch liquid pipes 252, is 1, the inner diameter of the first branch liquid pipes 251 is 7.6mm, the inner diameter of the second branch liquid pipes 252 is 3.36mm, and the included angle between the first plane and the second plane is 0 degree, 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, a ratio of the amount of refrigerant in the first branch liquid-separating pipe 251 to the amount of refrigerant in the second branch liquid-separating pipe 252 is 6: 1.

Similarly, when the included angle between the first plane and the second plane is less than or equal to 10 degrees, the inner diameter of the first branch liquid dividing pipe 251 is greater than or equal to 7.1mm and less than or equal to 8.1mm, and the inner diameter of the second branch liquid dividing pipe 252 is greater than or equal to 3.1mm and less than or equal to 3.7mm, the ratio of the refrigerant amount in the first branch liquid dividing pipe 251 to the refrigerant amount in the second branch liquid dividing pipe 252 can be better realized to be 6: 1. The temperature difference realized by other inner diameters and included angles and the heating capacity of the air conditioner in this embodiment are similar to the data in tables 23 and 24, and are not described herein again.

Similarly, when the included angle between the first plane and the second plane is less than or equal to 10 degrees, the inner diameter of the first branch liquid dividing pipe 251 is greater than or equal to 7.1mm and less than or equal to 8.1mm, and the inner diameter of the second branch liquid dividing pipe 252 is greater than or equal to 3.1mm and less than or equal to 3.7mm, the ratio of the refrigerant amount in the first branch liquid dividing pipe 251 to the refrigerant amount in the second branch liquid dividing pipe 252 can be better realized to be 7: 1. The temperature difference realized by other inner diameters and included angles and the heating capacity of the air conditioner in this embodiment are similar to the data in tables 23 and 24, and are not described herein again. Optionally, when the included angle between the first plane and the second plane is less than or equal to 10 degrees, the inner diameter of the first branch liquid dividing pipe 251 is greater than or equal to 7.1mm and less than or equal to 8.1mm, and the inner diameter of the second branch liquid dividing pipe 252 is greater than or equal to 3.1mm and less than or equal to 3.7mm, the ratio of the amount of refrigerant in the first branch liquid dividing pipe 251 to the amount of refrigerant in the second branch liquid dividing pipe 252 can be preferably realized 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 degree. Optionally, the inner diameter of the first branch liquid dividing pipe 251 is greater than the inner diameter of the second branch liquid dividing pipe 252, and the second pipe segment 242 of the collecting pipe 240 is inclined toward the second branch liquid dividing pipe 252, so that more refrigerant flows into the first branch liquid dividing pipe 251 under the action of gravity, and the flow rate difference between the refrigerant in the first branch liquid dividing pipe 251 and the refrigerant in the second branch liquid dividing pipe 252 is increased.

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

Optionally, the second pipe segment 242 is disposed offset to the side of the second branch pipe 252. The second pipe segment 242 of the collecting pipe 240 is arranged towards the side of the second branch liquid pipe 252, and optionally, the inner diameter of the second branch liquid pipe 252 is smaller than that of the first branch liquid pipe 251. The difference in the flow rates of the refrigerant in the first branch liquid-separating pipe 251 and the refrigerant in the second branch liquid-separating pipe 252 is further increased by the difference in the inner diameters of the two branch pipes and the offset arrangement of the second pipe section 242.

Optionally, the length of the first tube segment 241 is less than or equal to 10 cm. Optionally, the first tube segment 241 has a length of 3cm, 4cm, 5cm, 6cm, 7cm, 8cm, or 9cm, etc. When the length of the first pipe section 241 is small, the refrigerant entering the first pipe section 241 from the second pipe section 242 tends to be biased toward the first liquid dividing port due to the centrifugal force, so that the requirement that the liquid dividing amount of the first liquid dividing port is larger than that of the second liquid dividing port is met. If the length of the first pipe section 241 is greater than 10cm, the tendency of the refrigerant to deflect to the first liquid dividing port due to the centrifugal force is weakened or even disappeared because the flow distance is too long, which is not favorable for realizing the requirement that the liquid dividing amount of the first liquid dividing port is greater than that of the second liquid dividing port.

Optionally, the length of the first tube segment 241 is less than or equal to 5 cm. Alternatively, the length of the first tube segment 241 may be 2cm, 2.5cm, 3cm, 3.5cm, 4cm, 4.2cm, 4.5cm, or 5cm, etc. When the length of the first pipe section 241 is less than or equal to 5cm, the refrigerant entering the first pipe section 241 from the second pipe section 242 has a more obvious tendency of deviating to the first liquid dividing port due to the centrifugal force, which is more favorable for realizing the requirement that the liquid dividing amount of the first liquid dividing port is greater than that of the second liquid dividing port.

Optionally, the second branch 252 has an inner diameter greater than or equal to 3 mm. Alternatively, the second branch 252 may have an inner diameter of 3mm, 3.36mm, 5mm, 10mm, 12mm, etc. As mentioned above, the inner diameter of the branch liquid-separating pipe has a minimum limit, for example, the inner diameter of the branch liquid-separating pipe cannot be less than 3mm, even not less than 3.36mm, the copper pipe below the inner diameter has actually become a capillary pipe, the capillary pipe has a large flow resistance, and forms a throttling and pressure-reducing effect on the flow of the refrigerant, so as to increase the power of the compressor and reduce the performance of the system; even when the air conditioner operates in a heating working condition, the outdoor heat exchanger is frosted seriously, and the safety and reliability of the system are affected. In the embodiment of the disclosure, the inner diameter of the second branch liquid pipe 252 is greater than or equal to 3mm, so that the flow resistance of the refrigerant in the second branch liquid pipe 252 is reduced, and the performance of the air conditioning system is improved.

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

Optionally, the numerical range of x is: x is more than or equal to 1.3 and less than or equal to 1.7. Optionally, x may take on a value of 1.4, 1.5, 1.6, or 1.7, etc. Optionally, the ratio of the number of heat exchange branches respectively communicating with the first branch liquid pipes 251 and the second branch liquid pipes 252 is less than 2. Alternatively, the number of the heat exchange branches communicated with the first branch liquid-dividing pipe 251 is 3, and the number of the heat exchange branches communicated with the second branch liquid-dividing pipe 252 is 2; alternatively, the number of the heat exchange branches communicated with the first branch liquid-dividing pipe 251 is 4, and the number of the heat exchange branches communicated with the second branch liquid-dividing pipe 252 is 3; alternatively, the number of the heat exchange branches communicated with the first branch liquid-dividing pipe 251 is 5, and the number of the heat exchange branches communicated with the second branch liquid-dividing pipe 252 is 4; alternatively, the number of heat exchange branches communicating with first tapping branch 251 is 5, the number of heat exchange branches communicating with second tapping branch 252 is 3, etc.

Optionally, the ratio of the cross-sectional area of the first branch knock-out tube 251 to the cross-sectional area of the second branch knock-out tube 252 is greater than x. Wherein x is a preset value. Optionally, the numerical range of x is: x is more than or equal to 1.3 and less than or equal to 1.7. Optionally, x may take a value of 1.4, 1.5, 1.6, 1.7, or the like. Alternatively, the ratio of the number of heat exchange branch pipes respectively communicating with the first branch liquid dividing pipe 251 and with the second branch liquid dividing pipe 252 is greater than or equal to 2. For example, the number ratio of the heat exchange branch pipes respectively communicated with the first branch liquid dividing pipe 251 and the second branch liquid dividing pipe 252 is 2:1-7:1, such as 2:1, 3:1, 4:1, 5:1, 6:1 or 7: 1.

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

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

Optionally, the numerical range of y is: y is more than or equal to 10 and less than or equal to 12. Optionally, y may take on a value of 10, 11, 12, or the like.

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

Optionally, the included angle α between the first pipe segment 241 and the housing is 30-75 degrees. Optionally, the angle α between the first tube segment 241 and the housing is 30 degrees, 35 degrees, 40 degrees, 45 degrees, 50 degrees, 60 degrees, 70 degrees, or 75 degrees. Fig. 22 shows a simulation effect diagram of the flow of the refrigerant in the liquid separator when the included angle between the first pipe segment 241 and the housing is 50 degrees. As can be seen from fig. 22, when the included angle between the first pipe segment 241 and the shell is 50 degrees, the amount of the refrigerant flowing into the first branch liquid-separating pipe 251 is much larger than the amount of the refrigerant flowing into the second branch liquid-separating pipe 252, and the refrigerant is distributed unevenly between the first branch liquid-separating pipe 251 and the second branch liquid-separating pipe 252. Fig. 23 shows a simulation effect diagram of the flow of the refrigerant in the liquid separator when the included angle between the first pipe segment 241 and the housing is 80 degrees. As can be seen from fig. 23, when the included angle between the first pipe segment 241 and the housing is 80 degrees, the difference between the amount of the refrigerant flowing into the first branch liquid dividing pipe 251 and the amount of the refrigerant flowing into the second branch liquid dividing pipe 252 is not large.

Optionally, the included angle α between the first pipe segment 241 and the housing is 45-60 degrees. As shown in fig. 14. Optionally, the angle α between the first tube segment 241 and the housing is 45 degrees, 50 degrees, 55 degrees, or 60 degrees.

Optionally, the inner diameter of the manifold 240 is larger than the inner diameter of the first tapping branch 251. As shown in fig. 15. Optionally, the inner diameter of the collecting pipe 240 is larger than the inner diameter of the first branch liquid diversion pipe 251, and the inner diameter of the first branch liquid diversion pipe 251 is larger than the inner diameter of the second branch liquid diversion pipe 252.

Optionally, a first area where the first branch cavity 235 communicates with the sink cavity 234 is larger than a second area where the second branch cavity 236 communicates with the sink cavity 234. Thus, more refrigerant can flow into the first branch liquid dividing pipe 251 through the first branch cavity 235, and the difference of the refrigerant amount flowing into the two branch liquid dividing pipes is increased.

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

Optionally, the numerical range of z is: z is more than or equal to 2 and less than or equal to 15. Optionally, z may take a value of 2, 3, 5, 8, 9, 10, 12, or the like. Alternatively, the ratio of the number of heat exchange branch pipes respectively communicating with the first branch liquid dividing pipe 251 and with the second branch liquid dividing pipe 252 is greater than or equal to 2. For example, the number ratio of the heat exchange branch pipes respectively communicating with the first branch liquid dividing pipe 251 and the second branch liquid dividing pipe 252 is 2:1-7:1, such as 2:1, 3:1, 4:1, 5:1, 6:1 or 7: 1. Alternatively, as mentioned above, the inner diameter of the two liquid branch pipes should be at least 3mm, even 3.36mm, and the inner diameter of the copper pipe used in the heat exchanger of the air conditioner at present is generally not more than 10.6 mm. Alternatively, for better preparation of the liquid separator, the ratio of the cross-sectional area of the first branch 251 to the cross-sectional area of the second branch 252 is less than or equal to 2.

Optionally, the numerical range of z is: z is more than or equal to 10 and less than or equal to 12. Optionally, z may take on a value of 10, 11, 12, or the like.

Optionally, the communication area of the manifold 240 with the first branch cavity 235 is larger than the communication area of the manifold 240 with the second branch cavity 236. Thus, more refrigerant can flow into the first branch liquid dividing pipe 251 through the first branch cavity 235, and the difference of the refrigerant amount flowing into the two branch liquid dividing pipes is increased.

Optionally, the cross-section of the manifold 240 comprises straight segments. The cross-section of the manifold 240 includes one or more straight segments, optionally disposed in communication with the second branch cavities 236.

Alternatively, the manifold 240 is a D-shaped tube or a triangular tube, as shown in fig. 20. Optionally, the straight section of the D-tube is disposed in communication with the second branch chamber 236.

Optionally, the manifold 240 is provided with a baffle towards the inside of the second branch chamber 236. The flow blocking portion blocks the refrigerant from flowing into the second branch chamber 236, so as to reduce the amount of the refrigerant flowing into the second branch liquid pipe 252.

Optionally, the axis of the first branch 251 is non-parallel to the centerline of the chamber. It can be understood that the first branch liquid-dividing pipe 251 is deviated to one side, and the flow amount of the refrigerant into the first branch liquid-dividing pipe 251 is reduced.

Optionally, the axis of the second branch 252 is non-parallel to the centerline of the branch chamber. It can be understood that the second branch liquid dividing pipe 252 is deviated to one side, and the flow amount of the refrigerant into the second branch liquid dividing pipe 252 is reduced, as shown in fig. 18.

Optionally, the axis of the first branch liquid distribution pipe 251 and the center line of the liquid distribution chamber form a first included angle, the axis of the second branch liquid distribution pipe 252 and the center line of the liquid distribution chamber form a second included angle, and the first included angle and the second included angle are not equal. The first included angle is not equal to the second included angle, so that the refrigerant flows to the first branch liquid dividing pipe 251 and the second branch liquid dividing pipe 252 in different amounts.

Optionally, the length of the first branch 251 extending into the chamber is less than the length of the second branch 252 extending into the chamber. As shown in fig. 19. The part of the second branch liquid distribution pipe 252 extending into the liquid distribution cavity is long, and the flow amount of the refrigerant flowing into the second branch liquid distribution pipe 252 is reduced, so that the refrigerant flows to the first branch liquid distribution pipe 251 and the second branch liquid distribution pipe 252 in different amounts. Fig. 24 shows a schematic flow distribution of the refrigerant in the first branch liquid-dividing pipe 251 and the second branch liquid-dividing pipe 252.

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

Optionally, the first axis of the manifold 240 is between the second axis of the first branch 251 and the third axis of the second branch 252. The first axis is between the second axis and the third axis such that the refrigerant in the manifold 240 may be distributed to the first branch liquid distribution pipe 251 and the second branch liquid distribution pipe 252 simultaneously.

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

Optionally, the inner diameter of first branch knock out leg 251 is greater than the inner diameter of second branch knock out leg 252. Wherein the axis of the collecting pipe 240 is offset to the first branch liquid dividing pipe 251 side. Thus, the flow rate of the refrigerant flowing into the first branch liquid-dividing pipe 251 is greater than that of the refrigerant flowing into the second branch liquid-dividing pipe 252.

Optionally, the liquid separator is disposed at the first refrigerant inlet and outlet 111, the collecting pipe 240 of the liquid separator is communicated with the first refrigerant inlet and outlet 111, and the number of the heat exchange branches communicated with the first liquid separation branch pipes 251 is different from the number of the heat exchange branches communicated with the second liquid separation branch pipes 252.

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

Optionally, the number of heat exchange branches communicating with first liquid dividing branch 251 of first liquid divider 211 is greater than or equal to 2. The number of the heat exchange branches communicated with the second branch liquid 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 check valve 311. One end of the first heat exchange branch 121 is connected with the second liquid separator 212; one end of the second heat exchange branch 122 is connected with a second liquid separator 212; one end of the fourth heat exchange branch 124 is connected to the first liquid separator 211; the first bypass line 151 connects the first and

second dividers

211 and 212, the first check valve 311 is disposed in the first bypass line 151, and the conducting direction of the first check valve 311 is defined as flowing from the first divider 211 to the second divider 212.

Optionally, the heat exchanger includes a gas collecting pipe, a first heat exchanging branch 121, a second heat exchanging branch 122, a third heat exchanging branch 123, a fourth heat exchanging branch 124, a first bypass line 151, a second bypass line 152, a first check valve 311, and a second check valve 312. A first end of the first heat exchange branch 121 is connected with a first pipe orifice of the gas collecting pipe, and a second end is connected with the second liquid separator 212; a first end of the second heat exchange branch 122 is connected with a second pipe orifice of the gas collecting pipe, and a second end is connected with the second liquid separator 212; a first end of the third heat exchange branch 123 is connected with the third liquid separator 213, and a second end is connected with the first liquid separator 211; a first end of the fourth heat exchange branch 124 is connected with the third liquid separator 213, and a second end is connected with the first liquid separator 211; the first bypass line 151 connects the first and

second dividers

211 and 212; the second bypass line 152 is connected with the third liquid separator 213 and the gas collecting pipe; the first check valve 311 is disposed in the first bypass line 151, and a conducting direction of the first check valve 311 is defined as flowing from the first dispenser 211 to the second dispenser 212; the second check valve 312 is disposed on the second bypass line 152, and a conducting direction of the second check valve 312 is defined as flowing from the third liquid distributor 213 to the gas collecting pipe.

Optionally, the cooling flow is downward, and a flow path of the refrigerant in the heat exchanger is: the refrigerant enters through the gas collecting pipe and is divided into two paths, the first path flows through the first heat exchange branch 121, the second path flows through the second heat exchange branch 122, the two paths converge at the second liquid separator 212, flow through the third heat exchange branch 123, flow 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, the heat exchanger provided by the embodiment of the present disclosure has the advantages that the refrigerant flows downwards, due to the arrangement of the first check valve 311 and the second check valve 312, the length of the refrigerant path flowing downwards in the refrigeration flow direction is increased, the heat exchange time of the refrigerant in the heat exchanger is prolonged, the refrigerant can fully exchange heat with the surrounding environment, the number of branches through which the refrigerant flows is small, the flow rate is high, the heat exchange effect of the heat exchanger is improved, and further, the refrigeration efficiency of the air conditioner is improved.

Optionally, the refrigerant is divided into four paths in the downward heating flow direction, and the first path passes through the first check valve 311 and the second liquid separator 212, flows through the first heat exchange branch 121, and flows out after passing through the gas collecting pipe; the second branch passes through the first check 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 check valve 311 and the second liquid separator 212, flows through the third heat exchange branch 123, passes through the third liquid separator 213, the second check valve 312 and the gas collecting pipe, and then flows out; the fourth branch passes through the fourth heat exchange branch 124, passes through the third liquid distributor 213, the second check valve 312 and the gas collecting pipe, and then flows out. It can be seen that, in the heat exchanger provided by the embodiment of the present disclosure, due to the arrangement of the first check valve 311 and the second check valve 312, the first heat exchange branch 121, the second heat exchange branch 122, the third heat exchange branch 123 and the fourth heat exchange branch 124 are connected in parallel and communicated, at this time, the number of branches through which the refrigerant flows is large, the problem of pressure loss caused by too long flow path is avoided, the heat exchange efficiency of the heat exchanger is improved, and further the heating efficiency of the air conditioner is improved.

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

Considering that the branch liquid separating pipe of the liquid separator needs to have a certain insertion depth, and meanwhile, the branch liquid separating pipe and the shell wall of the liquid separator need to have a certain distance so as not to obstruct the flow of the refrigerant; under the refrigeration working condition, the refrigerant flows in from the branch liquid pipes and flows out from other branch liquid pipes after being bent for 180 degrees, and at the moment, the refrigerant circulation in the branch liquid cavity is not influenced by the bottom of the cavity, so the height of the liquid separator cannot be too small, if the length-diameter ratio of the branch liquid cavity is too small, the corresponding diameter of the liquid separator is too large, the pipeline space of the outdoor unit is difficult to arrange, and the lower limit of the length-diameter ratio of the liquid separator is determined by the limiting conditions of the liquid separator and the outdoor unit. Therefore, as shown in FIG. 25, optionally, the length-diameter ratio L1/D ≧ a1 of the liquid-separating chamber 230, where a1 is a first predetermined ratio.

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

For the liquid separator in the embodiment of the disclosure, on one hand, the branch liquid separating pipe needs to be inserted into the liquid separator for a certain depth, and the specific depth depends on the actual size of the liquid separator; taking a model with rated refrigerating capacity of 3.5KW as an example, the insertion depth generally reaches at least 0.2R; on the other hand, under the refrigeration working condition, the refrigerant flows in from the branch liquid pipe, bends 180 degrees and flows out from the last branch liquid pipe, the length from the lower end of the branch liquid pipe to the bottom of the branch liquid chamber needs to be a certain length, generally reaches at least about 1R, the length-diameter ratio is at least about 1.2R, meanwhile, the lower limit value of L/D is 0.3-0.8 in consideration of certain difference of units with different capacities and different refrigerant types.

In this embodiment, the performance data of the liquid separator defined by the above lower limit of the length-diameter ratio and the performance data of the liquid separator exceeding the lower limit of the length-diameter ratio are respectively tested in a three-way split mode, the test conditions are 27 ℃/19 ℃ in an indoor condition, 35 ℃/24 ℃ in an outdoor condition, and the other operating states of the air conditioner are the same, and the test data are shown in the following table 25:

TABLE 25

Aspect ratio	Capability of	Power of	Energy efficiency
				0.2	3379.8W	888.7W	3.80
0.5	3436.3W	863.7W	3.98

As can be seen from the above table, in the case where the aspect ratio is smaller than the minimum value of 0.3 of the lower limit value, the air conditioner is rather lower in energy efficiency in the case where the power is larger, and in the case where the aspect ratio is larger than the minimum value of 0.3 of the lower limit value, the air conditioner can achieve more excellent operation energy efficiency.

The draw ratio lower limit of the liquid separating cavity limited by the embodiment is adopted to limit, the problems that the refrigerant is too much accumulated in the liquid separator and the circulation quantity of the refrigerant of the air conditioner is influenced can be avoided, and meanwhile, the power loss can be effectively reduced.

Optionally, the length L1 ≧ b1 of the dispensing chamber 230, where b1 is the first length threshold.

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

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

In still other embodiments, the headspace height of the dispenser is typically within 10cm, while the diameter of the dispenser is typically above 2cm, so that the definition of the two dictates that the aspect ratio of the dispenser is typically within 5; in addition, in order to realize liquid storage, a certain volume of the liquid distributor needs to be ensured, the liquid distributor is slender according to the same height, the volume is smaller, and the liquid distributor also has an influence factor.

When the heat exchanger is used as a condenser, the liquid distributor needs to have a liquid storage function, and when the height of the liquid distributor is fixed, the larger the length-diameter ratio is, the smaller the diameter of the liquid distributor is, the smaller the volume of the liquid distribution cavity is, and the smaller the liquid storage amount is; the larger the length-diameter ratio is, the more slender the liquid distributor is, the closer the distance between the liquid distributing branches is, the mutual influence is easy to occur, and the final flow distributing effect is influenced; meanwhile, the refrigerant flows into the branch liquid separating pipe, is bent by 180 degrees and then flows out of other branch liquid separating pipes, and if the liquid separator is too thin and long, the refrigerant can be influenced by the side wall of the liquid separating cavity in the flowing process; when the diameter of the liquid distributor is fixed, the larger the length-diameter ratio is, the larger the height of the distributor is, the larger the occupied space in the pipe group is, and the compatibility is difficult. Therefore, the upper limit of the length-diameter ratio of the liquid separation cavity a2 cannot be too large, and the length-diameter ratio L1/D of the liquid separation cavity 230 is less than or equal to a 2. a2 is a second preset proportion value which is larger than a 1.

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

In a further alternative,

that is to say

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

For example, in this embodiment, the performance data of the liquid separator defined by the above lower limit of the length-diameter ratio and the liquid separator exceeding the lower limit of the length-diameter ratio are respectively tested in a four-way split manner under the conditions of 27 ℃/19 ℃ for indoor conditions, 35 ℃/24 ℃ for outdoor conditions, and the same other operating states of the air conditioner, and the test data are shown in the following table 26:

watch 26

Aspect ratio	Capability of	Power of	Energy efficiency
				2.8	3421.6W	865.1W	3.96
4.3	3387.1W	905.7W	3.74

As can be seen from the above table, in the case where the aspect ratio is greater than the maximum value 3 of the upper limit value, the air conditioner is rather lower in energy efficiency in the case where the power is higher, and in the case where the aspect ratio is less than the maximum value 3 of the upper limit value, the air conditioner can achieve more excellent operation energy efficiency.

Optionally, the length L1 ≦ b2 of the dispensing chamber 230, where b2 is a second length threshold greater than b 1.

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

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

Alternatively, as shown in fig. 26 to 28, the liquid-separating chamber 230 includes a first liquid-storing chamber 231 communicated with the manifold 240 and a second liquid-storing chamber 232 communicated with the first liquid-separating port and the second liquid-separating port.

Optionally, the first reservoir 231 and the second reservoir 232 are in communication via a reservoir channel 233 of reduced bore.

The beneficial effect who adopts above-mentioned scheme design lies in: when the heat exchanger is used as a condenser, the refrigerant is in a gas-liquid two-phase state at the moment and occupies a large volume, and the second liquid storage cavity of the liquid separator has the functions of converging and dividing the flow, so that the refrigerant can be turned back at 180 degrees, and the pressure loss is reduced; the first liquid storage cavity is positioned below the second liquid storage cavity, liquid refrigerants are gathered at the bottom under the action of gravity, the liquid storage effect is achieved, the impact of the refrigerants in the second liquid storage cavity is reduced due to the fact that the middle channel is narrow, the state of the liquid refrigerants is stable, the impact on a check valve connected with the first liquid dividing cavity can be reduced, and the sealing performance is better; when the heat exchanger uses as the evaporimeter, the refrigerant reverse flow can make more refrigerants participate in the circulation, satisfies refrigerant circulation demand, and first stock solution chamber can have the muffler effect concurrently simultaneously, eliminates refrigerant flow noise.

Optionally, the volume of the first liquid storage cavity 231 is greater than or equal to that of the second liquid storage cavity 232, so that more liquid refrigerants can be stored, and the liquid storage amount is increased; simultaneously first stock solution chamber adopts bigger volume form to set up, also can improve the cushioning effect to the refrigerant flow to and utilize bigger cavity to carry out the amortization when using as "muffler".

Optionally, the volume v1 ═ c1 × Q of the first reservoir 231, where v1 is the volume of the first reservoir in cm³And Q is rated refrigerating capacity and is measured in kW.

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

Optionally, the volume v2 of the second reservoir 232 is c 2Q, where v2 is the volume of the first reservoir in cm³And Q is rated refrigerating capacity and is measured in kW.

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

In the present embodiment, under the condition of liquid storage of the liquid separator, the first liquid storage cavity 231 mainly contains liquid refrigerant, which has higher density and higher quality of the refrigerant stored in the same volume; the second liquid storage cavity 232 mainly contains gas-liquid mixed refrigerant, the density of the refrigerant is low, and the quality of the refrigerant stored under the same volume is low; in order to meet the capacity requirement that the liquid storage quantity of the liquid separator needs to reach about 5% of the total filling quantity, the volume range proportion of the first liquid storage cavity and the second liquid storage cavity is respectively set according to the change condition of the refrigerant density of the two liquid storage cavities in the running process of the air conditioner under different loads during testing, so that the first liquid storage cavity 231 is used for containing refrigerants with more quality, and the sum of the refrigerant storage quantities of the first liquid storage cavity 231 and the second liquid storage cavity 232 can meet the capacity requirement.

Optionally, the liquid storage cavity channel 233 comprises a circular pipe section, two ports of the circular pipe section are configured as tapered ports with gradually increasing diameters, the tapered ports can facilitate the refrigerant to flow more smoothly between the liquid storage cavity channel and the liquid storage cavity, and the problem of turbulent flow and the like caused by flow area change in the flowing process of the refrigerant and the liquid storage cavity is reduced.

Optionally, the length of the reservoir 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 collecting pipe 240, in this embodiment, the flow resistance of the refrigerant flowing through the collecting pipe and the liquid separator during the liquid separation process can be reduced when the heat exchanger is used as an evaporator, and the refrigerant flow is accelerated to ensure the heat exchange performance of the heat exchanger.

For example, in this embodiment, taking an air conditioner with a rated cooling capacity of 7.2Kw as an example, performance data of both the rated cooling and the rated heating using a common dispenser and a dispenser as claimed in this application were respectively tested, and the test data is as shown in the following table 27:

watch 27

According to the data, under the rated refrigeration working condition, the energy efficiency COP which can be achieved by the air conditioner is higher than the test data of the air conditioner adopting the common liquid separator under the condition that the actually measured power is lower.

Optionally, as shown in fig. 29, a mesh 260 is disposed in the liquid separation chamber 230, and is used for filtering or dispersing the refrigerant flowing through the liquid separation chamber 230.

In this embodiment, as shown in fig. 30, the mesh 260 mainly functions to break up large liquid droplets and air bubbles to form a turbulent flow region, and the gas-liquid two-phase refrigerant after being broken up needs to be mixed at the upper portion of the mesh structure, so as to ensure uniform distribution of the refrigerant entering the branch pipes, and uniform distribution of the gas-liquid two-phase refrigerant flowing in through the collecting pipe when flowing into the liquid separating branch pipe.

Optionally, the net member 260 is disposed at the height 1/4-3/4 of the liquid separation chamber.

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

In some embodiments, the mesh 260 is a planar mesh structure perpendicular to the axis of the dispensing chamber 230. In still other embodiments, the mesh 260 is an arcuate mesh with a concave center toward the dispensing opening.

Table 28 below shows several porosities and corresponding parameters for the wire mesh,

watch 28

As shown in the above table, the smaller the number of holes, the larger the hole diameter, the more difficult it is to break up the large droplets and bubbles, and the larger the number of holes, the larger the pressure drop at that position, and the disadvantage of refrigerant flow. Therefore, a 60-120 mesh wire mesh is selected.

Meanwhile, simulation analysis is performed on the nets with different hole numbers and wire diameters built in the liquid distributors with the same specification, and simulation test data are shown in fig. 31 and 32, wherein the unevenness and the instability of the fluid flowing through the nets with 80 meshes and 100 meshes are kept at a low level and are lower than those of the venturi distributor, so that the porosity of the preferable net is 100 meshes, the wire diameter is 0.1mm, and the unevenness and the instability of the net are the lowest values.

Referring to fig. 33, 34a and 34b, an alternative check 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 the valve outlet 322 and the valve inlet 321. The valve core 330 is axially movably disposed in the valve passage, so as to implement conduction/blocking switching of the check valve.

As shown in fig. 35, the length between the two end points of the valve body 330 is set to L2, and the equivalent diameter of the end surface of the valve body 330 at the end corresponding to the valve outlet 322 is set to D.

Optionally, the ratio of L2/D is greater than or equal to e 1. e1 is the first predetermined ratio. Through the slenderness ratio to the check valve case be provided with the lower limit value to reduce the condition such as case and valve casing inner wall vibration collision, noise that the slenderness ratio undersize leads to and appear, adopt the check valve that this embodiment was injectd, it can make the refrigerant flow through the check valve in-process case can keep better stationarity.

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

Still alternatively, the ratio of L2/D is less than or equal to e 2. e2 is a second predetermined ratio greater than e 1. The length-diameter ratio of the valve core of the one-way valve is provided with an upper limit value, and the effect of reducing wall vibration collision and noise can be achieved, so that the valve core can keep good stability.

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

Illustratively, for the same air conditioner, under the same test condition, noise data of a common one-way valve and the one-way valve to be protected by the application are respectively tested, wherein the test condition is that 0.05MPa nitrogen is introduced into the lower port of a valve core, the atmosphere is introduced into the upper port, and the noise value is tested at a position 1m away from the valve body; the test data is shown in table 29 below:

TABLE 29

e value	Noise test results
		0.45	Noise value 33.3dB (A), abnormal sound of slight valve core collision positioning pin
0.5	Noise value 33.3dB (A) and no abnormal sound
		1.16	Noise value 33.1dB (A), no noise
2	Noise value of 35.3dB (A) and no abnormal sound
		2.32	Noise value 35.8dB (A), abnormal sound of valve core colliding with pipe wall

From the comparison of the data, when the length-diameter ratio L2/D (e is 0.45) of the valve core is smaller than e1 or L2/D (e is 2.32) is larger than e2, the abnormal sound of the valve core hitting the positioning pin slightly exists, the noise test result is poor, and when the length-diameter ratio of the valve core is within the range of e1 and e2, the measured noise is low, and the low-noise operation can be realized.

Alternatively, as shown in fig. 36 to 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 part of the valve core can increase the contact area of the superheated refrigerant and the end surface of the valve core and increase the stress area of the valve core; meanwhile, the hollow structure is symmetrically designed around the central line of the valve core, and the stability of closing the valve core can be improved by fully storing a refrigerant in the hollow structure

Alternatively, as shown in connection with fig. 36, 37a and 37b, the hollow structure includes a hollow groove 335 formed from an end surface of the first end to be recessed in the axial direction.

Optionally, the radial cross-section of the hollow slot 335 is circular or diamond or triangular.

Optionally, the groove base of the hollow groove 335 is configured planar or concave conical.

In some alternative embodiments, the design parameters of the hollow slot 335 meet the requirements set forth in table 30 below:

watch 30

D is D2/D1, D2 is the equivalent diameter of the hollow groove, and D1 is the equivalent diameter of the valve core; h is H2/H1, H2 is the equivalent length of the hollow groove, and H1 is the equivalent length of the valve core; v is V2/V1, V2 is hollow groove volume, and V1 is valve core solid volume.

In this embodiment, for the same air conditioner, under the same test conditions, refrigerant leakage data of the check valves (plum blossom-shaped valve core, square solid valve core) in two valve core forms in the prior art and the check valve adopting the hollow groove design of the present application are respectively tested, the test conditions are that 0.02MPa nitrogen is introduced, and the test data are as shown in the following table 31:

watch 31

Valve core form	Quincunx valve core	Cubic solid valve core	Valve core with hollow groove
				Leakage rate of refrigerant	257ml/min	143ml/min	91ml/min

It can be seen through above-mentioned data contrast that the refrigerant leakage volume of the case of taking hollow groove that this application adopted is lower, and sealed effect is better.

In still other alternative embodiments, as shown in connection with fig. 37c, the hollow structure includes a closed hollow cavity 336 formed within the valve core 330.

Alternatively, as shown in fig. 37c, the body of the valve core 330 includes a cylindrical section near the outlet side of the valve and a conical section near the inlet side of the valve, wherein the hollow cavity 336 is formed primarily in the cylindrical section portion.

The hollow cavity 336 can play a role in reducing the weight of the cylindrical section of the valve core, so that the gravity of the whole valve core moves downwards, the gravity can be concentrated on the conical section more, and the stability of the valve core is kept in the sealing process of the valve core.

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

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

Optionally, the value range of the ratio of the axial length of the hollow cavity to the axial length of the cylindrical section of the valve core is 1/5-4/5.

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

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

In this embodiment, the density of the stabilizing block 334 is greater, so that the stabilizing block plays a role of weighting the tapered end portion, so that the center of gravity of the whole valve element moves downward, gravity can be concentrated on the tapered section more, and the stability of the valve element is kept in the process of closing the valve element.

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

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

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

Claims

1. A heat exchanger, comprising;

the liquid separating and storing device is provided with a confluence pipe orifice communicated with the refrigerant inlet and outlet and a plurality of liquid separating ports communicated with the plurality of heat exchange branches one by one;

the flow dividing and liquid storing device is configured to be used for dividing the refrigerant conveyed by the refrigerant inlet and outlet to the plurality of heat exchange branches under the condition that the heat exchanger serves as an evaporator, and converging and storing the refrigerant under the condition that the heat exchanger serves as a condenser.

2. The heat exchanger according to claim 1, wherein the liquid separating and storing device comprises a second liquid separator, the second liquid separator is provided with a liquid separating cavity, and the confluence pipe orifice and the plurality of liquid separating orifices which are communicated with the liquid separating cavity;

and at least one liquid inlet and at least one liquid outlet in the liquid separating ports are used as condensers of the heat exchanger, so that the liquid separators converge and the liquid separating cavities store part of refrigerants.

3. The heat exchanger of claim 2, wherein the liquid separation chamber satisfies the following relationship:

v is not less than f 1Q, and/or, V is not more than f 2Q,

wherein f1 and f2 are preset multiples, V is the volume of the liquid separation cavity, and the unit is cm³And Q is rated refrigerating capacity and is measured in kW.

4. The heat exchanger of claim 2, wherein the fluid distribution chamber has a first fluid storage chamber communicating with the manifold port and a second fluid storage chamber communicating with the fluid distribution port, the first fluid storage chamber and the second fluid storage chamber being in communication via a fluid storage chamber passage having a narrowed diameter.

5. The heat exchanger according to claim 4, wherein the volume v1 ═ c1 × Q of the first reservoir, c1 ranges from 3 to 10, and v1 is the volume of the first reservoir in cm³And Q is rated refrigerating capacity and is measured in kW.

6. The heat exchanger according to claim 4, wherein the volume v2 ═ c2 × Q of the second reservoir, c2 ranges from 1.5 to 5, and v2 is the volume of the second reservoir in cm³And Q is rated refrigerating capacity and is measured in kW.

7. The heat exchanger of claim 1, wherein the one-way conduction means comprises:

the one-way valve is provided with a valve outlet communicated with the confluence pipe orifice and a valve inlet communicated with the corresponding refrigerant inlet and outlet, the one-way valve is in a conducting state when a refrigerant flows from the valve inlet to the valve outlet, and the one-way valve is in a blocking state when the refrigerant flows from the valve outlet to the valve inlet; or,

an electrically controlled valve configured to be controlled open in the case of the heat exchanger acting as an evaporator and controlled closed in the case of the heat exchanger acting as a condenser.

8. The heat exchanger of claim 7, wherein the one-way valve comprises:

a valve housing having a valve outlet and a valve inlet and a valve passage formed inside the valve housing and communicating the valve outlet and the valve inlet;

and the valve core is movably arranged in the valve channel along the axial direction, wherein a first end of the valve core, which corresponds to the valve outlet, is provided with a hollow structure, and the hollow structure comprises a closed hollow cavity formed inside the valve core.

9. The heat exchanger of claim 8, wherein the hollow cavity is circular in radial cross-section.

10. The heat exchanger of claim 7, wherein the one-way valve comprises:

the valve core comprises a valve core main body and a stabilizing block, wherein the material density of the valve core main body is smaller than that of the stabilizing block; the stabilizing block is configured as a tapered end portion of the valve cartridge body corresponding to the second end of the valve inlet, or is encapsulated within the valve cartridge body and disposed proximate to the second end.

11. The heat exchanger of claim 1, further comprising a first liquid separator, the first liquid separator comprising:

the liquid separation device comprises a shell, a liquid separation device and a liquid separation device, wherein a liquid separation cavity is formed in the shell, and a first liquid separation port and a second liquid separation port are formed in the shell;

the first liquid separation branch pipe is communicated with the liquid separation cavity through the first liquid separation port; and,

the second liquid dividing branch pipe is communicated with the liquid dividing cavity through the second liquid dividing port;

the collecting pipe is communicated with the liquid separating cavity through the collecting pipe opening;

wherein the inner diameter of the first branch liquid-dividing pipe is larger than that of the second branch liquid-dividing pipe.

12. The heat exchanger according to claim 11, wherein the manifold comprises a first pipe section and a second pipe section which are connected in a bending way, the first pipe section is directly connected with the liquid dividing cavity, the plane of the axes of the first pipe section and the second pipe section is a first plane, the plane of the axes of the first liquid dividing branch pipe and the second liquid dividing branch pipe is a second plane, and the first plane and the second plane are not perpendicular.

13. The heat exchanger of claim 12, wherein the first plane is angled less than 90 degrees from the second plane.

14. The heat exchanger of claim 13, wherein the first plane is at an angle of 0 degrees, 30 degrees, 50 degrees, 60 degrees, 70 degrees, or 80 degrees to the second plane.

15. The heat exchanger according to any one of claims 11 to 14, wherein a ratio of a cross-sectional area of the first branch liquid-dividing line to a cross-sectional area of the second branch liquid-dividing line is less than or equal to x, wherein x is a preset value.

16. The heat exchanger of claim 15, wherein the range of values for x is: x is more than or equal to 1.3 and less than or equal to 1.7.

17. A refrigeration cycle system comprising a heat exchanger as claimed in any one of claims 1 to 16.

18. The refrigeration cycle system as set forth in claim 17, wherein said one-way conduction means includes a one-way valve, said one-way valve satisfying the following relationship:

L₃ ⁴*R≤Z1，

wherein L is₃The diameter of the throat part of the valve body of the one-way valve is measured in cm, and R is the valve core of the one-way valveEquivalent radius, in cm; z1 is the set value.

19. The refrigeration cycle system of claim 18, wherein Z1 is determined according to a rated cooling capacity Q of the refrigeration cycle system.

20. The refrigeration cycle system according to claim 19, wherein the larger the rated cooling capacity Q of the refrigeration cycle system, the larger Z1 is.

21. The refrigeration cycle system according to claim 19,

in the case of Q of 3.5kW, Z1 ═ 2.8; and/or the presence of a gas in the gas,

in the case of Q of 5.0kW, Z1 ═ 5.7; and/or the presence of a gas in the gas,

in the case of Q of 7.2kW, Z1 is 11.9.

22. The refrigeration cycle system according to claim 19,

Z1＝(z₂*λ*Q²)/(ρ_{agent for treating cancer}*ρ_Core)，

Where ρ is_{Agent for treating cancer}Is the density of the refrigerant in kg/m³Meter, p_CoreThe unit is the valve core density of the one-way valve in kg/m³In the formula, λ is a local resistance coefficient, z₂Are weighting coefficients.

23. The refrigeration cycle system of claim 22, wherein z is₂＝1.5*10⁵。

24. An air conditioner characterized by comprising the heat exchanger according to any one of claims 1 to 16; and/or the presence of a gas in the gas,

a refrigeration cycle system as claimed in any one of claims 17 to 23.