CN216977017U

CN216977017U - Heat pump system and air conditioner

Info

Publication number: CN216977017U
Application number: CN202123086451.6U
Authority: CN
Inventors: 马强; 齐兆乾; 王飞; 张心怡; 李阳; 吴丽琴; 于文文
Original assignee: Qingdao Haier Air Conditioner Gen Corp Ltd; Qingdao Haier Smart Technology R&D Co Ltd; Qingdao Haier Air Conditioning Electric Co Ltd; Haier Smart Home Co Ltd
Current assignee: Qingdao Haier Air Conditioner Gen Corp Ltd; Qingdao Haier Smart Technology R&D Co Ltd; Qingdao Haier Air Conditioning Electric Co Ltd; Haier Smart Home Co Ltd
Priority date: 2021-12-09
Filing date: 2021-12-09
Publication date: 2022-07-15
Anticipated expiration: 2031-12-09

Abstract

The application relates to the technical field of intelligent household appliances and discloses a heat pump system, which comprises: the defrosting device comprises a compressor, a heat exchanger, a first check valve and a first defrosting loop. The heat exchanger comprises a first refrigerant inlet and outlet, a second refrigerant inlet and outlet, a first heat exchange pipeline and a second heat exchange pipeline, wherein the first heat exchange pipeline and the second heat exchange pipeline are connected between the first refrigerant inlet and outlet and the second refrigerant inlet and outlet in parallel; the first check valve is arranged between the first heat exchange pipeline and the second heat exchange pipeline, and the conduction direction of the first check valve is that the first check valve is conducted from the first refrigerant inlet and outlet towards the second refrigerant inlet and outlet; one end of the first defrosting loop is communicated with a high-temperature refrigerant outlet of the compressor, the other end of the first defrosting loop is communicated with an outlet end of the first one-way valve, and the first defrosting loop is provided with a first electromagnetic valve. The heat exchanger can give consideration to both refrigeration and defrosting by adopting fewer electromagnetic valves matched with one-way valves, so that indoor heating stop can be avoided, the cost is reduced, and the running stability of the system is improved. The application also discloses an air conditioner.

Description

Heat pump system and air conditioner

Technical Field

The application relates to the technical field of intelligent household appliances, for example, to a heat pump system and an air conditioner.

Background

At present, when a heat pump system operates at a low temperature, an outdoor condenser frosts to influence heat exchange performance, refrigeration is reversely operated to defrost after a certain time, heating in a room is stopped, and therefore the indoor temperature is reduced, and the comfort of a user is reduced.

In the related art, a plurality of electromagnetic valves are adopted to control a flow path, and a heat exchanger is designed in a segmented manner, so that partial areas of the heat exchanger can be defrosted, and the rest parts of the heat exchanger can work normally, thereby avoiding indoor heating stop. But the structure is comparatively complicated and a plurality of solenoid valves are adopted, so that the cost is higher, and the solenoid valves are damaged, so that the system is not stable enough.

Therefore, how to avoid stopping heating indoors, reduce the overall cost, and improve the stability of system operation becomes a technical problem to be solved urgently by technical personnel in the field.

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 nor is intended to identify key/critical elements or to delineate the scope of such embodiments but rather as a prelude to the more detailed description that is presented later.

The embodiment of the disclosure provides a heat pump system and an air conditioner, so that a heat exchanger can perform both refrigeration and defrosting by adopting fewer electromagnetic valves matched with one-way valves, indoor heating stop can be avoided, cost is reduced, and the stability of system operation is improved.

In some embodiments, a heat pump system comprises: the defrosting device comprises a compressor, a heat exchanger, a first check valve and a first defrosting loop. The heat exchanger comprises a first refrigerant inlet and outlet, a second refrigerant inlet and outlet, a first heat exchange pipeline and a second heat exchange pipeline, wherein the first heat exchange pipeline and the second heat exchange pipeline are connected between the first refrigerant inlet and outlet and the second refrigerant inlet and outlet in parallel; the first check valve is arranged between the first heat exchange pipeline and the second heat exchange pipeline, and the conduction direction of the first check valve is that the first check valve is conducted from the first refrigerant inlet and outlet towards the second refrigerant inlet and outlet; one end of the first defrosting loop is communicated with a high-temperature refrigerant outlet of the compressor, the other end of the first defrosting loop is communicated with an outlet end of the first one-way valve, and the first defrosting loop is provided with a first electromagnetic valve.

In some embodiments, an air conditioner includes: the heat pump system of any of the above.

The heat pump system and the air conditioner provided by the embodiment of the disclosure can realize the following technical effects:

the heat exchanger is divided into a first heat exchange pipeline and a second heat exchange pipeline, wherein a first one-way valve is arranged between the first heat exchange pipeline and the second heat exchange pipeline, when defrosting is needed, an electromagnetic valve on a first defrosting loop is opened, high-temperature refrigerant discharged by a compressor is led to an outlet end of the first one-way valve through the first defrosting loop, the outlet end of the one-way valve faces the first heat exchange pipeline, the first one-way valve is closed under the pressure action of the high-temperature refrigerant entering the first defrosting loop, the high-temperature refrigerant can only flow to the first heat exchange pipeline under the interception action of the one-way valve, and at the moment, low-temperature refrigerant normally flows in the second heat exchange pipeline, so that the second heat exchange pipeline keeps normal evaporation refrigeration, the high-temperature refrigerant in the first heat exchange pipeline is liquefied to release heat, the first heat exchange pipeline is defrosted, and the heat exchanger can take refrigeration and defrosting into account by adopting fewer electromagnetic valves to match with the one-way valve, the indoor heating stop can be avoided, the cost is reduced, and the stability of the system operation is improved.

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 pump system according to an embodiment of the present disclosure;

FIG. 2 is a schematic diagram of another heat pump system according to an embodiment of the present disclosure;

fig. 3 is a schematic structural view of a water pan provided in the embodiment of the present disclosure;

FIG. 4 is a schematic diagram of another heat pump system according to an embodiment of the present disclosure;

fig. 5 is a schematic structural diagram of a first liquid separator according to an embodiment of the present disclosure.

Reference numerals:

100. a compressor; 200. a heat exchanger; 201. a first check valve; 202. a first refrigerant inlet and outlet; 203. a second refrigerant inlet and outlet; 204. a first heat exchange line; 205. a second heat exchange line; 206. a water pan; 207. a water leakage hole; 208. a first branch pipe; 209. a second branch pipe; 300. a first defrost circuit; 301. a first solenoid valve; 400. a first liquid separator; 500. a second one-way valve; 600. a second defrost circuit.

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 cases, well-known structures and heat pump systems may be shown for simplicity.

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 embodiments thereof, and are not intended to limit the indicated heat pump systems, 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; either directly or indirectly through an intermediary, or internal communication between two heat pump systems, 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.

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.

As shown in fig. 1-5, an embodiment of the present disclosure provides a heat pump system including: compressor 100, heat exchanger 200, first check valve 201, first defrost circuit 300. The heat exchanger 200 comprises a first refrigerant inlet and outlet 202, a second refrigerant inlet and outlet 203, a first heat exchange pipeline 204 and a second heat exchange pipeline 205, wherein the first heat exchange pipeline 204 and the second heat exchange pipeline 205 are connected in parallel between the first refrigerant inlet and outlet 202 and the second refrigerant inlet and outlet 203; the first check valve 201 is disposed between the first heat exchange pipeline 204 and the second heat exchange pipeline 205, and the conduction direction thereof is from the first refrigerant inlet/outlet 202 to the second refrigerant inlet/outlet 203; one end of the first defrost circuit 300 is communicated with the high-temperature refrigerant outlet of the compressor 100, and the other end is communicated with the outlet end of the first check valve 201, and the first defrost circuit 300 is provided with a first solenoid valve 301.

By adopting the heat pump system provided by the embodiment of the disclosure, the heat exchanger 200 is divided into a first heat exchange pipeline 204 and a second heat exchange pipeline 205, wherein a first check valve 201 is arranged between the first heat exchange pipeline 204 and the second heat exchange pipeline 205, when defrosting is required, a first electromagnetic valve 301 on a first defrosting loop 300 is opened, a high-temperature refrigerant discharged by the compressor 100 passes through the first defrosting loop 300 and flows to an outlet end of the first check valve 201, wherein the outlet end of the check valve faces towards the first heat exchange pipeline 204, under the pressure action of the high-temperature refrigerant entering the first defrosting loop 300, the first check valve 201 is closed, the high-temperature refrigerant can only flow to the first heat exchange pipeline 204 under the shutoff action of the first check valve 201, at the moment, a low-temperature refrigerant normally flows in the second heat exchange pipeline 205, so that the second heat exchange pipeline 205 keeps normal evaporation refrigeration, and the high-temperature refrigerant in the first heat exchange pipeline 204 liquefies and releases heat, the first heat exchange pipeline 204 is defrosted, and the heat exchanger 200 (outdoor heat exchanger) can perform refrigeration and defrosting at the same time by adopting fewer electromagnetic valves and matching with one-way valves, so that indoor heating stop can be avoided, the cost is reduced, and the stability of system operation is improved.

The first check valve 201 may be set in a conducting state when not defrosting, so that the refrigerant may pass through the first heat exchange pipeline 204 and the second heat exchange pipeline 205 in parallel when the refrigerant flows from the first refrigerant inlet and outlet 202 to the second refrigerant inlet and outlet 203.

Optionally, the outlet end of the first check valve 201 faces the first heat exchange pipe 204, and the first heat exchange pipe 204 is disposed on the upper side of the second heat exchange pipe 205. Therefore, when defrosting is required, a high-temperature refrigerant discharged from the compressor 100 can be directly led to the first heat exchange pipeline 204, wherein an outlet of the first check valve 201 faces the first heat exchange pipeline 204, and under the condition that the high-temperature refrigerant flows into the first heat exchange pipeline 204, the pressure is increased, so that the first check valve 201 is closed, at this time, the high-temperature refrigerant releases heat in the first heat exchange pipeline 204, defrosting is performed on the first heat exchange pipeline 204, and meanwhile, a normal low-temperature refrigerant flows into the second heat exchange pipeline 205, so that normal heating of the indoor unit is maintained, wherein the first heat exchange pipeline 204 is arranged on the upper side of the second heat exchange pipeline 205, so that defrosting water of the first heat exchange pipeline 204 can be dropped on the second heat exchange pipeline 205, and defrosting is performed on the second heat exchange pipeline 205, and defrosting efficiency is improved.

As shown in fig. 3, optionally, a water pan 206 is disposed on a lower side of the first heat exchange pipe 204, and a water leakage hole 207 is disposed on a lower side of the water pan 206. Like this, the defrosting water can flow into on the water collector 206 earlier to through leaking hole 207 downward flow on the water collector 206, make the defrosting water can keep the dwell of certain time near first heat transfer pipeline 205, carry out certain degree of heating to the defrosting water through first heat transfer pipeline 205, improve the temperature of defrosting water, and then will have the defrosting water of certain temperature and drip on second heat transfer pipeline 205, change the frost to second heat transfer pipeline 205, and then improve the defrosting effect of whole heat exchanger 200.

Alternatively, the first heat exchange line 204 comprises a plurality of first branch lines 208 and the second heat exchange line 205 comprises a plurality of second branch lines 209. Like this, every heat transfer pipeline all includes a plurality of bleeder, can improve heat exchanger 200's heat transfer area, improves the heat transfer effect to set up every a plurality of bleeder and arrange by the form that can be different, make heat exchanger 200's use more nimble.

Alternatively, the plurality of first branch pipes 208 are connected in parallel with each other. Therefore, the refrigerant can uniformly pass through the first heat exchange pipeline 204, the flowing uniformity of the refrigerant is improved, and the condition of non-uniform heat exchange is prevented.

Optionally, the plurality of second branch pipes 209 are connected in parallel with each other. Therefore, the refrigerant can uniformly pass through the second heat exchange pipeline 205, the flowing uniformity of the refrigerant is improved, and the condition of non-uniform heat exchange is prevented.

As shown in fig. 2, optionally, a plurality of first branch pipes 208 are arranged crosswise to a plurality of second branch pipes 209. Like this, when first branch pipe 208 way changes frost, can make partial heat transfer to second branch pipe 209 way, the heat exchange can be carried out better to the two crossing arrangement, thereby when first branch pipe 208 way is gone on defrosting, the heat that can utilize its production changes frost to second branch pipe 209 way, when not influencing second branch pipe 209 way normal work, improve holistic defrosting ability, and then make the air conditioner can change the frost operation under the indoor condition that does not stop to heat, improve the travelling comfort of air conditioner air-out.

Optionally, each of the branch pipes includes 3 to 5U-shaped heat exchange tubes thereon. Like this, set up the quantity that the U-shaped heat exchange tube set up at reasonable within range, can fully carry out the heat transfer, can prevent again that the pressure drop is too big, improve heat exchange efficiency.

Optionally, the U-shaped heat exchange tubes on each branch line are arranged in series. In this way, the plurality of branch pipes are connected in series so that the branch pipes have a sufficient path length and can sufficiently exchange heat.

Alternatively, the first branch pipes 208 and the second branch pipes 209 are arranged alternately in the longitudinal direction, and the uppermost one is the first branch pipe 208 and the lowermost one is the second branch pipe 209. Thus, when defrosting is performed in the first branch pipe 208, the defrosting water can flow into the second branch pipe 209, and the defrosting of the second branch pipe 209 is performed by the defrosting water in the first branch pipe 208, thereby further improving the defrosting efficiency.

Optionally, the spacing between the first branch pipe 208 and the second branch pipe 209 is less than or equal to 0.5 cm. Thus, a relatively small distance can be maintained between the first branch pipe 208 and the second branch pipe 209, and when defrosting is performed in the first branch pipe 208, a part of the heat is transferred to the second branch pipe 209, and thus appropriate defrosting can be performed in the second branch pipe 209, and the overall defrosting efficiency can be improved.

Optionally, when the heat exchanger 200 is used as an evaporator, the refrigerant flows from the first refrigerant inlet and outlet 202 to the second refrigerant inlet and outlet 203, wherein the first check valve 201 is disposed on one side of the first heat exchange pipeline 204, the second heat exchange pipeline 205 and the first refrigerant inlet and outlet 202; a second check valve 500 is disposed on a side of the first heat exchange pipeline 204 and the second heat exchange pipeline 205, which communicates with the second refrigerant inlet and outlet 203, and a conduction direction of the second check valve 500 is the same as a direction from the first refrigerant inlet and outlet 202 to the second refrigerant inlet and outlet 203. Thus, the second check valve 500 is arranged at one end of the first heat exchange pipeline 204 and the second heat exchange pipeline 205, which is communicated with the second refrigerant inlet and outlet 203, and the heat exchanger 200 has different flow path numbers when being used as an evaporator and a condenser through the control of the first check valve 201 and the second check valve 500, so as to better meet different heat exchange requirements when the heat exchanger 200 is used as an evaporator and a condenser, wherein when the heat exchanger 200 is used as an evaporator, the refrigerant flows in from the first refrigerant inlet and outlet 202, at the same time, the first check valve 201 and the second check valve 500 are both conducted, the refrigerant simultaneously passes through the first heat exchange pipeline 204 and the second heat exchange pipeline 205 and is converged to flow out from the second refrigerant inlet and outlet 203, when the heat exchanger 200 is used as a condenser, the refrigerant flows in from the second refrigerant inlet and outlet 203, at the same time, the first check valve 201 and the second check valve 500 are both closed, the refrigerant circulates through first heat exchange pipeline 204 under the effect of blocking of second check valve 500, and enter into second heat exchange pipeline 205 under the effect of blocking of first check valve 201, finally flow out by first refrigerant access & exit 202, can make heat exchanger 200 possess more flow paths under the condition of using as the evaporimeter, make the better circulation of the refrigerant after the evaporation, reduce the pressure drop, improve heat transfer effect, and under the condition of using as the condenser, make refrigerant circulation route longer, and then can make the better condensation of refrigerant, improve the subcooling effect, carry out the heat transfer better.

Optionally, the heat pump system further comprises: a first dispenser 400. The first liquid separator 400 is provided with a collecting pipe and two liquid separation ports, wherein the collecting pipe is communicated with the first refrigerant inlet and outlet 202, one of the two liquid separation ports is communicated with the first heat exchange pipeline 204, and the other is communicated with the second heat exchange pipeline 205. Like this, shunt the refrigerant through first knockout 400, make the reposition of redundant personnel process more smooth and easy, prevent to cause the reposition of redundant personnel uneven, lead to the refrigerant flow inhomogeneous, influence holistic heat dissipation to the knockout itself possesses certain volume and can play certain stock solution function, improves the stability of inside refrigerant circulation.

Optionally, the heat pump system further comprises: the collecting pipe of the second liquid separator is communicated with one liquid separating opening of the first liquid separator 400, the branch openings of the second liquid separator are respectively communicated with one first branch pipe 208, the third liquid separator is communicated with the other liquid separating opening of the first liquid separator 400, and the branch openings of the third liquid separator are respectively communicated with one second branch pipe 209. Thus, the refrigerant can be distributed into the plurality of first branch pipes 208 by the second liquid distributor, the uniformity of the refrigerant flow in the plurality of first branch pipes 208 can be maintained, and the refrigerant can be distributed into the plurality of second branch pipes 209 by the third liquid distributor, the uniformity of the refrigerant flow in the second branch pipes 209 can be maintained, and the stability of the entire refrigerant flow can be improved.

Optionally, the heat pump system further comprises: the second check valve 500 is disposed on one side of the first heat exchange pipeline 204 and the second heat exchange pipeline 205, which are communicated with the second refrigerant inlet and outlet 203, a liquid outlet end of the second check valve 500 faces the second refrigerant inlet and outlet 203, a part of the first branch pipes 208 is communicated with all the second branch pipes 209 and liquid inlet ends of the second check valve 500, and the other part of the first branch pipes 208 is communicated with the liquid outlet end of the second check valve 500. In this way, when the second check valve 500 is set such that the refrigerant flows from the second refrigerant inlet/outlet 203 to the first refrigerant inlet/outlet 202, the refrigerant flows through the first heat exchange pipeline 204 and the second heat exchange pipeline 205 in sequence, thereby sufficiently supercooling the refrigerant and improving the heat exchange effect.

It can be understood that the conducting direction of the second check valve 500 is from the liquid inlet end to the liquid outlet end, and the liquid outlet end is blocked from the liquid inlet end.

As shown in fig. 4, optionally, the heat pump system further includes: the second defrost circuit 600. One end of the second defrosting circuit 600 is communicated with the high-temperature refrigerant outlet of the compressor 100, and the other end is communicated with the second heat exchange pipeline 205, and a second electromagnetic valve is arranged on the second defrosting circuit 600. In this way, the first defrosting circuit 300 and the second defrosting circuit 600 are alternately opened, so that the first heat exchange pipeline 204 and the second heat exchange pipeline 205 can be alternately defrosted respectively, and when defrosting is completed, the other heat exchange pipeline can normally perform heat exchange work, so that defrosting is completed without stopping heating indoors, and the defrosting effect is faster than that of the first defrosting circuit 300.

It can be understood that the first solenoid valve 301 and the second solenoid valve are opened alternately, so that one of the first heat exchange pipeline 204 and the second heat exchange pipeline 205 can be in normal heat exchange, and the other can defrost, thereby achieving the effect of defrosting while continuously heating indoor. When the room does not need to be heated, the first electromagnetic valve 301 and the second electromagnetic valve can be opened simultaneously, so that the defrosting speed is increased.

Optionally, the second defrost circuit 600 makes an acute angle between the flow path direction of the second heat exchange pipeline 205 and the flow path direction of the second heat exchange pipeline 205 when the heat exchanger 200 is used as an evaporator through the Y connection pipe and the second heat exchange pipeline 205. In this way, the refrigerant of the second defrost circuit 600 leading to the second heat exchange line 205 can flow along the flow direction of the second heat exchange line 205, and the normal heat exchange of the first heat exchange line 204 is prevented from being affected by the backflow of the high-temperature refrigerant.

Alternatively, a solenoid valve may be provided at a portion of the connection of the second defrost circuit 600 and the second heat exchange line 205 facing the first dispenser 400. In this way, the high-temperature refrigerant introduced by the second defrosting circuit 600 can be more stably prevented from flowing backwards by controlling the solenoid valve, and the normal heat exchange efficiency of the first heat exchange pipeline 204 is maintained under the condition that the second heat exchange pipeline 205 is defrosted.

In some embodiments, one or more of the first, second, and third dispensers (collectively, dispensers) are provided with a dispensing chamber.

Optionally, the second dispenser comprises a dispenser chamber.

Optionally, as shown in fig. 5, the liquid separator is disposed obliquely, the liquid separation port is disposed obliquely upward, and the collecting pipe is disposed obliquely downward, which can also achieve the liquid storage function of the liquid separator, and at least one of the liquid inlet and the liquid outlet of the liquid separation port is implemented in the case that the heat exchanger 200 is used as a condenser.

In order to realize the liquid storage function of the liquid separator 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 f 2Q, f2 is a preset multiple, V is the volume of the liquid separation cavity, and the unit is cm3, Q is rated refrigerating capacity, and the unit is kW.

Optionally, f2 ranges from 8 to 12.

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

In this embodiment, the relationship between the rated capacity of the unit and the filling amount is approximately: m-160Q; the normal heating mode is 10-15% higher than the refrigerant filling amount requirement of the cooling mode, while the gas-liquid separator of the compressor 100 can generally store 5-10% of the refrigerant, the actual amount of the refrigerant required to be stored by the liquid separator is 5% of the total filling amount, and if the actual amount of the storage 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 the 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 rated refrigerating capacity of 3.5KW, the volume of the liquid separating cavity of the liquid separator is selected to satisfy V ≦ f2 ═ Q ═ 10 ═ 3.5 ═ 35, namely, the volume of the liquid separating cavity of the liquid separator is less than or equal to 35cm 3.

Here, the present application respectively tests the operation performance of the same air conditioner under the condition that f2 takes the value of 8/10/12/14, etc., and compares different volume dispensers (taking the value of f 2), and the test data are shown in the following table 16:

TABLE 1

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 liquid separator, avoid the problem of unable liquid storage due to the volume of the liquid separation chamber of the liquid separator being too small, and adapt to the liquid storage requirements of different air conditioner models, optionally, the liquid separator 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, the lower limit f1 of the volume of the liquid separator is in the range of 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 volume limit of the liquid distributor is mainly determined by the structural limitation, and for reliability, the cross-sectional radius R of the liquid distributor is generally about 4 times the radius R of the branch pipes, so as to ensure that the radius of the distributor is not too large (i.e. the radius of the distributor does not affect the space of the heat exchanger 200), and that the distance between the branch pipes is certain, and the distributor still has sufficient strength after welding. That is, in this example, the radius R of the dispenser is 4R, and in this example, R is 1.4 cm.

Here, the present application tests the operation performance of the same air conditioner when f1 is 1/2/3/4, and compares different volume dispensers (with f 1), and the test data is shown in the following table 17:

TABLE 2

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.

Optionally, when the second liquid separator is obliquely arranged, the inclination angle alpha to the vertical direction is less than or equal to beta, and the beta 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 °.

Here, the description will be continued by taking the outdoor heat exchanger 200 of the air conditioner as an example. Generally, for a given air conditioner and operating conditions, there is an optimum refrigerant charge that optimizes the performance of the air conditioner; 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 this embodiment, the outdoor heat exchanger 200 is used as a "condenser" during the cooling operation, so that the internal volume of the dispenser in the outdoor heat exchanger 200 can be utilized to realize the function of "storing liquid".

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 runs in a heating mode, the outdoor heat exchanger 200 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 starting-up state when the air conditioner is in a shutdown state; when the air conditioner operates in a cooling mode, the outdoor heat exchanger 200 is used as a condenser, and the storage amount of the refrigerant in the liquid distributor is larger than that in the shutdown state when the air conditioner is started. When the air conditioner is stopped, part of the refrigerant is stored in the indoor and outdoor heat exchangers 200, the cavity of the compressor 100, the gas-liquid separator, and the like.

The embodiment of the disclosure provides an air conditioner, including the heat pump system of any one of above-mentioned embodiments.

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 pump system, comprising:

a compressor (100);

the heat exchanger (200) comprises a first refrigerant inlet and outlet (202), a second refrigerant inlet and outlet (203), a first heat exchange pipeline (204) and a second heat exchange pipeline (205), wherein the first heat exchange pipeline (204) and the second heat exchange pipeline (205) are connected in parallel between the first refrigerant inlet and outlet (202) and the second refrigerant inlet and outlet (203);

the first check valve (201) is arranged between the first heat exchange pipeline (204) and the second heat exchange pipeline (205), and the conduction direction of the first check valve is that the first refrigerant inlet and outlet (202) is conducted towards the direction of the second refrigerant inlet and outlet (203);

and one end of the first defrosting circuit (300) is communicated with a high-temperature refrigerant outlet of the compressor (100), the other end of the first defrosting circuit is communicated with an outlet end of the first one-way valve (201), and a first electromagnetic valve (301) is arranged on the first defrosting circuit (300).

2. The heat pump system according to claim 1, wherein an outlet end of the first check valve (201) faces the first heat exchange line (204), and the first heat exchange line (204) is disposed on an upper side of the second heat exchange line (205).

3. Heat pump system according to claim 1, characterized in that said first heat exchange line (204) comprises a plurality of first branch pipes (208) and said second heat exchange line (205) comprises a plurality of second branch pipes (209).

4. A heat pump system according to claim 3, characterized in that a plurality of said first branch pipes (208) and a plurality of said second branch pipes (209) are arranged crosswise.

5. The heat pump system according to claim 4, wherein the first branch pipes (208) and the second branch pipes (209) are arranged in a staggered manner in the longitudinal direction, and the uppermost one is the first branch pipe (208) and the lowermost one is the second branch pipe (209).

6. The heat pump system according to claim 3, wherein, in a case where the heat exchanger (200) is used as an evaporator, a refrigerant flows from the first refrigerant inlet/outlet (202) to the second refrigerant inlet/outlet (203), wherein the first check valve (201) is disposed on a side where the first heat exchange line (204) and the second heat exchange line (205) communicate with the first refrigerant inlet/outlet (202); and a second check valve (500) is arranged on one side of the first heat exchange pipeline (204) and one side of the second heat exchange pipeline (205) communicated with the second refrigerant inlet and outlet (203), and the conduction direction of the second check valve (500) is also conducted from the first refrigerant inlet and outlet (202) to the second refrigerant inlet and outlet (203).

7. The heat pump system of any one of claims 1 to 6, further comprising:

and the first liquid separator (400) is provided with a collecting pipe and two liquid separating ports, wherein the collecting pipe is communicated with the first refrigerant inlet and outlet (202), one of the two liquid separating ports is communicated with the first heat exchange pipeline (204), and the other liquid separating port is communicated with the second heat exchange pipeline (205).

8. The heat pump system of any one of claims 1 to 6, further comprising:

and one end of the second defrosting circuit (600) is communicated with a high-temperature refrigerant outlet of the compressor (100), the other end of the second defrosting circuit is communicated with the second heat exchange pipeline (205), and a second electromagnetic valve is arranged on the second defrosting circuit (600).

9. The heat pump system of claim 8, wherein the second defrost circuit (600) is connected to the second heat exchange line (205) via a Y-connection such that the flow path direction is at an acute angle to the flow path direction of the second heat exchange line (205) when the heat exchanger (200) is used as an evaporator.

10. An air conditioner characterized by comprising the heat pump system according to any one of claims 1 to 9.