CN109237644B

CN109237644B - Heat pump unit and control method thereof

Info

Publication number: CN109237644B
Application number: CN201811200812.5A
Authority: CN
Inventors: 杨慧斌; 罗苏瑜; 刘晋鸿; 马腾飞; 郭怀远
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2018-10-16
Filing date: 2018-10-16
Publication date: 2023-09-05
Anticipated expiration: 2038-10-16
Also published as: CN109237644A

Abstract

The invention provides a heat pump unit and a control method thereof. The heat pump unit includes: a main connecting pipe in circulation communication; a first throttling part arranged on the main connecting pipe; the compressor is arranged on the main connecting pipe; an outdoor heat exchanger located between the first throttling part and the compressor and communicated with the main connection pipe at one side of the compressor; the indoor heat exchanger is positioned between the first throttling component and the compressor and is communicated with the main connecting pipe at the other side of the compressor, and the indoor heat exchanger is also arranged in an indoor space and can directly exchange heat with air in the indoor space; and a second throttling part positioned between the indoor heat exchanger and the first throttling part. When the indoor heat exchanger exchanges heat, the refrigerant directly passes through the indoor heat exchanger to exchange heat with indoor air, so that the heat pump unit can exchange heat only once, the energy consumption of the system is reduced, and the control accuracy of the indoor temperature is improved.

Description

Heat pump unit and control method thereof

Technical Field

The invention relates to the technical field of air conditioning equipment, in particular to a heat pump unit and a control method thereof.

Background

For the current magnetic suspension centrifugal heat pump unit, the evaporation sides are dry evaporators, flooded evaporators or falling film evaporators, the indoor sides are water system heat exchangers, and the heat pump unit belongs to secondary heat exchange and has high energy consumption. Meanwhile, due to secondary heat exchange, the indoor temperature control precision can only be maintained at +/-2 ℃, and the partial load regulation is poor, so that the comfort in use is affected.

Disclosure of Invention

Based on the above, it is necessary to provide a heat pump unit and a control method thereof, which can reduce the energy consumption and improve the control accuracy, aiming at the problems of high energy consumption and low indoor temperature control accuracy caused by the adoption of secondary heat exchange in the conventional heat pump unit.

The above purpose is achieved by the following technical scheme:

a heat pump assembly comprising:

a main connecting pipe in circulation communication;

a first throttling part arranged on the main connecting pipe;

the compressor is arranged on the main connecting pipe;

an outdoor heat exchanger located between the first throttling part and the compressor and communicated with the main connection pipe at one side of the compressor;

the indoor heat exchanger is positioned between the first throttling component and the compressor and is communicated with the main connecting pipe at the other side of the compressor, and the indoor heat exchanger is also arranged in an indoor space and can directly exchange heat with air in the indoor space; and

And the second throttling component is positioned between the indoor heat exchanger and the first throttling component.

In one embodiment, the outdoor heat exchanger comprises an evaporative condensing heat exchanger and/or an air-cooled heat exchanger.

In one embodiment, the evaporative condensing heat exchanger comprises a first heat exchange component, the first heat exchange component is arranged in the heat exchange box body, two ends of the first heat exchange component are respectively connected with the main connecting pipe, and a water film can be attached to the outer wall of the first heat exchange component.

In one embodiment, the evaporative condensing heat exchanger further includes a spray assembly for spraying the first heat exchange member.

In one embodiment, the spray assembly comprises:

the water tank is positioned below the first heat exchange component;

the conveying pipeline is communicated with the water tank and used for conveying water in the water tank;

and the spraying component is communicated with the conveying pipeline and is aligned with the spraying component and used for spraying water to the first heat exchange component.

In one embodiment, the spray assembly further comprises a water delivery pump disposed on the delivery line for delivering water from the tank to the spray member via the delivery line.

In one embodiment, the evaporative condensing heat exchanger further comprises a pool of water, the first heat exchange member being immersed in the pool of water.

In one embodiment, the evaporative condensing heat exchanger further comprises a heat exchange box, the first heat exchange component is located in the heat exchange box, the heat exchange box is provided with an air inlet and an air outlet, and the air inlet and the air outlet are both communicated with an outdoor environment.

In one embodiment, the evaporative condensing heat exchanger further comprises a first fan and a second fan, wherein the first fan is arranged at the air inlet, and the second fan is arranged at the air outlet.

In one embodiment, the evaporative condensing heat exchanger may be disposed in the indoor space.

In one embodiment, the first heat exchange member is bent at least twice, or the first heat exchange member is bent once.

In one embodiment, the air-cooled heat exchanger comprises a plurality of groups of second heat exchange components and a third fan corresponding to each group of second heat exchange components, and the plurality of groups of second heat exchange components are arranged in parallel.

In one embodiment, each group of the second heat exchange components comprises two groups of fin tube heat exchangers and fin side plates arranged on the fin tube heat exchangers, the two groups of the fin tube heat exchangers are arranged in a V shape, and two adjacent groups of the second heat exchange components are connected through the fin side plates.

In one embodiment, a preset distance exists between every two adjacent third fans.

In one embodiment, the first throttling element is arranged at the indoor heat exchanger.

In one embodiment, the compressor comprises a magnetic levitation compressor or an air levitation compressor.

In one embodiment, the heat pump unit further comprises a pressurizing assembly, wherein the pressurizing assembly is arranged on the main connecting pipe and is used for pressurizing the refrigerant in the main connecting pipe.

In one embodiment, the main connecting pipe comprises a liquid pipe and a gas pipe, the pressurizing assembly comprises a first pressurizing component and a second pressurizing component, the first pressurizing component is arranged on the liquid pipe and is used for pressurizing liquid-state refrigerant in the liquid pipe, and the second pressurizing component is arranged on the gas pipe and is used for pressurizing gaseous-state refrigerant in the gas pipe.

In one embodiment, the pressurizing assembly further comprises a first valve and a second valve, wherein two ends of the first valve are connected to the liquid pipe and are arranged in parallel with the first pressurizing component, and two ends of the second valve are connected to the air pipe and are arranged in parallel with the second pressurizing component.

In one embodiment, the heat pump unit further comprises a support frame for supporting the pressurizing assembly.

In one embodiment, the heat pump unit further comprises a liquid storage part and a switch valve positioned at two ends of the liquid storage part, one end of the liquid storage part is connected with the liquid pipe, the other end of the liquid storage part is connected with the inlet of the first pressurizing part, and the switch valve is used for realizing on-off between the liquid storage part and the first pressurizing part.

In one embodiment, the outdoor heat exchanger further includes a supercooling part for supercooling the refrigerant entering the first pressurizing part.

In one embodiment, the heat pump unit further includes a first distribution part, the number of the indoor heat exchangers is plural, and each indoor heat exchanger is located at the same level and is connected to the main connection pipe through the first distribution part.

In one embodiment, the heat pump unit further includes a plurality of first distribution components, the number of the indoor heat exchangers is plural, the levels of at least two indoor heat exchangers are different, and at least one indoor heat exchanger of each level is connected to the main connecting pipe through the corresponding first distribution component;

Each horizontal indoor heat exchanger corresponds to one pressurizing assembly or one pressurizing assembly and the liquid storage part.

In one embodiment, the first distribution component includes a distribution box, a plurality of distribution pipelines, a refrigeration valve and a heating valve, the distribution pipelines are connected with the indoor heat exchanger and the main connecting pipe, and the refrigeration valve and the heating valve are respectively arranged in the corresponding distribution pipelines.

In one embodiment, the air pipe and the liquid pipe are directly connected with the first distributing component of each level;

or, the main connecting pipe further comprises a plurality of gas branch pipes and a plurality of liquid branch pipes, the gas pipe is connected with each first distributing component through a plurality of the gas branch pipes, and the liquid pipe is connected with each first distributing component through a plurality of the liquid branch pipes.

The control method of the heat pump unit comprises the steps that when the heat pump unit is in refrigeration operation, the opening degree of a first throttling component changes along with indoor load, and a second throttling component is fully opened, and when the heat pump unit is in heating operation, the first throttling component is fully opened, and the opening degree of the second throttling component changes along with the indoor load;

The control method comprises the following steps:

acquiring response of the indoor load, starting a corresponding indoor heat exchanger, and starting a refrigeration valve or a heating valve corresponding to the first distribution part;

and adjusting the opening degree of the first throttling part or the second throttling part according to the indoor load.

In one embodiment, the step of adjusting the opening degree of the first throttle member or the second throttle member according to the respective indoor loads includes the steps of:

increasing the opening degree of the first throttle member or the second throttle member or increasing the rotor rotation speed of the compressor when the indoor load becomes large;

when the indoor load becomes small, the opening degree of the first throttle member or the second throttle member is reduced, or the rotor rotation speed of the compressor is reduced.

In one embodiment, the control method further includes the steps of:

acquiring the evaporating pressure or condensing pressure of the refrigerant in the indoor heat exchanger at a certain level;

if the evaporation pressure or the condensation pressure below the level is normal, the pressurizing assembly does not work;

the pressurizing assembly operates if the evaporation pressure or the condensation pressure at the level and above decreases.

In one embodiment, the step of operating the pressurizing assembly if the evaporating pressure or condensing pressure decreases includes the steps of:

when the evaporation pressure is lower than a first preset pressure, the first pressurizing part is controlled to be opened, and the first valve is closed;

if the evaporation pressure reaches a first preset pressure, controlling the first valve to be opened, and closing the first pressurizing part;

and if the evaporation pressure continues to drop, controlling the first pressurizing component to continuously pressurize until the evaporation pressure reaches the first preset pressure.

when the condensing pressure is lower than a second preset pressure, the second pressurizing part is controlled to be opened, and the second valve is closed;

if the condensing pressure reaches a second preset pressure, controlling the second valve to be opened, and closing the second pressurizing part;

and if the condensing pressure continues to drop, controlling the second pressurizing component to continuously pressurize until the evaporating pressure reaches a second preset pressure.

In one embodiment, the control method further includes the steps of:

Acquiring suction pressure at a suction port of the first pressurizing member;

if the suction pressure is equal to a third preset pressure, the first pressurizing part is closed, and the first valve is opened;

if the suction pressure is lower than the third preset pressure, controlling the liquid storage part to convey the refrigerant to the first pressurizing part, and/or increasing the supercooling degree of the refrigerant and/or controlling the rotating speed of the first pressurizing part at the downstream to be increased;

if the suction pressure is restored to the third preset pressure, controlling the first pressurizing component to restore to an initial state;

if the suction pressure continues to decrease, the rotational speed of the first pressurizing member downstream is controlled to increase, and/or the rotational speed of the rotor of the compressor is controlled to increase.

After the technical scheme is adopted, the invention has at least the following technical effects:

when the heat pump unit is in operation, refrigerant enters the indoor heat exchanger after being throttled by the second throttling component, after being subjected to heat exchange by the indoor heat exchanger and indoor air, the refrigerant in the indoor heat exchanger enters the outdoor heat exchanger after being compressed by the main connecting pipe through the compressor, and then the refrigerant enters the second throttling component after being subjected to heat exchange by the outdoor heat exchanger and outdoor air through the main connecting pipe after entering the first throttling component. When the indoor heat exchanger exchanges heat, the refrigerant directly passes through the indoor heat exchanger to exchange heat with indoor air, so that the problems of high energy consumption and low indoor temperature control precision caused by the adoption of secondary heat exchange of the conventional heat pump unit are effectively solved. Therefore, the heat pump unit can exchange heat only once, the energy consumption of the system is reduced, the energy efficiency of the heat pump unit is improved, meanwhile, the control precision of indoor temperature is improved, and the comfort level of a user in use is ensured.

Drawings

FIG. 1 is a schematic cycle diagram of a heat pump unit according to an embodiment of the present invention;

fig. 2 is an application scenario diagram of the heat pump unit shown in fig. 1 in the first embodiment;

fig. 3 is an application scenario diagram of the heat pump unit shown in fig. 1 in a second embodiment;

FIG. 4 is a side view of a third embodiment of an evaporative condensing heat exchanger of the heat pump assembly shown in FIG. 1;

FIG. 5 is a side view of a fourth embodiment of an evaporative condensing heat exchanger of the heat pump assembly shown in FIG. 1;

FIG. 6 is a front view of the evaporative condensing heat exchanger shown in FIG. 5;

FIG. 7 is a schematic view of a heat exchanger of the heat pump unit shown in FIG. 1;

FIG. 8 is a schematic illustration of the heat pump unit of FIG. 2 with the addition of a pressurization assembly;

FIG. 9 is a schematic illustration of the heat pump unit of FIG. 8 with the addition of a reservoir;

FIG. 10 is a flow chart illustrating operation of the heat pump unit shown in FIG. 1;

FIG. 11 is a flow chart illustrating operation of the heat pump unit shown in FIG. 8;

fig. 12 is a flowchart illustrating the operation of the heat pump unit shown in fig. 9.

Wherein:

100-heat pump units;

110-a main connection pipe;

111-liquid tube;

112-trachea;

113-liquid branch pipes;

114-gas branch pipes;

120-compressor;

130-an outdoor heat exchanger;

131-an evaporative condensing heat exchanger;

1311-a heat exchange box; 13111-an air intake; 13112-exhaust port;

1312-a first heat exchange member;

1313-a spray assembly; 13131-tank; 13132-a transfer line; 13133-spray component; 13134-water pump;

1314-a first fan;

1315-a second fan;

132-an air-cooled heat exchanger;

1321-a second heat exchange member;

1322-third fan;

140-an indoor heat exchanger;

150-a first throttle member;

160-a second throttle member;

170-a first dispensing member;

171-a distribution box;

172-a distribution line;

173-a refrigeration valve;

174-heating valve;

180-pressurizing assembly;

181-a first pressurizing member; 182-a second pressurizing member; 183-first valve; 184-a second valve;

190-reservoir part.

Detailed Description

In order to make the objects, technical solutions and advantages of the present application more apparent, the heat pump unit and the control method thereof according to the present application will be described in further detail by examples below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the application.

The numbering of the components itself, e.g. "first", "second", etc., is used herein merely to distinguish between the described objects and does not have any sequential or technical meaning. The term "coupled" as used herein includes both direct and indirect coupling (coupling), unless otherwise indicated. In the description of the present application, it should be understood that the terms "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are merely for convenience in describing the present application and simplifying the description, and do not indicate or imply that the device or element in question must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present application.

In the present invention, unless expressly stated or limited otherwise, a first feature "up" or "down" a second feature may be the first and second features in direct contact, or the first and second features in indirect contact via an intervening medium. Moreover, a first feature being "above," "over" and "on" a second feature may be a first feature being directly above or obliquely above the second feature, or simply indicating that the first feature is level higher than the second feature. The first feature being "under", "below" and "beneath" the second feature may be the first feature being directly under or obliquely below the second feature, or simply indicating that the first feature is less level than the second feature.

Referring to fig. 1, the present invention provides a heat pump unit 100. The heat pump unit 100 is used for adjusting the temperature of an indoor space to meet the cooling or heating requirements of users under different conditions. The heat pump unit 100 can directly exchange heat through the refrigerant, even if the heat pump unit 100 exchanges heat only once, the energy consumption of the system is reduced, the energy efficiency of the heat pump unit 100 is improved, the control precision of indoor temperature is improved, and the comfort level of a user in use is ensured.

In one embodiment, the heat pump assembly 100 includes a main connection pipe 110, a first throttling part 150, a compressor 120, an outdoor heat exchanger 130, an indoor heat exchanger 140, and a second throttling part 160. The main connection pipe 110 is in circulation communication. The first throttling part 150 is provided to the main connection pipe 110. The compressor 120 is disposed at the main connection pipe 110. The outdoor heat exchanger 130 is located between the first throttling part 150 and the compressor 120, and communicates with the main connection pipe 110 at one side of the compressor 120. The indoor heat exchanger 140 is positioned between the first throttling part 150 and the compressor 120 and is communicated with the main connection pipe 110 at the other side of the compressor 120, and the indoor heat exchanger 140 is also arranged in the indoor space and can directly exchange heat with the air in the indoor space. The second throttling part 160 is positioned between the indoor heat exchanger 140 and the first throttling part 150.

The main connection pipe 110 is a closed communication pipe such that the refrigerant may circulate to the indoor heat exchanger 140 and the outdoor heat exchanger 130 through the main connection pipe 110. When the heat pump unit 100 is in refrigeration operation, the first throttling component 150 is used for throttling and reducing the pressure of the refrigerant, and the second throttling component 160 is fully opened; during the heating operation of the heat pump unit 100, the first throttle member 150 is fully opened, and the second throttle member 160 cools and depressurizes the refrigerant. The indoor heat exchanger 140 is disposed in the indoor space to heat or cool the indoor space to adjust the temperature of the indoor space. The outdoor heat exchanger 130 is used for evaporating or condensing the refrigerant after heat exchange by the indoor heat exchanger 140. Further, the heat pump unit 100 further includes two stop valves (not shown), wherein one of the stop valves is disposed between the indoor heat exchanger 140 and the second throttling part 160, and the other stop valve is disposed between the compressor 120 and the indoor heat exchanger 140, and the stop valve is used for switching on and off the main connection pipe 110, thereby switching on and off the refrigerant flow path.

Alternatively, compressor 120 includes a magnetic levitation compressor or an air levitation compressor. This ensures reliable oil return to the compressor 120. In this embodiment, the compressor 120 is a magnetic levitation compressor.

When the heat pump unit 100 is operated in a cooling mode, the high-temperature and high-pressure liquid refrigerant in the indoor heat exchanger 140 is throttled by the first throttling part 150 to become a low-temperature and low-pressure liquid, absorbs heat of the indoor space to become a low-temperature and low-pressure gas, and flows into the outdoor heat exchanger 130 clockwise through the main connection pipe 110. Specifically, the low-temperature and low-pressure refrigerant gas in the main connection pipe 110 is compressed by the compressor 120 to become high-temperature and high-pressure gas, and then flows into the outdoor heat exchanger 130 to be condensed into high-temperature and high-pressure liquid. The second throttling part 160 is in a fully opened state, and the high-temperature and high-pressure liquid sent out by the outdoor heat exchanger 130 enters the indoor heat exchanger 140 through the main connecting pipe 110 after passing through the second throttling part 160, and becomes low-temperature and low-pressure liquid after being throttled by the first throttling part 150, thus reciprocally completing the refrigeration cycle.

When the heat pump unit 100 is in heating operation, the high-temperature and high-pressure refrigerant gas in the indoor heat exchanger 140 releases heat to become high-temperature and high-pressure liquid, the first throttling part 150 is fully opened, the second throttling part 160 throttles, the refrigerant liquid is throttled on the outdoor heat exchanger 130 side, and energy loss is prevented. The high temperature and high pressure refrigerant liquid flowing out of the indoor heat exchanger 140 flows counterclockwise in the main connection pipe 110, throttled and depressurized by the second throttling part 160, enters the outdoor heat exchanger 130 to evaporate and absorb heat, is compressed into high temperature and high pressure gas by the compressor 120, flows into the indoor heat exchanger 140 through the main connection pipe 110, and thus reciprocally completes the heating cycle.

The indoor heat exchanger 140 is directly located in the indoor space, and the refrigerant in the indoor heat exchanger 140 may directly exchange heat with the indoor air. The direct heat exchange refers to convection heat exchange, and is a heat transfer process caused by blending cold and hot fluids with each other due to macroscopic motion of the fluids. That is, the indoor heat exchanger 140 performs primary heat exchange, and the primary heat exchange is performed by the indoor heat exchanger 140, so that the cooling capacity or heat of the refrigerant may directly act on the indoor space. Compared with the traditional secondary heat exchange, the primary heat exchange reduces the energy consumption of the system, improves the energy efficiency of the heat pump unit 100, improves the control precision of indoor temperature, and ensures the comfort level of users during use. It will be appreciated that secondary heat exchange herein refers to: the heat exchange transfer of the conventional heat pump unit 100 is that refrigerant, water and air are directly introduced into an indoor water system heat exchanger such as a fan coil, a radiator, a copper-aluminum composite convection heat exchanger and the like through a hydraulic conveying system after chilled water is obtained on the evaporation side of the heat pump unit 100.

In the heat pump unit 100 of the present invention, the refrigerant of the outdoor heat exchanger 130 is directly sent to the indoor heat exchanger 140 through the main connection pipe 110, and the refrigerant in the indoor heat exchanger 140 is directly evaporated to provide cold or directly condensed to provide heat, so that primary heat exchange of the heat pump unit 100, i.e. direct heat exchange of the refrigerant and indoor air, is realized, the energy consumption of the heat pump unit 100 is reduced, and the energy efficiency of the heat pump unit 100 is improved. Meanwhile, when the heat pump unit 100 is used for refrigerating, the evaporating temperature can be reduced to below 0 ℃ to obtain lower indoor temperature, and meanwhile, the indoor temperature setting precision can be accurately controlled to be kept at +/-0.1 ℃, and meanwhile, the energy consumption of the unit can be saved, and the energy efficiency of the unit can be improved.

Alternatively, the first throttling element 150 may be an electronic expansion valve, and of course, in other embodiments of the present invention, the first throttling element 150 may be a capillary tube or other structure capable of realizing throttling and depressurization. The second throttling part 160 may be an electronic expansion valve, however, in other embodiments of the present invention, the second throttling part 160 may be a capillary tube or other structures capable of realizing throttling and depressurization. The opening degrees of the first and second throttle members 150 and 160 are adjusted according to the change of the indoor load, and the opening degree is large when the load increases and small when the load decreases. It will be appreciated that an increase in load is generally manifested as an increase in the heating set temperature value and a decrease in the cooling set temperature value. When the load decreases, the heating set temperature value generally decreases, and the cooling set temperature value increases. Also, the indoor heat exchanger 140 may be a fin heat exchanger, a tube heat exchanger, or the like.

Referring to fig. 1 to 3, in an embodiment, the number of indoor heat exchangers 140 is plural. That is, the same outdoor heat exchanger 130 drives the plurality of indoor heat exchangers 140 to operate simultaneously, so that the number of the outdoor units a can be reduced, one-to-many operation is realized, the occupied area of the outdoor units is reduced, and the energy consumption is reduced.

Optionally, at least two indoor heat exchangers 140 are located at different levels. The level is described by taking a floor as an example. That is, at least two indoor heat exchangers 140 are located at different floors, e.g., a portion of the indoor heat exchangers 140 are located in a first floor, a portion of the indoor heat exchangers 140 are located in a second floor, etc. Of course, in other embodiments of the present invention, each indoor heat exchanger 140 may be located at the same level. That is, the respective indoor heat exchangers 140 may be located at the same floor.

In one embodiment, the heat pump unit 100 further includes a first distribution part 170, and the indoor heat exchangers 140 of the same level are connected to the main connection pipe 110 through the first distribution part 170. That is, when the indoor heat exchangers 140 may be located at the same level, the indoor heat exchangers 140 are connected by one first distribution part 170, respectively. When the levels of the at least two indoor heat exchangers 140 are different, at least one indoor heat exchanger 140 of each level is connected to the main connection pipe 110 through the corresponding first distribution part 170. I.e. the indoor heat exchangers 140 of each floor are connected by a first distribution element 170.

It will be appreciated that the number of indoor heat exchangers 140 per floor is plural, the number of floors is plural, and the indoor heat exchangers 140 of each floor are connected to the main connection pipe 110 through the corresponding first distribution part 170. In this embodiment, only one, ten, twenty, thirty, and forty floors are described as examples. The indoor heat exchangers 140 of first, tenth, twentieth, thirty, forty floors are each connected to the main connection pipe 110 through a corresponding first distribution part 170. Other floors, such as eight floors, eighteen floors and even floors higher than forty floors, are all arranged in the same way and are not described in detail herein.

In one embodiment, the main connection tube 110 includes an air tube 112 and a liquid tube 111. The first distribution member 170 is connected to the air tube 112 and the liquid tube 111, respectively. Specifically, the pipe connected between the indoor heat exchanger 140 and the outdoor heat exchanger 130 and having the compressor 120 is the gas pipe 112, and the pipe connected between the indoor heat exchanger 140 and the outdoor heat exchanger 130 and having the second throttling part 160 is the liquid pipe 111. The gas pipe 112 is used for transporting a refrigerant gas, and the liquid pipe 111 is used for transporting a refrigerant liquid.

During the cooling operation of the heat pump unit 100, the liquid refrigerant sent from the outdoor heat exchanger 130 is sent to the indoor heat exchanger 140 through the liquid pipe 111, and the indoor heat exchanger 140 evaporates and absorbs heat to become a gaseous refrigerant, and the gaseous refrigerant flows back to the outdoor heat exchanger 130 from the air pipe 112. During heating operation of the heat pump unit 100, the gaseous refrigerant conveyed by the outdoor heat exchanger 130 is conveyed to the indoor heat exchanger 140 through the air pipe 112, the indoor heat exchanger 140 condenses and releases heat to become liquid refrigerant, and the gaseous refrigerant flows back to the outdoor heat exchanger 130 from the liquid pipe 111.

In an embodiment, the first distribution part 170 includes a distribution box 171, a plurality of distribution pipes 172, a refrigeration valve 173, and a heating valve 174, the distribution pipes 172 connect the indoor heat exchanger 140 and the main connection pipe 110, and the refrigeration valve 173 and the heating valve 174 are respectively disposed in the corresponding distribution pipes 172. One end of each of the plurality of distribution pipes 172 is connected to the indoor heat exchanger 140 on the same floor, and the other end of each of the plurality of distribution pipes 172 is connected to the gas pipe 112 or the liquid pipe 111. It will be appreciated that a portion of the distribution line 172 is connected to the air tube 112 and a portion of the distribution line 172 is connected to the liquid tube 111, as shown in fig. 1.

In fig. 1, it is assumed that each of the first distribution parts 170 connects two indoor heat exchangers 140. The number of distribution lines 172 is four, the number of refrigeration valves 173 is two, and the number of heating valves 174 is two. Two of the distribution lines 172 are connected at one end to the air pipe 112 and at the other end to the indoor heat exchanger 140. The other two distribution pipes 172 have one end connected to the liquid pipe 111 and the other end connected to the indoor heat exchanger 140. The two refrigeration valves 173 are provided in the two distribution lines 172 connected to the liquid pipe 111, and the two heating valves 174 are provided in the two distribution lines 172 connected to the gas pipe 112.

During the refrigerating operation of the heat pump unit 100, the liquid refrigerant in the liquid pipe 111 enters the indoor heat exchanger 140 through the distribution pipeline 172 where the refrigerating valve 173 is located, and after the refrigerant in the indoor heat exchanger 140 evaporates and absorbs heat, the liquid refrigerant enters the air pipe 112 through the distribution pipeline 172 where the heating valve 174 is located. During heating operation of the heat pump unit 100, gaseous refrigerant in the air pipe 112 enters the indoor heat exchanger 140 through the distribution pipeline 172 where the heating valve 174 is located, and after the refrigerant in the indoor heat exchanger 140 is condensed and released, the gaseous refrigerant enters the liquid pipe 111 through the distribution pipeline 172 where the cooling valve 173 is located.

It can be understood that the refrigerant of the heat pump unit 100 in the present invention has two distribution modes, one is that the refrigerant is already distributed directly at the outdoor heat exchanger 130, that is, the outdoor heat exchanger 130 is directly connected to a plurality of connection pipes, and the connection pipes are respectively connected to the first distribution parts 170 of different floors; the second type is that the outdoor heat exchanger 130 is a total refrigerant inlet/outlet pipe, and the distribution of the refrigerant is performed by the first distribution member 170 provided for each layer. The specific upward direction is as follows:

as shown in fig. 2, in the first embodiment, the air pipe 112 and the liquid pipe 111 are directly connected to the first distribution part 170 of each level. That is, the air pipe 112 and the liquid pipe 111 have a plurality of bifurcations, and there is a height difference between the bifurcations. The refrigerant in the liquid pipe 111 and the gas pipe 112 can be directly transferred to the first distribution part 170.

Of course, as shown in fig. 3, in the second embodiment, the main connection pipe 110 further includes a plurality of gas branch pipes 114 and a plurality of liquid branch pipes 113. The gas pipe 112 is connected to each of the first distribution members 170 through a plurality of gas branch pipes 114, and the liquid pipe 111 is connected to each of the first distribution members 170 through a plurality of liquid branch pipes 113. That is, the gas pipe 112 and the liquid pipe 111 are a main pipe, and a plurality of branch pipes are directly led out from the ends of the gas pipe 112 and the liquid pipe 111 to convey the refrigerant liquid and the refrigerant gas to the respective floors.

The outdoor heat exchanger 130, the compressor 120, and the second throttle 160 defining the heat pump unit 100 form an outdoor unit a of the heat pump unit 100. In contrast to the first embodiment, in which the air pipe 112 and the liquid pipe 111 extend out of the outer machine a, the air pipe 112 and the liquid pipe 111 are respectively allocated at each floor. That is, the outdoor heat exchanger 130 is composed of the gas pipe 112 and the liquid pipe 111, and the refrigerant is distributed by the first distribution member 170 of each layer. In the second embodiment, the air pipe 112 and the liquid pipe 111 are directly located in the external machine a, and the plurality of air branch pipes 114 and the plurality of liquid branch pipes 113 are led out through the external machine a. That is, the refrigerant may be directly distributed at the outdoor heat exchanger 130, that is, the outdoor heat exchanger 130 is directly connected to the plurality of gas branch pipes 114 and the plurality of liquid branch pipes 113, and is connected to the first distribution part 170 of the corresponding floor through the plurality of gas branch pipes 114 and the plurality of liquid branch pipes 113.

As shown in fig. 2, fig. 2 is an application scenario diagram of the heat pump unit 100 for distributing refrigerant. Wherein the outdoor heat exchanger 130 is not distributed at the source. The indoor heat exchanger 140 and the first distribution part 170 are disposed at the ceiling and connected to the external machine a through the air pipe 112 and the liquid pipe 111. The high-pressure liquid refrigerant in the refrigeration working condition or the high-pressure gaseous refrigerant in the heating working condition is distributed in each layer through branches led out from the air pipe 112 and the liquid pipe 111 respectively, and is distributed to the indoor heat exchangers 140 of each room through the first distribution part 170 of each layer.

As shown in fig. 3, this figure is also an application scenario diagram of the heat pump unit 100 distributing refrigerant, which differs from fig. 2 in that the outdoor heat exchanger 130 is distributed at the source. The number of the air branch pipes 114 and the liquid branch pipes 113 is basically one-to-one corresponding to the number of building layers, and ten layers are provided, so that ten corresponding liquid branch pipes 113 and ten air branch pipes 114 are respectively provided. The first gas-liquid branch pipe is connected with the first distribution part 170 of the first layer, and the fifth gas-liquid branch pipe is connected with the fifth layer first distribution part 170, so that the direct distribution of the refrigerant of the outdoor heat exchanger 130 is realized.

Alternatively, the main connection pipe 110 is connected using a stainless steel pipe. This can ensure cost reduction, and reduce heat and cold leakage between the heat pump unit 100 and the outside, so as to reduce energy loss in the main connection pipe 110. And, the distribution pipe 172 of the first distribution part 170 to the indoor heat exchanger 140 is connected using copper pipes.

Optionally, the heat pump unit 100 further includes two second distributing parts (not shown), where the two second distributing parts are respectively disposed on the air pipe 112 and the liquid pipe 111, the plurality of first distributing parts 170 are connected to the second distributing parts of the air pipe 112 through corresponding second air branch pipes 114, and the plurality of first distributing parts 170 are connected to the second distributing parts of the liquid pipe 111 through corresponding second liquid branch pipes 113. Of course, the second distribution part may be provided at both ends of the outdoor heat exchanger 130.

In one embodiment, the first throttling part 150 is disposed at the indoor heat exchanger 140. That is, in the cooling stage, the refrigerant is throttled down by the first throttling part 150 in the indoor heat exchanger 140. Therefore, the throttling loss of the cold energy in the external machine A can be avoided, and the cold energy utilization rate is improved. Preferably, the first throttling part 150 is located between the refrigeration valve 173 and the indoor heat exchanger 140.

Referring to fig. 1, 4-7, in one embodiment, the outdoor heat exchanger 130 includes an evaporative condensing heat exchanger 131 and/or an air-cooled heat exchanger 132. It will be appreciated that the evaporative condensing heat exchanger 131 and the air-cooled heat exchanger 132 may be used in combination. But in view of space occupation, cost and system complexity, the evaporative condensing heat exchanger 131 is generally used alone, or the air-cooled heat exchanger 132 is used alone. The air-cooled heat exchanger 132 exchanges heat by forced convection, and the evaporative condensing heat exchanger 131 exchanges heat by attaching a water film thereto.

The evaporative condensing heat exchanger 131 may be selected for areas where air drying and water resources are relatively abundant. Typically, a large public building is located in a central urban area, and the heat pump unit 100 consumes too much energy, which results in limited locations for installing cooling towers required for water-cooled heat exchangers. Therefore, the heat pump unit 100 according to an embodiment of the present invention employs the evaporative condensing heat exchanger 131. The evaporative condensing heat exchanger 131 is compact in structure, high in energy efficiency ratio and free of a cooling tower. The operation principle is as follows: the high-temperature and high-pressure refrigerant gas flows into the evaporation and condensation type heat exchanger 131, and the sensible heat transfer process of the refrigerant and the water film is realized under the driving of the temperature difference between the refrigerant gas and the attached water film. And then, under the driving of the temperature difference between the air and the water film and the driving of the difference between the saturated steam pressure on the surface of the water film and the partial pressure of the water steam in the outdoor air, the total heat transfer of the sensible heat and the latent heat in the heat transfer and mass transfer process of the water and the outdoor air is realized.

The evaporative condensing heat transfer is based on the difference between the wet bulb temperature and the water temperature of the outdoor air, and the greater the difference, the better the evaporative cooling effect, and the temperature difference of the evaporative condensing heat exchanger 131 is controlled to be 5 ℃ or higher. In addition, the areas rich in dry and water resources can provide enough cooling water required by the evaporative condensing heat exchanger 131 due to sufficient water sources, and evaporation of liquid water is facilitated due to dry weather. On the contrary, in cold and humid areas, the evaporation of liquid water is not facilitated due to the high water vapor content in the air, and the problem of water icing in cold areas can also occur.

For cold areas or air-wet areas, an air-cooled heat exchanger 132 may be selected. The air-cooled heat exchanger 132 is directly installed in an area where outdoor ventilation is good. When the heat pump unit 100 operates in a refrigerating mode, outdoor air enters the air-cooled heat exchanger 132 to take away heat of the refrigerant in the air-cooled heat exchanger 132, and is discharged out of the outdoor side to reduce condensation temperature, so that normal operation of the heat pump unit 100 is maintained. During heating operation of the heat pump unit 100, outdoor air enters the periphery of the air-cooled heat exchanger 132 to evaporate and absorb heat of the refrigerant in the air-cooled heat exchanger 132, so as to maintain a higher evaporation temperature meeting the building load.

Referring to fig. 1 and fig. 4 to fig. 6, in an embodiment, the evaporative condensing heat exchanger 131 includes a first heat exchange member 1312, the first heat exchange member 1312 is disposed in a heat exchange housing 1311, two ends of the first heat exchange member 1312 are respectively connected to the main connection pipe 110, and a water film can be attached to an outer wall of the first heat exchange member 1312. That is, heat exchange with the outside air is achieved by the first heat exchange member 1312 having a water film. During the heating operation of the heat pump unit 100, the water film absorbs heat of the refrigerant, exchanges heat with the outdoor air, heats the air, and discharges the air to the outside, and cools the water film. During the cooling operation of the heat pump unit 100, the refrigerant absorbs heat of a water film or heat of outdoor air. Alternatively, the first heat exchange member 1312 may be a heat exchange tube or a fin heat exchanger, or the like.

In an embodiment, the evaporative condensing heat exchanger 131 further includes a spray assembly 1313 for performing a spray operation on the first heat exchange member 1312. That is, the surface of the first heat exchange member 1312 is formed with a water film by spraying. In this way, after spraying, the sprayed water can form very good droplets on the surface of the first heat exchange component 1312, so as to improve the heat and mass transfer efficiency with air. Of course, in other embodiments of the present invention, the first heat exchange member 1312 may also be soaked to form a water film on the surface of the first heat exchange member 1312. Specifically, the evaporative condensing heat exchanger 131 further includes a water pool having water therein, in which the first heat exchange member 1312 is immersed.

In one embodiment, the spray assembly 1313 includes a water tank 13131, a delivery line 13132, and a spray member 13133. A water tank 13131 is located below the first heat exchange member 1312. The delivery line 13132 communicates with the water tank 13131 for delivering water in the water tank 13131. The spray member 13133 communicates with the delivery tube 13132 and is positioned in alignment with the spray member 13133 for spraying water to the first heat exchange member 1312. The water tank 13131 is a source of water for the spray assembly 1313 for storing water for use in spraying. The delivery line 13132 communicates the water tank 13131 with the spray member 13133. The delivery pipe 13132 delivers the water in the water tank 13131 to the spray member 13133, and sprays water to the first heat exchange member 1312 through the spray member 13133 so that the water adheres to the surface of the first heat exchange member 1312 to form a water film. Alternatively, the spray member 13133 is at least a spray head or a tube with small holes, or the like.

In an embodiment, the spray assembly 1313 further comprises a water pump 13134 disposed on the delivery line 13132 for delivering water from the water tank 13131 to the spray member 13133 via the delivery line 13132. The water pump 13134 is the power source for the spray assembly 1313 so that water can be delivered to the high-rise spray member 13133. When the refrigerant flows through the indoor heat exchanger 140, a water film formed on the surface of the first heat exchange member 1312 by water droplets discharged from the water tank 13131 to the shower member 13133 by the water pump is attached to the outside of the first heat exchange member 1312, and heat exchange is performed by the water film, which will be described later.

In an embodiment, the evaporative condensing heat exchanger 131 further includes a heat exchange housing 1311, the first heat exchange component 1312 is located in the heat exchange housing 1311, the heat exchange housing 1311 has an air inlet 13111 and an air outlet 13112, and the air inlet 13111 and the air outlet 13112 are both in communication with the outdoor environment. The heat exchange box 1311 plays a protective role, can prevent personnel from accidentally touching parts in the evaporative condensing heat exchanger 131, ensures safety, and can prevent sundries from entering the evaporative condensing heat exchanger 131. The air inlet 13111 is used for conveying air into the heat exchange box 1311, and the air outlet 13112 is used for discharging air in the heat exchange box 1311. Air in the external environment enters the heat exchange box 1311 through the air inlet 13111, exchanges heat with a water film on the outer surface of the first heat exchange component 1312, and then is discharged through the air outlet 13112.

Preferably, the evaporative condensing heat exchanger 131 may be disposed in the indoor space. At this time, the outdoor air can freely flow at the indoor side through the inlet 13111 and the outlet 13112, thereby satisfying the air volume required for the evaporative condensing heat exchanger 131.

In an embodiment, the evaporative condensing heat exchanger 131 further includes a first fan 1314 and a second fan 1315, the first fan 1314 is disposed at the air inlet 13111, and the second fan 1315 is disposed at the air outlet 13112. That is, the first blower 1314 is an air intake blower and the second blower 1315 is an air exhaust blower. The first fan 1314 and the second fan 1315 can accelerate airflow in the heat exchange box 1311, so as to ensure the heat exchange effect of the first heat exchange component 1312.

During the heating operation of the heat pump unit 100, the water film absorbs the heat of the refrigerant, and then exchanges heat with the air communicated with the outdoor side, the air is heated and discharged to the outdoor side, the water falls into the water tank 13131 after being cooled, and the water is continuously pressurized and conveyed to the spray member 13133 by the water pump to complete the cycle. When the heat pump unit 100 is operated and waste heat is available to heat water in the water tank 13131, the first fan 1314 and the second fan 1315 which are communicated with the outside are closed, so that heat exchange between the refrigerant and the hot water is realized; when there is no waste heat, the circulating water pump 13134 is turned off to drain the water in the water tank 13131, and the first fan 1314 and the second fan 1315, which are communicated with the outside, are turned on to obtain heat from the air by the refrigerant.

In a third embodiment, the first heat exchange member 1312 is bent at least twice. That is, after the first heat exchanging element 1312 is adopted, the evaporative condensing heat exchanger 131 is a multi-pass heat exchanger. I.e. the first heat exchange member 1312 is arranged in a serpentine shape with the refrigerant line going back and forth a number of times. In this way, the contact time or heat and mass transfer area between the refrigerant and water or air in the first heat exchange component 1312 can be increased, so as to achieve the purpose of full heat exchange. Of course, in the fourth embodiment, the first heat exchanging element 1312 may also be bent once. That is, after the first heat exchange member 1312 is adopted, the evaporative condensing heat exchanger 131 is a once-through heat exchanger. At this time, the evaporative condensing heat exchanger 131 has two separate refrigerant inlets and outlets, and is evaporated or condensed by the flow heat exchange in the first heat exchange member 1312. This also allows the refrigerant in the first heat exchange member 1312 to exchange heat with water or air.

And, can set up the shunt directly in the both ends of once-through or multipass evaporation condensation formula heat exchanger 131, connect a plurality of numbers of gas branch pipes 114 and liquid branch pipe 113 through the shunt, guaranteed the concentrated distribution of refrigerant in the source side, realized the independent one-to-one of every branch pipe and every layer of building, namely first branch pipe links to each other with first layer, and the fifth branch pipe links to each other with fifth layer, and so on. Of course, in other embodiments of the present invention, two separate inlets and outlets may be provided at two ends of the evaporative condensing heat exchanger 131, and the refrigerant is directly distributed in multiple stages in the main connection pipe 110 after being heated or cooled, that is, after being led out of the external machine a, the refrigerant is separately delivered in each layer through the air pipe 112 and the liquid pipe 111, instead of being distributed at the source.

In this embodiment, a splitter is provided at both ends of the multipass evaporative condensing heat exchanger 131, as shown in fig. 4, to distribute refrigerant at the source. Two separate inlets and outlets are provided at both ends of the once-through evaporative condensing heat exchanger 131, as shown in fig. 6, so that the refrigerant is not distributed at the source.

Referring to fig. 1 and 7, in an embodiment, the air-cooled heat exchanger 132 includes a plurality of sets of second heat exchange components 1321 and a third fan 1322 corresponding to each set of second heat exchange components 1321, the plurality of sets of second heat exchange components 1321 being arranged in parallel. The air-cooled heat exchanger 132 is installed in an area where outdoor ventilation is good to ensure a heat exchange effect. When the heat pump unit 100 is in operation, the third fan 1322 with high rotation speed and large air volume can introduce air into the second heat exchange component 1321 to exchange heat, and can discharge the air after heat exchange out of the room. It can be appreciated that the second heat exchange component 1321 can increase the contact area of the air-cooled heat exchanger 132 with the outside air. Of course, in other embodiments of the present invention, the second heat exchanging element 1321 is at least a fin heat exchanger, a tube heat exchanger, a heat exchanging tube, or the like. The plurality of groups of second heat exchanging members 1321 are connected in parallel with the liquid pipe 111 and the air pipe 112, respectively, to realize the conveyance of the refrigerant.

In one embodiment, each set of second heat exchange components 1321 includes two sets of fin tube heat exchangers and fin edge plates disposed on the fin tube heat exchangers, the two sets of fin tube heat exchangers are disposed in a V-shape, and two adjacent sets of second heat exchange components 1321 are connected by the fin edge plates. The two groups of fin tube heat exchangers are arranged in a V shape, so that the occupied area is reduced while the heat exchange area is ensured, and the service performance is ensured. The fin edge plates have a protective effect to protect the fin tube heat exchanger. The fin tube heat exchangers are tightly adhered by the fin edge plates.

In one embodiment, a predetermined distance exists between adjacent third fans 1322. That is, the adjacent third fans 1322 are not connected, so that the heat exchange relative independence of each group of fin tube heat exchangers can be ensured, and air short circuit is avoided, namely, air discharged by one third fan 1322 is prevented from entering the other third fan 1322. Preferably, the preset interval is in the range of 1/5-1/2 of the width of the V-shaped opening.

It will be appreciated that when there is a difference in height between the indoor heat exchanger 140 and the outdoor heat exchanger 130, the refrigerant supplied from the outdoor heat exchanger 130 to the indoor heat exchanger 140 may cause a problem of pressure loss of the refrigerant, and thus a change in evaporation temperature or condensation temperature may be caused, thereby reducing the capacity and energy efficiency of the heat pump unit 100. Accordingly, the heat pump unit 100 according to an embodiment of the present invention further includes a pressurizing assembly 180, the pressurizing assembly 180 is disposed on the main connection pipe 110, and the pressurizing assembly 180 is used for pressurizing the refrigerant in the main connection pipe 110. When the pressure of the refrigerant is lost, i.e., the evaporation pressure or the condensation pressure is lowered, the pressurizing assembly 180 is opened to pressurize the refrigerant in the main connection pipe 110. If no pressure loss occurs in the refrigerant, i.e., there is no drop in the evaporating or condensing pressure, then there is no need to open the pressurizing assembly 180. The pressurizing unit 180 of the floor where the pressure loss occurs is turned on, and the pressurizing unit 180 of the floor where the pressure loss does not occur is not turned on, which will be described later.

Referring to fig. 1 and 8, in an embodiment, the pressurizing assembly 180 includes a first pressurizing member 181 provided to the liquid pipe 111 for pressurizing the liquid refrigerant in the liquid pipe 111, and a second pressurizing member 182 provided to the gas pipe 112 for pressurizing the gaseous refrigerant in the gas pipe 112. The first pressurizing member 181 is a liquid pump, and the second pressurizing member 182 is an air pump, for example.

It can be appreciated that when the heat pump unit 100 is operated in refrigeration mode, the high-temperature and high-pressure refrigerant liquid is delivered to the indoor heat exchanger 140 through the liquid pipe 111, and the high density and the high viscosity of the liquid are combined with the gravity effect, so that the pressure loss is increased, and the liquid is flash-evaporated in advance. I.e., the dryness at the inlet is already much greater than about 0.2 as usual, and may be already close to more than 0.4, when entering the indoor heat exchanger 140, the refrigerating capacity per unit mass flow is greatly reduced. Accordingly, the heat pump assembly 100 of an embodiment of the present invention provides a pressurized design for the refrigerant in the liquid pipe 111 by the liquid pump. After the liquid pump is used for pressurizing the refrigerant, the refrigerant liquid before entering the indoor heat exchanger 140 is ensured to be compressed by a secondary small pressure ratio so as to ensure the constant evaporation temperature and refrigeration capacity, and the exhaust compression ratio and the power consumption can be reduced.

When the heat pump unit 100 is operated to heat, the high-temperature and high-pressure refrigerant gas is delivered to the indoor heat exchanger 140 through the gas pipe 112, the pressure loss is increased due to the high flow rate and the influence of gravity, so that the refrigerant gas is condensed in advance before entering the indoor heat exchanger 140. This increases the proportion of liquid phase at the inlet of the indoor heat exchanger 140 by 10% or more and 40% or more, thereby reducing the heating capacity. The heat pump assembly 100 of an embodiment of the present invention provides a pressurized design for the refrigerant in the air line 112 via an air pump. The pressure compensation pressure loss of the air side of the refrigerant is improved by pressurizing the air pump, and the heat exchange amount and the condensation temperature are ensured to be stable.

In one embodiment, the pressurizing assembly 180 further includes a first valve 183 and a second valve 184, wherein two ends of the first valve 183 are connected to the liquid pipe 111 and are disposed in parallel with the first pressurizing member 181, and two ends of the second valve 184 are connected to the air pipe 112 and are disposed in parallel with the second pressurizing member 182. The first valve 183 is used for switching on and off the liquid pipe 111, and the second valve 184 is used for switching on and off the air pipe 112. By way of example, the first valve 183 and the second valve 184 are solenoid valves or other valves that can be opened and closed.

After the first valve 183 and the second valve 184 are arranged, when the refrigeration working condition or the heating working condition is normal and no pressure is lost, the first pressurizing component 181 and the second pressurizing component 182 are in a closed state, and the first valve 183 and the second valve 184 which are connected in parallel with the first pressurizing component are in an open state, so that the refrigerant is ensured to continuously flow through the first valve 183 and the second valve 184. When the pressure loss occurs in the refrigeration working condition or the heating working condition, the first valve 183 or the second valve 184 corresponding to the first pressurizing component 181 or the second pressurizing component 182 is closed, and the first pressurizing component 181 or the second pressurizing component 182 is opened, so that the refrigerant is pressurized to raise the condensation temperature or the evaporation temperature. After the pressure is restored, the first pressurizing member 181 and the second pressurizing member 182 are closed, and the valves corresponding to the first pressurizing member 181 and the second pressurizing member 182 are opened, thereby realizing the normal circulation.

In an embodiment, the heat pump unit 100 further includes a control system, where the control system is connected to each component of the heat pump unit 100 to control the heating operation and the cooling operation of the heat pump unit 100. By way of example, the control system may be a controller, a control chip, or the like. The control system may perform control adjustment of the heat pump unit 100 according to the user's usage requirement, actual pipeline pressure loss condition, and operation conditions of the first pressurizing member 181 and the second pressurizing member 182. For example, the control system may also acquire the evaporation pressure or the condensation pressure of the refrigerant in the indoor heat exchanger 140 at a certain level in real time. Based on the level, the pressurizing unit 180 does not operate if the evaporation pressure or the condensation pressure below the level is normal. If the evaporation pressure or the condensation pressure at the level and above is lowered, the pressurizing unit 180 operates.

Specifically, after the control system obtains the evaporation pressure of the refrigerant at a certain level, if the evaporation pressure is not reduced below the level, the control system maintains the closed state of the first pressurizing member 181, and maintains the open state of the first valve 183. At this time, the refrigerant is directly transferred to the indoor heat exchanger 140 through the liquid pipe 111 via the first valve 183. If the evaporation pressure at the level and above is reduced and is lower than the first preset pressure, the first valve 183 is controlled to be closed, and the first pressurizing member 181 is controlled to be opened. The refrigerant in the liquid pipe 111 is pressurized by the first pressurizing member 181, and is sent to the indoor heat exchanger 140 after being pressurized. This reduces the pressure loss of the refrigerant and reduces the energy consumption of the heat pump unit 100.

When the evaporation pressure reaches the first preset pressure, the first valve 183 is controlled to open, and the first pressurizing member 181 is closed. That is, after the evaporation pressure is restored, the first pressurizing member 181 and the first valve 183 are restored, that is, the closed state of the first pressurizing member 181 is maintained, and the opened state of the first valve 183 is maintained.

If the evaporation pressure continues to decrease, the first pressurizing unit 181 is controlled to continuously pressurize until the evaporation pressure reaches the first preset pressure. That is, if the problem of the pressure drop of the evaporation pressure is not solved, the first pressurizing member 181 needs to continuously pressurize, that is, increase the rotation speed of the first pressurizing member 181 until the evaporation pressure is within a set reasonable range, and then the first valve 183 is opened to close the first pressurizing member 181.

Assuming that ten layers are taken as an example, when the evaporation pressure of ten layers is reduced, and the evaporation pressure of nine layers and below is normal, the evaporation pressure of ten layers and above is reduced. At this time, the operation states of the nine-stage or less first pressurizing members 181 and the first valves 183 are unchanged, the ten-stage or more first pressurizing members 181 are opened, and the first valves 183 are closed. The refrigerant in the liquid pipe 111 is pressurized by the first pressurizing member 181. When the evaporation pressure reaches the first preset pressure, the first valve 183 is controlled to open, and the first pressurizing member 181 is closed. If the evaporation pressure continues to decrease, the first pressurizing unit 181 is controlled to continuously pressurize until the evaporation pressure reaches the first preset pressure.

The control system obtains a condensing pressure of the refrigerant at a certain level. The closed state of the second pressurizing member 182 is maintained and the open state of the second valve 184 is maintained if the condensing pressure at the level or lower is not lowered based on the condensing pressure at the level. At this time, the refrigerant is directly transferred to the indoor heat exchanger 140 through the gas pipe 112 via the second valve 184. If the condensing pressure at the level and above is lowered and is lower than the second preset pressure, the second valve 184 is controlled to be closed and the second pressurizing member 182 is opened. The refrigerant in the gas pipe 112 is pressurized by the second pressurizing member 182, and is supplied to the indoor heat exchanger 140 after being pressurized. This reduces the pressure loss of the refrigerant and reduces the energy consumption of the heat pump unit 100.

When the condensing pressure reaches the second preset pressure, the second valve 184 is controlled to be opened, and the second pressurizing member 182 is closed. That is, after the condensing pressure is restored, the second pressurizing member 182 and the second valve 184 are restored, that is, the closed state of the second pressurizing member 182 is maintained, and the opened state of the second valve 184 is maintained.

If the condensing pressure continues to decrease, the second pressurizing member 182 is controlled to continuously pressurize until the condensing pressure reaches the second preset pressure. That is, if the problem of the pressure drop of the condensing pressure is not solved, the second pressurizing member 182 needs to continuously pressurize, that is, increase the rotation speed of the second pressurizing member 182 until the condensing pressure is within a set reasonable range, and then the second valve 184 is opened to close the second pressurizing member 182.

Assuming that ten layers are taken as an example, when the condensing pressure of ten layers is lowered, and the vapor condensing pressure of nine layers and below is normal, the condensing pressure of ten layers and above is lowered. At this time, the operation states of the nine-layer and below second pressurizing members 182 and the second valve 184 are unchanged, the ten-layer and above second pressurizing members 182 are opened, and the second valve 184 is closed. The refrigerant in the gas pipe 112 is pressurized by the second pressurizing member 182. When the condensing pressure reaches the second preset pressure, the second valve 184 is controlled to be opened, and the second pressurizing member 182 is closed. If the condensing pressure continues to decrease, the second pressurizing member 182 is controlled to continuously pressurize until the condensing pressure reaches the second preset pressure.

It can be appreciated that the first preset pressure is the rated pressure of the evaporating pressure when the indoor heat exchanger 140 is operating normally; the second preset pressure is a rated pressure of the condensing pressure when the indoor heat exchanger 140 is operating normally.

In one embodiment, the heat pump assembly 100 further includes a support bracket (not shown) for supporting the pressurizing assembly 180. The support frame is an external support member, which is disposed at a corresponding floor and is used for supporting the corresponding first pressing member 181 and second pressing member 182, so as to prevent the main connection pipe 110 from falling due to the gravity of the first pressing member 181 and the second pressing member 182.

Referring to fig. 1 and 9, it can be understood that, when the first pressurizing member 181 is operated, cavitation of the first pressurizing member 181 may occur due to a pressure decrease or insufficient liquid supply, that is, the pressure in the first pressurizing member 181 is lower than the evaporation pressure of the liquid refrigerant, so that flash gas may occur, and thus corrosion phenomenon occurs to the inside of the first pressurizing member 181. Based on this, the heat pump unit 100 of an embodiment of the present invention provides two solutions:

one is by ensuring a sufficient degree of supercooling of the refrigerant liquid prior to entering the first pressurizing member 181. This reduces the probability of liquid flashing. The principle is that since the conditions of the liquid flash evaporation can be obtained by taking heat from the inside of the liquid in addition to the pressure reduction, it is ensured that the liquid refrigerant is sufficiently supercooled to prevent the flash evaporation, thereby avoiding cavitation, and optionally, the outdoor heat exchanger 130 further includes a supercooling part for supercooling the refrigerant entering the first pressurizing part 181. For example, the length of the first heat exchange member 1312 may be increased to ensure a proper supercooling degree. Of course, in other embodiments of the present invention, means such as flexibly increasing the rotational speed of the fan in the outdoor heat exchanger 130 may be used to ensure proper supercooling.

The other is to avoid cavitation by ensuring that the refrigerant liquid at the suction port of the first pressurizing member 181 is not interrupted, that is, by ensuring that the suction port is sufficiently flowed with the liquid refrigerant. The present invention provides the liquid refrigerant of the suction port to flow uninterruptedly by providing the liquid storage part 190 with the first pressurizing part 181. Specifically, the heat pump unit 100 further includes a liquid storage component 190 and a switch valve (not shown) located at two ends of the liquid storage component 190, one end of the liquid storage component 190 is connected to the liquid pipe 111, the other end of the liquid storage component 190 is connected to the inlet of the first pressurizing component 181, and the switch valve is used for realizing on-off between the liquid storage component 190 and the first pressurizing component 181.

The liquid storage part 190 is used to store the refrigerant to ensure that the suction port of the first pressurizing part 181 has sufficient liquid refrigerant so that the liquid refrigerant at the suction port continuously flows to avoid cavitation. Illustratively, the reservoir 190 is a reservoir and the on-off valve is a solenoid valve. One end of the liquid storage part 190 is connected with the liquid pipe 111, a switch valve is arranged between the liquid storage part 190 and the liquid pipe to control the amount of the refrigerant entering the liquid storage part 190, the other end of the liquid storage part 190 is connected with the suction inlet of the first pressurizing part 181, and a switch valve is arranged between the liquid storage part 190 and the suction inlet of the first pressurizing part 181 to control the amount of the refrigerant entering the first pressurizing part 181. When the heat pump unit 100 is in operation, the liquid pipe 111 and the switch valve of the liquid storage part 190 are opened periodically to ensure that the liquid storage part 190 has refrigerant liquid.

When the pressure of the suction inlet of the first pressurizing part 181 is too low, the switch valve between the liquid pipe 111 and the liquid storage part 190 is closed, and the switch valve between the liquid storage part 190 and the first pressurizing part 181 is opened, so that the refrigerant liquid in the liquid storage part 190 can be ensured to continuously flow into the suction inlet of the liquid pump, and cavitation is avoided.

In one embodiment, each horizontal indoor heat exchanger 140 corresponds to one pressurizing assembly 180 or one pressurizing assembly 180 and a liquid storage member 190. That is, the first distribution part 170 of each floor corresponds to one pressurizing assembly 180 or one pressurizing assembly 180 and the liquid storage part 190. Thus, the operation of the indoor heat exchanger 140 of each floor can be monitored, and the energy consumption of the heat pump unit 100 can be reduced.

It should be noted that, in the preset height range, the evaporation pressure or the condensation pressure of the refrigerant is not affected when the heat pump unit 100 is operated, and when the preset height is exceeded, the evaporation pressure or the condensation pressure of the refrigerant is significantly reduced. At this time, the pressurizing assembly 180 or one pressurizing assembly 180 and the liquid storage member 190 may be provided only above a predetermined height range. It will be appreciated that the preset height range herein refers to a range from one floor to less than ten floors, and is selected according to the actual working conditions. In this embodiment, each floor is provided with a pressurizing assembly 180 and a liquid storage component 190, so as to ensure normal operation of the heat pump unit 100 and reduce power consumption.

When the heat pump unit 100 is operated, the control system acquires the suction pressure at the suction port of the first pressurizing member 181. If the suction pressure is equal to the third preset pressure, the first pressurizing member 181 operates normally. At this time, the on-off valve between the liquid storage member 190 and the first pressurizing member 181 is closed, and the liquid storage member 190 does not need to be used to convey the refrigerant to the first pressurizing member 181. If the suction pressure is lower than the third preset pressure, the suction pressure at the suction inlet of the first pressurizing member 181 needs to be adjusted to avoid cavitation of the first pressurizing member 181. It is understood that the third preset pressure refers to the rated suction pressure at the suction inlet of the first pressurizing member 181 when the first pressurizing member 181 is operating normally.

The suction pressure at the suction port of the first pressurizing member 181 is ensured in two ways, and the first is to increase the supercooling degree of the refrigerant, and at this time, the length of the first heat exchanging member 1312 may be increased or the rotation speed of the fan in the outdoor heat exchanger 130 may be increased. The second is to control the liquid storage part 190 to deliver the refrigerant to the first pressurizing part 181. That is, the switch valve between the liquid pipe 111 and the liquid storage part 190 is closed, and the switch valve between the liquid storage part 190 and the first pressurizing part 181 is opened, so that the refrigerant liquid in the liquid storage part 190 can be ensured to flow into the suction inlet of the liquid pump continuously.

If the suction pressure is restored to the third preset pressure, the first pressurizing member 181 is controlled to restore the initial state. I.e., to reduce the degree of supercooling of the refrigerant or to close the switching valve between the liquid storage part 190 and the first pressurizing part 181. If the suction pressure continues to decrease, the rotational speed of the first pressurizing member 181 downstream of the control increases. That is, assuming that the suction pressure at the suction port of the first pressurizing member 181 at the tenth floor continues to decrease, the rotation speed of the first pressurizing member 181 downstream of the control, i.e., the ninth floor, increases. Of course, it is also possible to employ an increase in the rotor speed of the compressor 120 so that the suction pressure is restored to the normal state. After the suction pressure is restored to the normal state, the rotation speed of the downstream first pressurizing member 181 correspondingly decreases or correspondingly decreases the rotation speed of the rotor of the compressor 120.

The heat pump unit 100 of the invention realizes one-time heat exchange of the heat pump unit 100 through direct evaporation of the refrigerant, thereby reducing the energy consumption of the system and improving the accuracy of indoor temperature control. Meanwhile, the heat pump unit 100 is integrated to solve the problem that the traditional multi-split air conditioner is complex to install, and the occupied area is overlarge due to the installation interval among the multi-split air conditioner A is needed to be considered. And, the design of evaporating pressure and condensing pressure ensures the high operation energy efficiency of the heat pump unit 100, and reduces the energy consumption of the unit.

Referring to fig. 1 and 10, an embodiment of the present invention further provides a control method of a heat pump unit 100, in which the opening degree of the first throttling part 150 is changed with the indoor load during the cooling operation of the heat pump unit 100, the second throttling part 160 is fully opened, and in which the opening degree of the first throttling part 150 is fully opened during the heating operation of the heat pump unit 100, the opening degree of the second throttling part 160 is changed with the indoor load.

The control method comprises the following steps:

acquiring response of indoor load, opening the corresponding indoor heat exchanger 140, and opening the corresponding refrigeration valve 173 or heating valve 174 of the first distribution part 170;

the opening degree of the first throttle member 150 or the second throttle member 160 is adjusted according to the respective indoor loads.

The control system can control the operation of each component according to the actual use requirement of a user. Specifically, when a room in a certain floor has a cooling or heating demand response, the heat pump unit 100 is started, and the cooling valve 173 or the heating valve 174 corresponding to the indoor heat exchanger 140 corresponding to the room is opened first, and the first throttling part 150 or the second throttling part 160 is kept to have a certain opening degree. Therefore, the refrigerating or heating of the indoor space can be realized, so that the use requirement of a user can be met. And, when the indoor load is changed accordingly, the control system adjusts the opening degree of the first throttle member 150 or the second throttle member 160 accordingly. When the indoor load is not changed, the heat pump unit 100 maintains a normal operation.

In an embodiment, the step of adjusting the opening degree of the first throttle member 150 or the second throttle member 160 according to the respective indoor loads includes the steps of:

when the indoor load becomes large, the opening degree of the first throttle member 150 or the second throttle member 160 is increased, or the rotor rotation speed of the compressor 120 is increased;

when the indoor load becomes small, the opening degree of the first throttle member 150 or the second throttle member 160 is reduced, or the rotor speed of the compressor 120 is reduced.

When the load increases, the heating set temperature value generally increases, and the cooling set temperature value decreases. In the cooling operation of the heat pump unit 100, it is necessary to increase the opening degree of the first throttling part 150 or increase the rotor speed of the compressor 120 to increase the heat exchange amount. In the heating operation of the heat pump unit 100, it is necessary to increase the opening degree of the second throttle 160 or increase the rotor speed of the compressor 120 to increase the heat exchange amount.

When the load decreases, the heating set temperature value generally decreases, and the cooling set temperature value increases. In the cooling operation of the heat pump unit 100, it is necessary to decrease the opening degree of the first throttling part 150 or decrease the rotor speed of the compressor 120 to increase the heat exchange amount. In the heating operation of the heat pump unit 100, it is necessary to reduce the opening degree of the second throttle member 160 or reduce the rotor speed of the compressor 120 to increase the heat exchange amount.

Referring to fig. 1, 8 and 11, in an embodiment, the control method further includes the steps of:

acquiring an evaporation pressure or a condensation pressure of the refrigerant in the indoor heat exchanger 140 at a certain level;

if the evaporation pressure or the condensation pressure below the level is normal, the pressurizing assembly 180 does not operate;

if the evaporation pressure or the condensation pressure at the level and above is lowered, the pressurizing unit 180 operates.

The control system can acquire the evaporation pressure or the condensation pressure of the refrigerant in the indoor heat exchanger 140 in real time. If the evaporating pressure or condensing pressure is normal, the pressurizing assembly 180 does not operate. If the evaporating pressure or condensing pressure is reduced, the pressurizing assembly 180 operates to increase the refrigerant, reduce the pressure loss of the refrigerant, and reduce the power consumption of the heat pump unit 100.

In one embodiment, the step of operating the pressurizing assembly 180 if the evaporating pressure or condensing pressure decreases includes the steps of:

when the evaporation pressure is lower than the first preset pressure, the first pressurizing part 181 is controlled to be opened, and the first valve 183 is controlled to be closed;

if the evaporating pressure reaches the first preset pressure, the first valve 183 is controlled to be opened, and the first pressurizing part 181 is closed;

if the evaporation pressure continues to decrease, the first pressurizing unit 181 is controlled to continuously pressurize until the evaporation pressure reaches the first preset pressure.

After the control system obtains the evaporation pressure of the refrigerant at a certain level, if the evaporation pressure is not reduced below the level, the control system maintains the closed state of the first pressurizing member 181, and maintains the open state of the first valve 183. At this time, the refrigerant is directly transferred to the indoor heat exchanger 140 through the liquid pipe 111 via the first valve 183. If the evaporation pressure at the level and above is reduced and is lower than the first preset pressure, the first valve 183 is controlled to be closed, and the first pressurizing member 181 is controlled to be opened. The refrigerant in the liquid pipe 111 is pressurized by the first pressurizing member 181, and is sent to the indoor heat exchanger 140 after being pressurized. This reduces the pressure loss of the refrigerant and reduces the energy consumption of the heat pump unit 100.

Referring to fig. 1, 9 and 12, in one embodiment, the step of operating the pressurizing assembly 180 if the evaporating pressure or condensing pressure decreases includes the steps of:

when the condensing pressure is lower than the second preset pressure, the second pressurizing member 182 is controlled to be opened, and the second valve 184 is controlled to be closed;

if the condensing pressure reaches the second preset pressure, the second valve 184 is controlled to be opened, and the second pressurizing member 182 is closed;

if the condensing pressure continues to decrease, the second pressurizing member 182 is controlled to continuously pressurize until the evaporating pressure reaches the second preset pressure.

In an embodiment, the control method further comprises the steps of:

acquiring the suction pressure at the inlet of the first pressurizing member 181;

if the suction pressure is equal to the third preset pressure, the first pressurizing member 181 is closed and the first valve 183 is opened;

if the suction pressure is lower than the third preset pressure, the liquid storage part 190 is controlled to deliver the refrigerant to the first pressurizing part 181, and/or the supercooling degree of the refrigerant is increased, and/or the rotation speed of the downstream first pressurizing part 181 is controlled to be increased;

if the suction pressure is restored to the third preset pressure, the first pressurizing part 181 is controlled to restore the initial state;

If the suction pressure continues to decrease, the rotational speed of the first pressurizing member 181 downstream of the control is increased, and/or the rotational speed of the rotor of the compressor 120 is increased.

When the heat pump unit 100 is operated, the control system acquires the suction pressure at the suction port of the first pressurizing member 181. If the suction pressure is equal to the third preset pressure, the first pressurizing member 181 is closed and the first valve 183 is opened. At this time, the on-off valve between the liquid storage member 190 and the first pressurizing member 181 is closed, and the liquid storage member 190 does not need to be used to convey the refrigerant to the first pressurizing member 181. If the suction pressure is lower than the third preset pressure, the suction pressure at the suction inlet of the first pressurizing member 181 needs to be adjusted to avoid cavitation of the first pressurizing member 181. It is understood that the third preset pressure refers to the rated suction pressure at the suction inlet of the first pressurizing member 181 when the first pressurizing member 181 is operating normally.

The technical features of the above-described embodiments may be arbitrarily combined, and all possible combinations of the technical features in the above-described embodiments are not described for brevity of description, however, as long as there is no contradiction between the combinations of the technical features, they should be regarded as the description scope of the present specification.

The foregoing examples illustrate only a few embodiments of the invention and are described in detail herein without thereby limiting the scope of the invention. It should be noted that it will be apparent to those skilled in the art that several variations and modifications can be made without departing from the spirit of the invention, which are all within the scope of the invention. Accordingly, the scope of protection of the present invention is to be determined by the appended claims.

Claims

1. A heat pump assembly, comprising:

a main connecting pipe (110) which is circularly communicated and comprises a liquid pipe (111) and an air pipe (112);

a first throttle member (150) provided to the main connection pipe (110);

a compressor (120) provided to the main connection pipe (110);

an outdoor heat exchanger (130) which is located between the first throttle member (150) and the compressor (120) and communicates with the main connection pipe (110) on one side of the compressor (120);

an indoor heat exchanger (140) located between the first throttling part (150) and the compressor (120) and communicated with the main connecting pipe (110) at the other side of the compressor (120), wherein the indoor heat exchanger (140) is also arranged in an indoor space and can directly exchange heat with air in the indoor space;

a second throttling part (160) located between the indoor heat exchanger (140) and the first throttling part (150); and

a pressurizing unit (180) provided to the main connection pipe (110);

a control system connected to the pressurizing assembly (180) for obtaining an evaporation pressure or a condensation pressure of the refrigerant in the indoor heat exchanger (140) at a certain level;

the pressurizing assembly (180) comprises a first pressurizing component (181) and a first valve (183), wherein the first pressurizing component (181) is arranged on the liquid pipe (111) and is used for pressurizing liquid-state refrigerant in the liquid pipe (111), and two ends of the first valve (183) are connected to the liquid pipe (111) and are arranged in parallel with the first pressurizing component (181); the control system is used for controlling the first pressurizing part (181) to be opened and controlling the first valve (183) to be closed when the evaporation pressure is lower than a first preset pressure when the evaporation pressure or the condensation pressure at the level and above is reduced; if the evaporation pressure reaches a first preset pressure, controlling the first valve (183) to be opened, and controlling the first pressurizing component (181) to be closed; if the evaporation pressure continues to drop, controlling the first pressurizing component (181) to continuously pressurize until the evaporation pressure reaches the first preset pressure; and/or

The pressurizing assembly (180) comprises a second pressurizing component (182) and a second valve (184), the second pressurizing component (182) is arranged on the air pipe (112) and is used for pressurizing gaseous refrigerant in the air pipe (112), and two ends of the second valve (184) are connected to the air pipe (112) and are arranged in parallel with the second pressurizing component (182); the control system is used for controlling the second pressurizing part (182) to be opened and the second valve (184) to be closed when the condensing pressure is lower than a second preset pressure when the evaporating pressure or the condensing pressure at the level and above is reduced; controlling the second valve (184) to open and the second pressurizing member (182) to close if the condensing pressure reaches a second preset pressure; if the condensing pressure continues to drop, the second pressurizing component (182) is controlled to continuously pressurize until the evaporating pressure reaches a second preset pressure.

2. The heat pump assembly according to claim 1, wherein the outdoor heat exchanger (130) comprises an evaporative condensing heat exchanger (131) and/or an air-cooled heat exchanger (132).

3. The heat pump unit according to claim 2, wherein the evaporative condensing heat exchanger (131) comprises a first heat exchange component (1312), the first heat exchange component (1312) is disposed in a heat exchange box (1311), two ends of the first heat exchange component (1312) are respectively connected with the main connecting pipe (110), and a water film can be attached to the outer wall of the first heat exchange component (1312).

4. A heat pump assembly according to claim 3, wherein the evaporative condensing heat exchanger (131) further comprises a spray assembly (1313) for performing a spray operation on the first heat exchange member (1312).

5. The heat pump assembly of claim 4, wherein the spray assembly (1313) comprises:

-a water tank (13131) located below the first heat exchange member (1312);

a delivery line (13132) in communication with the water tank (13131) for delivering water in the water tank (13131);

and a spraying component (13133) communicated with the conveying pipeline (13132) and aligned with the spraying component (13133) for spraying water to the first heat exchange component (1312).

6. The heat pump assembly according to claim 5, wherein the spray assembly (1313) further comprises a water pump (13134) arranged on the delivery line (13132) for delivering water in the water tank (13131) to the spray member (13133) via the delivery line (13132).

7. A heat pump unit according to claim 3, wherein the evaporative condensing heat exchanger (131) further comprises a water basin with water, the first heat exchange member (1312) being immersed in the water basin.

8. A heat pump unit according to claim 3, wherein the evaporative condensing heat exchanger (131) further comprises a heat exchange box (1311), the first heat exchange component (1312) is located in the heat exchange box (1311), the heat exchange box (1311) has an air inlet (13111) and an air outlet (13112), and both the air inlet (13111) and the air outlet (13112) are communicated with the outdoor environment.

9. The heat pump assembly of claim 8, wherein the evaporative condensing heat exchanger (131) further comprises a first fan (1314) and a second fan (1315), the first fan (1314) is disposed at the air inlet (13111), and the second fan (1315) is disposed at the air outlet (13112).

10. The heat pump assembly according to claim 8, wherein the evaporative condensing heat exchanger (131) is positionable in the indoor space.

11. A heat pump assembly according to claim 3, wherein the first heat exchanging element (1312) is bent at least twice or the first heat exchanging element (1312) is bent once.

12. The heat pump assembly according to claim 2, wherein the air-cooled heat exchanger (132) comprises a plurality of sets of second heat exchanging elements (1321) and a third fan (1322) corresponding to each set of the second heat exchanging elements (1321), and the plurality of sets of second heat exchanging elements (1321) are arranged in parallel.

13. The heat pump assembly according to claim 12, wherein each set of the second heat exchanging elements (1321) comprises two sets of fin tube heat exchangers and fin edge plates provided to the fin tube heat exchangers, the two sets of the fin tube heat exchangers are arranged in a V-shape, and two adjacent sets of the second heat exchanging elements (1321) are connected by the fin edge plates.

14. The heat pump assembly according to claim 13, wherein a predetermined distance exists between adjacent third fans (1322).

15. The heat pump assembly according to any one of claims 1 to 13, wherein the first throttle member (150) is provided to the indoor heat exchanger (140).

16. Heat pump assembly according to any of claims 1 to 13, wherein the compressor (120) comprises a magnetic levitation compressor or an air levitation compressor.

17. The heat pump assembly according to any one of claims 1 to 13, further comprising a support frame for supporting the pressurizing assembly (180).

18. The heat pump unit according to any one of claims 1 to 13, further comprising a liquid storage part (190) and a switch valve located at two ends of the liquid storage part (190), wherein one end of the liquid storage part (190) is connected to the liquid pipe (111), the other end of the liquid storage part (190) is connected to the inlet of the first pressurizing part (181), and the switch valve is used for realizing on-off between the liquid storage part (190) and the first pressurizing part (181).

19. The heat pump assembly according to any one of claims 1 to 13, wherein the outdoor heat exchanger (130) further comprises a supercooling member for supercooling the refrigerant entering the first pressurizing member (181).

20. The heat pump assembly according to claim 18, further comprising a first distribution member (170), wherein the number of indoor heat exchangers (140) is plural, and each indoor heat exchanger (140) is located at the same level and is connected to the main connection pipe (110) through the first distribution member (170).

21. The heat pump assembly according to claim 18, further comprising a plurality of first distribution members (170), wherein the number of the indoor heat exchangers (140) is plural, and the levels of at least two indoor heat exchangers (140) are different, and at least one indoor heat exchanger (140) of each level is connected to the main connection pipe (110) through a corresponding first distribution member (170);

each horizontal indoor heat exchanger (140) corresponds to one pressurizing assembly (180) or one pressurizing assembly (180) and the liquid storage component (190).

22. The heat pump assembly according to claim 21, wherein the first distribution part (170) includes a distribution tank (171), a plurality of distribution pipes (172), a refrigeration valve (173), and a heating valve (174), the distribution pipes (172) connect the indoor heat exchanger (140) and the main connection pipe (110), and the refrigeration valve (173) and the heating valve (174) are respectively disposed in the corresponding distribution pipes (172).

23. The heat pump assembly according to claim 22, wherein the air pipe (112) and the liquid pipe (111) are directly connected to the first distribution member (170) of each level;

alternatively, the main connection pipe (110) further comprises a plurality of gas branch pipes (114) and a plurality of liquid branch pipes (113), the gas pipe (112) is connected with each of the first distribution members (170) through a plurality of the gas branch pipes (114), and the liquid pipe (111) is connected with each of the first distribution members (170) through a plurality of the liquid branch pipes (113).

24. A control method of a heat pump unit, characterized in that the control method is used for controlling the heat pump unit (100) according to any one of claims 1 to 23, when the heat pump unit (100) is in refrigeration operation, the opening degree of a first throttling component (150) changes along with indoor load, a second throttling component (160) is fully opened, when the heat pump unit (100) is in heating operation, the first throttling component (150) is fully opened, and the opening degree of the second throttling component (160) changes along with the indoor load;

The control method comprises the following steps:

acquiring the response of the indoor load, opening the corresponding indoor heat exchanger (140), and opening a refrigeration valve (173) or a heating valve (174) corresponding to the first distribution component (170);

the opening degree of the first throttle member (150) or the second throttle member (160) is adjusted in accordance with the respective indoor loads.

25. The control method according to claim 24, characterized in that said step of adjusting the opening degree of said first throttle member (150) or said second throttle member (160) according to the respective indoor loads includes the steps of:

increasing the opening degree of the first throttle member (150) or the second throttle member (160) or increasing the rotor speed of the compressor (120) when the indoor load becomes large;

when the indoor load becomes small, the opening degree of the first throttle member (150) or the second throttle member (160) is reduced, or the rotor speed of the compressor (120) is reduced.

26. The control method according to claim 24, characterized in that the control method further comprises the step of:

if the evaporation pressure or the condensation pressure below the level is normal, the pressurizing assembly (180) is not operated.

27. The control method according to claim 24, characterized in that the control method further comprises the step of:

acquiring suction pressure at a suction port of the first pressurizing member (181);

if the suction pressure is equal to a third preset pressure, the first pressurizing member (181) is closed and the first valve (183) is opened;

if the suction pressure is lower than the third preset pressure, controlling a liquid storage component (190) to deliver the refrigerant to the first pressurizing component (181), and/or increasing the supercooling degree of the refrigerant and/or controlling the rotating speed of the first pressurizing component (181) at the downstream to increase;

if the suction pressure is restored to the third preset pressure, controlling the first pressurizing member (181) to restore the initial state;

if the suction pressure continues to decrease, the rotational speed of the first pressurizing member (181) downstream is controlled to increase, and/or the rotational speed of the rotor of the compressor (120) is controlled to increase.