CN215570858U - Air conditioner outdoor unit and air conditioning system - Google Patents

Abstract

The application discloses air condensing units and air conditioning system, air condensing units includes: a chassis; the shell is arranged on the chassis and forms an installation cavity with the chassis; the auxiliary heat exchanger is arranged in the installation cavity and comprises a heat exchange main body and a collecting pipe assembly, the collecting pipe assembly is used for providing refrigerant flow for the heat exchange main body, and the heat exchange main body is used for heating the installation cavity. According to the scheme, the auxiliary heat exchanger does not need to be powered, potential safety hazards of electric leakage are avoided, and safety performance of the air conditioner outdoor unit is improved.

Description

Air conditioner outdoor unit and air conditioning system

Technical Field

The application relates to the technical field of air conditioners, in particular to an air conditioner outdoor unit and an air conditioning system.

Background

The outdoor unit of the air conditioner is arranged outdoors, and the outdoor environment temperature is relatively low, for example, the environment temperature is-20 degrees; the drain hole of the outdoor unit of the air conditioner is frozen or frosted. At present, an outdoor unit of an air conditioner is provided with an electric heating device to prevent a drain hole from being frozen, and the electric heating device has potential safety hazards of electric leakage.

SUMMERY OF THE UTILITY MODEL

The application at least provides an air conditioner outdoor unit and an air conditioning system.

The present application provides in a first aspect an outdoor unit of an air conditioner, including:

a chassis;

the shell is arranged on the chassis and forms an installation cavity with the chassis;

the auxiliary heat exchanger is arranged in the installation cavity and comprises a heat exchange main body and a collecting pipe assembly, the collecting pipe assembly is used for providing refrigerant flow for the heat exchange main body, and the heat exchange main body is used for heating the installation cavity.

The second aspect of the present application provides an air conditioning system, air conditioning system includes compressor, cross valve, indoor heat exchanger, auxiliary heat exchanger and foretell air condensing units, auxiliary heat exchanger sets up in air condensing units's the installation cavity, be used for the heating the installation cavity, the compressor passes through the cross valve is in air condensing units with provide the refrigerant stream of circulation flow between the indoor heat exchanger.

The beneficial effect of this application is: the application discloses air condensing units includes: a chassis; the shell is arranged on the chassis and forms an installation cavity with the chassis; the auxiliary heat exchanger is arranged in the installation cavity and comprises a heat exchange main body and a collecting pipe assembly, the collecting pipe assembly is used for providing refrigerant flow to the heat exchange main body, and the heat exchange main body is used for heating the installation cavity; the refrigerant flow through the heat exchange main body dissipates heat, so that the heating installation cavity is realized, icing or frosting is prevented, the auxiliary heat exchanger does not need power supply, the potential safety hazard of electric leakage is avoided, and the safety performance of the outdoor unit of the air conditioner is improved.

It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the application.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the present application and, together with the description, serve to explain the principles of the application.

Fig. 1 is a schematic structural diagram of an air conditioning system in an embodiment of the present application;

FIG. 2 is a schematic structural diagram of a heat exchange body of the heat exchanger of FIG. 1;

FIG. 3 is a schematic structural view of the single-layer microchannel and the multi-layer microchannel of FIG. 2;

FIG. 4 is a schematic block diagram of an embodiment of a manifold assembly of the heat exchanger of FIG. 1;

FIG. 5 is a schematic structural view of another embodiment of a header assembly of the heat exchanger of FIG. 1;

FIG. 6 is a schematic block diagram of yet another embodiment of a header assembly of the heat exchanger of FIG. 1;

FIG. 7 is a schematic structural diagram of a heat exchange body of a heat exchanger according to another embodiment of the present application;

FIG. 8 is a perspective view of the first tube of FIG. 7;

FIG. 9 is a schematic structural diagram of a heat exchange body of a heat exchanger according to another embodiment of the present application;

FIG. 10 is a schematic diagram of the heat exchanger of FIG. 9;

fig. 11 is a schematic perspective view of an outdoor unit of an air conditioner according to an embodiment of the present application;

FIG. 12 is an enlarged view of region A of FIG. 11;

FIG. 13 is a schematic diagram of a framework of an air conditioning system according to an embodiment of the present application;

fig. 14 is a flow chart diagram of a control method applied to the air conditioning system of fig. 13;

FIG. 15 is a flowchart illustrating an embodiment of step S142 in FIG. 14;

fig. 16 is a schematic flowchart of another embodiment of step S142 in fig. 14.

Detailed Description

The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are only a part of the embodiments of the present application, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.

Reference herein to "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment can be included in at least one embodiment of the application. The appearances of the phrase in various places in the specification are not necessarily all referring to the same embodiment, nor are separate or alternative embodiments mutually exclusive of other embodiments. It is explicitly and implicitly understood by one skilled in the art that the embodiments described herein can be combined with other embodiments.

Referring to fig. 1, fig. 1 is a schematic structural diagram of an air conditioning system according to an embodiment of the present application. As shown in fig. 1, the air conditioning system 1 mainly includes a compressor 2, a four-way valve 3, an outdoor heat exchanger 4, an indoor heat exchanger 5, a heat exchanger 6, an expansion valve 12, and an expansion valve 13. The expansion valve 13 and the heat exchanger 6 are disposed between the outdoor heat exchanger 4 and the indoor heat exchanger 5, and the compressor 2 provides a refrigerant flow circulating between the outdoor heat exchanger 4 and the indoor heat exchanger 5 through the four-way valve 3.

The heat exchanger 6 includes a first heat exchange path 610 and a second heat exchange path 611, a first end of the first heat exchange path 610 is connected to the outdoor heat exchanger 4 through an expansion valve 13, a second end of the first heat exchange path 610 is connected to the indoor heat exchanger 5, a first end of the second heat exchange path 611 is connected to a second end of the first heat exchange path 610 through an expansion valve 12, and a second end of the second heat exchange path 611 is connected to the suction port 22 of the compressor 2.

When the air conditioning system 1 is in the cooling mode, the path of the refrigerant flow is as follows:

the exhaust port 21 of the compressor 2, the connection port 31 of the four-way valve 3, the connection port 32 of the four-way valve 3, the outdoor heat exchanger 4, the heat exchanger 6, the indoor heat exchanger 5, the connection port 33 of the four-way valve 3, the connection port 34 of the four-way valve 3, and the suction port 22 of the compressor 2.

The path (main path) of the refrigerant flow of the first heat exchange channel 610 is: a first end of the first heat exchange channel 610-a second end of the first heat exchange channel 610-the indoor heat exchanger 5. The path (sub path) of the refrigerant flow of the second heat exchange channel 611 is: the second end of the first heat exchange passage 610-the expansion valve 12-the first end of the second heat exchange passage 611-the second end of the second heat exchange passage 611-the suction port 22 of the compressor 2.

For example, the operating principle of the air conditioning system 1 at this time is: the outdoor heat exchanger 4 serves as a condenser, and outputs a medium-pressure medium-temperature refrigerant flow (the temperature may be 40 ° or less) through the expansion valve 13, the refrigerant flow of the first heat exchange channel 610 is the medium-pressure medium-temperature refrigerant flow, the expansion valve 12 converts the medium-pressure medium-temperature refrigerant flow into a low-pressure low-temperature refrigerant flow (the temperature may be 10 ° or less, and a gas-liquid two-phase refrigerant flow), and the refrigerant flow of the second heat exchange channel 611 is the low-pressure low-temperature refrigerant flow. The low-pressure low-temperature refrigerant flow of the second heat exchange channel 611 absorbs heat from the medium-pressure medium-temperature refrigerant flow of the first heat exchange channel 610, and further the refrigerant flow of the second heat exchange channel 611 is gasified, so that the refrigerant flow of the first heat exchange channel 610 is further supercooled. The gasified refrigerant flow of the second heat exchange channel 611 performs enhanced vapor injection on the compressor 2, so as to improve the refrigerating capacity of the air conditioning system 1.

The expansion valve 12 is used as a throttling component of the second heat exchange channel 611, and adjusts the flow rate of the refrigerant flow of the second heat exchange channel 611. The refrigerant flow of the first heat exchange channel 610 exchanges heat with the refrigerant flow of the second heat exchange channel 611 to supercool the refrigerant flow of the first heat exchange channel 610. Therefore, the heat exchanger 6 can be used as an economizer of the air conditioning system 1, and the supercooling degree is improved, so that the heat exchange efficiency of the air conditioning system 1 is improved.

Further, as understood by those skilled in the art, in the heating mode, the connection port 31 of the four-way valve 3 is connected to the connection port 33, and the connection port 32 of the four-way valve 3 is connected to the connection port 34. The refrigerant flow output from the compressor 2 through the discharge port 21 flows from the indoor heat exchanger 5 to the outdoor heat exchanger 4, and the indoor heat exchanger 5 serves as a condenser. At this time, the refrigerant flow output from the indoor heat exchanger 5 is divided into two paths, one of which flows into the first heat exchange channel 610 (main path), and the other of which flows into the second heat exchange channel 611 (auxiliary path) via the expansion valve 12. The refrigerant flow of the second heat exchange channel 611 can also realize supercooling of the refrigerant flow of the first heat exchange channel 610, and the refrigerant flow flowing through the second heat exchange channel 611 performs air supplement and enthalpy increase on the compressor 2, so that the heating capacity of the air conditioner is improved.

The present application further optimizes the following aspects based on the overall structure of the air conditioning system 1 described above:

1. micro-channel heat exchanger

As shown in fig. 2, the heat exchanger 6 comprises a heat exchange body 61, the heat exchange body 61 is provided with a plurality of microchannels 612, and the plurality of microchannels 612 are divided into a first microchannel and a second microchannel, wherein the first microchannel serves as a first heat exchange channel 610 of the heat exchanger 6, and the second microchannel serves as a second heat exchange channel 611 of the heat exchanger 6. Thus, first microchannel 610 is given the same reference number as first heat exchange channel 610 and second microchannel 611 is given the same reference number as second heat exchange channel 611.

The heat exchange body 61 may comprise a single plate body 613, the plate body 613 is provided with a plurality of microchannels 612, the plurality of microchannels 612 of the plate body 613 may be divided into first microchannels 610 and second microchannels 611 which are alternately arranged, and an extending direction D1 of the first microchannels 610 and an extending direction D2 of the second microchannels 611 are parallel to each other, for example, the extending direction D1 of the first microchannels 610 is the same as the extending direction D2 of the second microchannels 611. The board 613 may be a flat pipe so that a heat dissipation element or an electronic element may be disposed on the board 613. In other embodiments, the plate body 613 may also be a carrier with a cross section of other shapes, such as a cylinder, a rectangular parallelepiped, a cube, and the like. In other embodiments, as described below, the heat exchange body 61 may also include at least two plates disposed on top of each other or two tubes nested within each other.

The cross-sectional shape of each micro channel 612 perpendicular to its extension direction may be rectangular, with each micro channel 612 having a side of 0.5mm to 3 mm. The thickness between each micro channel 612 and the surface of plate body 613 and between micro channels 612 is 0.2mm-0.5mm so that micro channels 612 meet the requirements of pressure resistance and heat transfer performance. In other embodiments, the cross-sectional shape of the micro-channels 612 may be other shapes, such as circular, triangular, trapezoidal, elliptical, or irregular.

For example, in the cooling mode of the air conditioning system shown in fig. 1, a first refrigerant flow (i.e., a medium-pressure medium-temperature refrigerant flow) flows through the first microchannel 610, a second refrigerant flow (i.e., a low-pressure low-temperature refrigerant flow) flows through the second microchannel 611, the first refrigerant flow may be a liquid-phase refrigerant flow, and the second refrigerant flow may be a gas-liquid two-phase refrigerant flow. The second refrigerant stream absorbs heat from the first refrigerant stream of the first microchannel 610 during flow along the second microchannel 611 and is further vaporized to further subcool the first refrigerant stream.

It should be noted that the heat exchanger based on the micro-channel structure described above and below is not limited to the application scenario shown in fig. 1, and thus the first micro-channel 610 and the second micro-channel 611 and the "first" and "second" in the first refrigerant flow and the second refrigerant flow are only used for distinguishing different micro-channels and refrigerant flows, and should not be considered as limiting the specific application of the micro-channels and refrigerant flows. For example, in other embodiments or operation modes, the first refrigerant flow flowing through the first microchannel 610 absorbs heat of the second refrigerant flow of the second microchannel 611, and the states of the first refrigerant flow and the second refrigerant flow are not limited to the liquid phase or the gas-liquid two-phase as defined above.

As shown in fig. 1, the flow direction a1 of the first refrigerant flow is opposite to the flow direction a2 of the second refrigerant flow, so that a large temperature difference exists between the temperature of the first refrigerant flow and the temperature of the second refrigerant flow, and the heat exchange efficiency of the first refrigerant flow and the second refrigerant flow is improved.

Alternatively, the flow direction a1 of the first refrigerant stream may be the same as or perpendicular to the flow direction a2 of the second refrigerant stream.

Alternatively, heat exchange body 61 may comprise at least two sets of first microchannels 610 and second microchannels 611, which sets of first microchannels 610 and second microchannels 611 are spaced apart from each other in a direction perpendicular to the direction of extension D1, which is the width direction of plate body 613, as shown in fig. 2, and in other embodiments, which may be the thickness direction of plate body 613. For example, a first predetermined number of micro-channels in the plurality of micro-channels 612 are divided into first micro-channels 610, a second predetermined number of micro-channels in the plurality of micro-channels 612 are divided into second micro-channels 611, and the plurality of sets of first micro-channels 610 and the plurality of sets of second micro-channels 611 are alternately arranged in sequence, that is, the second micro-channels 611 are arranged between two sets of first micro-channels 610, and the first micro-channels 610 are arranged between two sets of second micro-channels 611, so that the at least two sets of first micro-channels 610 and the second micro-channels 611 are arranged at intervals to form the heat exchanger 6 in which the first micro-channels 610 and the second micro-channels 611 are alternately arranged, as shown in fig. 2. The first and second preset numbers may be equal, for example 3; in other embodiments, the first predetermined number and the second predetermined number may not be equal, for example, the first predetermined number is 3 and the second predetermined number is 2.

Alternatively, the first predetermined number and the second predetermined number may be 1, one microchannel in the plurality of microchannels 612 is the first microchannel 610, and one microchannel disposed adjacent to the first microchannel 610 is the second microchannel 611.

Taking the heat exchange body 61 provided with 10 × 10 microchannels 612 as an example, the cross-sectional area of the heat exchange body 61 is the same as that of the conventional channels, and refrigerant flows with the same mass and flow rate respectively flow through the 10 × 10 microchannels 612 and the conventional channels. The characteristic length Dh of each microchannel 612 is 1/10 for the conventional channel, where the pressure drop is related to L/(Dh)²) In proportion, maintaining the same pressure drop, the length L of the microchannel 612 is 1/100 the length of the conventional channel.

The effective heat exchange area of the microchannels 612 is 1/10 the effective heat exchange area of the conventional channels. Based on the formula: the heat transfer coefficient is constant, and the heat transfer coefficient of the micro-channel 612 is 10 times that of the conventional channel; based on the formula: the heat exchange amount is the heat exchange coefficient, and the heat exchange amount of the micro channel 612 is equal to that of the conventional channel. Thus, 10 x 10 microchannels 612 have a length 1/100 that is the length of a conventional channel, i.e., the same thermal load requirements can be met.

Through the above manner, the heat exchange main body 61 is provided with the plurality of first microchannels 610 and the plurality of second microchannels 611, so that the length of the heat exchange main body 61 is shortened, and the volume of the heat exchanger 6 is further reduced under the condition that the heat exchange amount of the economizer is equal.

As shown in fig. 3, the plurality of microchannels 612 may be arranged as a single layer microchannel or a multi-layer microchannel. In fig. 3, the cross-sectional area of the multi-layer microchannel is 4 times the cross-sectional area of the single-layer microchannel, the length of the single-layer microchannel is 4 times the length of the multi-layer microchannel, refrigerant flows with the same mass and flow rate respectively flow through the single-layer microchannel and the multi-layer microchannel, and the flow rate of the multi-layer microchannel is 1/4 of the flow rate of the single-layer microchannel.

Under the condition that the flow state of the refrigerant flow is laminar flow, the pressure drop of the multilayer microchannel is 1/16 of the pressure drop of the single-layer microchannel, wherein the characteristic length of the heat exchange coefficient is constant, the characteristic length is unchanged, the heat exchange coefficient is unchanged, the heat transfer area of the single-layer microchannel and the heat transfer area of the multilayer microchannel are unchanged, and the heat transfer quantity of the single-layer microchannel is identical to the heat transfer quantity of the multilayer microchannel. Therefore, when the flow velocity of the refrigerant flow is low and the flow state of the refrigerant flow is laminar, the larger the cross-sectional area of the plurality of microchannels 612 is, the shorter the length of the plurality of microchannels 612 is, and the flow resistance loss of the refrigerant flow can be reduced.

Under the condition that the flow state of the refrigerant flow is turbulent flow, the pressure drop of the multilayer microchannel is 1/48 of the pressure drop of the single-layer microchannel, at the moment, the heat exchange coefficient has a functional relation with the flow speed of the refrigerant flow, the larger the flow speed of the refrigerant flow is, the larger the heat exchange coefficient is, and therefore the heat transfer capacity of the single-layer microchannel is higher than that of the multilayer microchannel. As described above, when the heat transfer amount is satisfied, the pressure loss of the refrigerant flow can be reduced as the cross-sectional area of the plurality of microchannels 612 is increased.

1.1 manifold Assembly

As shown in fig. 4, the heat exchanger 6 further includes a header assembly 62, and the header assembly 62 and the heat exchange body 61 are horizontally disposed, for example, the header assembly 62 and the heat exchange body 61 are horizontally disposed. In other embodiments, the header assembly 62 is vertically disposed, i.e., the header assembly 62 is disposed along a direction perpendicular to the horizontal plane (i.e., the direction of gravity), and the heat exchange body 61 is horizontally disposed; or, the collecting pipe assembly 62 is vertically arranged, and the heat exchange main body 61 is vertically arranged; alternatively, the header assembly 62 is horizontally disposed and the heat exchange body 61 is vertically disposed.

The header assembly 62 includes a first header 621 and a second header 622, the first header 621 being provided with a first collecting passage, and the second header 622 being provided with a second collecting passage. The cross-sectional shape of the heat exchanger 6 along the flow direction of the refrigerant flow (the first refrigerant flow or the second refrigerant flow) in the heat exchange body 61 is I-shaped. In other embodiments, the cross-sectional shape of the heat exchanger 6 along the flow direction of the refrigerant flow in the heat exchange body 61 may be L-shaped, U-shaped, G-shaped, or circular.

The first collecting channel is connected to the first microchannel 610 to provide the first refrigerant flow to the first microchannel 610 through the first collecting channel and/or to collect the first refrigerant flow flowing through the first microchannel 610. In this embodiment, the number of the first collecting pipes 621 is two, and the two first collecting pipes 621 are respectively connected to two ends of the first microchannel 610, so as to provide a first refrigerant flow to the first microchannel 610 by using one of the two first collecting pipes 621; and the other of the two first headers 621 is used to collect the first refrigerant flow passing through the first micro-channel 610.

For example, in the air conditioning system shown in fig. 1, the first end of the first microchannel 610 is connected to the outdoor heat exchanger 4 through the expansion valve 13 via one of the two first collecting pipes 621, so as to provide the first refrigerant flow to the first microchannel 610 in the cooling mode; the second end of the first microchannel 610 is connected to the indoor heat exchanger 5 through the other of the two first headers 621 to collect the first refrigerant flow flowing through the first microchannel 610. In the heating mode, since the flow direction of the first refrigerant flow in the first microchannels 610 is opposite, the functions of the two first collecting pipes 621 are interchanged compared to the cooling mode.

The second collecting channel is connected to the second microchannel 611 to supply the second refrigerant flow to the second microchannel 611 through the second collecting channel and/or to collect the second refrigerant flow flowing through the second microchannel 611. In this embodiment, the number of the second collecting pipes 622 is two, and the two second collecting pipes 622 are respectively connected to two ends of the second microchannel 611, so as to provide the second refrigerant flow to the second microchannel 611 by using one of the two second collecting pipes 622; and the second refrigerant flow flowing through the second microchannels 611 is collected by the other of the two second headers 622.

For example, in the air conditioning system shown in fig. 1, the first end of the second microchannel 611 is connected to the expansion valve 12 through one of the two second collecting pipes 622 to provide the second refrigerant flow to the second microchannel 611; the second end of the second microchannel 611 is connected to the suction port 22 of the compressor 2 through the other of the two second collecting pipes 622 to collect the second refrigerant flow passing through the second microchannel 611.

In an embodiment, the same end of the first microchannel 610 in the at least two groups of first microchannels 610 and the same end of the second microchannels 611 in the at least two groups of second microchannels 611 are connected to the same first collecting pipe 621, that is, the same end of all the first microchannels 610 of the heat exchanger 6 is connected to the same first collecting pipe 621, and the same end of all the second microchannels 611 of the heat exchanger 6 is connected to the same second collecting pipe 622, so as to avoid providing a corresponding collecting pipe for each microchannel, and reduce the cost.

In the embodiment shown in fig. 4, since the extending direction D1 of the first microchannel 610 and the extending direction D2 of the second microchannel 611 are parallel to each other, the extending directions of the first header 621 and the second header 622 are parallel to each other. However, in other embodiments, the extending directions of the first header 621 and the second header 622 may be adjusted according to the extending directions of the first microchannel 610 and the second microchannel 611, for example, arranged perpendicular to each other.

1.2 the first collecting pipe and the second collecting pipe are arranged at intervals

As shown in fig. 4, the first header 621 and the second header 622 are disposed at intervals along the extending direction of the heat exchange body 61, the extending direction of the heat exchange body 61 is the same as the extending direction D1 of the first microchannel 610 and the extending direction D2 of the second microchannel 611, the second microchannel 611 penetrates the first header 621 and is connected to the second header 622, wherein the first header 621 is disposed between the second header 622 and the heat exchange body 61, the second microchannel 611 penetrates the first header 621 and is inserted into the second header 622 and is fixed by welding, and the first microchannel 610 is inserted into the first header 621 and is fixed by welding. In other embodiments, the first microchannel 610 may be inserted into the first header 621 after penetrating the second header 622.

The distance between the first header 621 and the second header 622 is R-2R, where R is the maximum cross-sectional dimension of the first header 621 along the direction of the interval between the first header 621 and the second header 622. The cross-sectional shapes of the first header 621 and the second header 622 may be both circular, and R is the diameter of the first header 621 or the diameter of the second header 622. In other embodiments, the cross-sectional shapes of the first header 621 and the second header 622 may be configured to be other shapes, such as an oval shape, a square shape, a rectangle shape, or an irregular shape, and when the cross-sectional shapes of the first header 621 and the second header 622 are non-circular, R is the diameter of a circle circumscribed by the first header 621 or the second header 622.

Therefore, the distance between the first header 621 and the second header 622 is set to be large, so that the first header 621 and the second header 622 can be easily welded to the heat exchange body 61. In addition, the second microchannel 611 located between the first header 621 and the second header 622 does not exchange heat with the first microchannel 610, and by setting the distance between the first header 621 and the second header 622 to be small, the length of the second microchannel 611 located between the first header 621 and the second header 622 can be reduced, and the heat exchange area of the second microchannel 611 can be increased.

In other embodiments, the first header 621 and the second header 622 may be welded together to reduce the distance between the first header 621 and the second header 622.

In addition, the first microchannel 610 may bypass the second header 622 and then connect to the first header 621, for example, the first microchannel 610 is disposed outside the second header 622 and then connects to the first header 621 after bypassing the second header 622. Alternatively, the second microchannel 611 may bypass the first header 621 and then connect to the second header 622.

1.3 dividing the main header into two headers

As shown in fig. 5, the header assembly 62 includes a main header 623 and a flow dividing plate 624, and the flow dividing plate 624 is disposed in the main header 623 and is used for dividing the main header 623 into a first header 621 and a second header 622, i.e., the main header 623 is disposed as the first header 621 and the second header 622 separated by the flow dividing plate 624. At this time, as shown in fig. 5, the first microchannels 610 penetrate the sidewall of the main header 623 and are inserted into the first header 621, and the second microchannels 611 penetrate the sidewall of the main header 623 and the cutoff plate 624 and are inserted into the second header 622. In other embodiments, the second microchannels 611 extend through the sidewall of the header 623 and are inserted into the second header 622, while the first microchannels 610 extend through the sidewall of the header 623 and the cutoff plate 624 and are inserted into the first header 621. In comparison to the manifold assembly 62 shown in fig. 4: in this embodiment, the function of the first header 621 and the function of the second header 622 are simultaneously realized by one header 623, so that the cost and the volume of the header assembly 62 can be reduced.

In other embodiments, the header 623 may be divided into two first headers 621 or two second headers 622 using the cutoff plate 624. At this time, one end of the first microchannel 610 penetrates the sidewall of the main header 623 and is inserted into one of the first headers 621, and the other end of the first microchannel 610 penetrates the sidewall of the main header 623 and is inserted into the other of the first headers 621. One first header 621 of the two first headers 621 is configured to provide a first refrigerant flow to the first micro-channel 610, and the other first header 621 of the two first headers 621 is configured to collect the first refrigerant flow flowing through the first micro-channel 610, where the first micro-channel 610 is a U-shaped flow path.

Alternatively, one end of the second microchannel 611 penetrates the sidewall of the main header 623 and is inserted into one of the second headers 622, and the other end of the second microchannel 611 penetrates the sidewall of the main header 623 and the cutoff plate 624 and is inserted into the other of the second headers 622. One of the two second headers 622 is configured to provide a second refrigerant flow to the second microchannel 611, and the other of the two second headers 622 is configured to collect the second refrigerant flow flowing through the second microchannel 611, where the second microchannel 611 is a U-shaped flow path.

1.4 nesting arrangement of first header and second header

As shown in fig. 6, the diameter of the second header 622 is smaller than that of the first header 621, the first header 621 is sleeved outside the second header 622, and the first microchannel 610 penetrates through the sidewall of the first header 621 and is inserted into the first header 621. The second microchannels 611 extend through the sidewalls of the first header 621 and the second header 622 and are inserted into the second header 622. In other embodiments, the second header 622 may be sleeved outside the first header 621, and the second micro-channels 611 penetrate through the sidewall of the second header 622 and are inserted into the second header 622. The first microchannels 610 extend through the sidewalls of the second header 622 and the first header 621 and are inserted into the first header 621.

In comparison to the manifold assembly 62 shown in fig. 4: the nested arrangement allows for a reduction in the volume of the manifold assembly 62.

In other embodiments, it may be that the two first headers 621 are nested within each other, or that the two second headers 622 are nested within each other. At this time, one end of the first microchannel 610 penetrates the sidewall of the outer first header 621 and is inserted into the outer first header 621. The other end of the first microchannel 610 penetrates the sidewalls of the two first headers 621 and is inserted into the inner first header 621. The outer first collecting pipe 621 is configured to provide a first refrigerant flow to the first micro channel 610, and the inner first collecting pipe 621 is configured to collect the first refrigerant flow flowing through the first micro channel 610; or the inner first collecting pipe 621 is used for providing the first refrigerant flow to the first microchannel 610, and the outer first collecting pipe 621 is used for collecting the first refrigerant flow flowing through the first microchannel 610; the first microchannel 610 is a U-shaped flow path at this time.

Alternatively, one end of the second microchannel 611 penetrates the sidewall of the outer second header 622 and is inserted into the outer second header 622. The other end of the second microchannel 611 penetrates the sidewalls in the two second headers 622 and is inserted into the inner second header 622. The outer second collecting pipe 622 is configured to provide a second refrigerant flow to the second microchannel 611, and the inner second collecting pipe 622 is configured to collect the second refrigerant flow flowing through the second microchannel 611; alternatively, the inner second collecting pipe 622 is used for providing the second refrigerant flow to the second microchannel 611, and the outer second collecting pipe 622 is used for collecting the second refrigerant flow flowing through the second microchannel 611; the second microchannel 611 is a U-shaped flow path at this time.

2. Sleeve type heat exchanger

As shown in fig. 7, the heat exchanger 6 includes a heat exchange body 61, and the heat exchange body 61 includes a first tubular body 614 and a second tubular body 615 which are nested with each other. A plurality of first microchannels 610 are arranged in the first tube 614, a plurality of second microchannels 611 are arranged in the second tube 615, and the plurality of first microchannels 610 and the plurality of second microchannels 611 are the same as the microchannels 612 shown in fig. 2, so that the length of the heat exchange main body 61 is shortened, and the volume of the heat exchanger 6 is further reduced.

The plurality of first microchannels 610 of the first tubular body 614 serve as first heat exchange channels 610 of the heat exchanger 6 and the plurality of second microchannels 611 of the second tubular body 615 serve as second heat exchange channels 611 of the heat exchanger 6. Wherein, the extending direction of first microchannel 610 and the extending direction of second microchannel 611 are parallel to each other, for example, the extending direction of first microchannel 610 is the same as the extending direction of second microchannel 611.

In this embodiment, the first tube 614 is sleeved outside the second tube 615, and the outer surface of the first tube 614 is provided with at least one flat surface 616 to form a heat exchange contact surface of the first tube 614, as shown in fig. 8. Heat dissipation elements or electronic components may be disposed on the planar surface 616 for ease of mounting. In other embodiments, the second tube 615 can be disposed outside the first tube 614.

In the air conditioning system shown in fig. 1, the first refrigerant flow may be a liquid-phase refrigerant flow, and the second refrigerant flow may be a gas-liquid two-phase refrigerant flow. The second refrigerant stream absorbs heat from the first refrigerant stream of the first microchannels 610 during flow along the second microchannels 611 and is further vaporized to further subcool the first refrigerant stream. In other embodiments, the first refrigerant flow and the second refrigerant flow may adopt other arrangements described above.

In contrast to the heat exchanger 6 shown in fig. 2: the heat exchange body 61 has a large cross-sectional area, and pressure loss of the refrigerant flow can be reduced. In addition, the first pipe 614 is sleeved outside the second pipe 615, so that the heat exchange area between the first microchannels 610 and the second microchannels 611 can be increased, and the heat exchange efficiency between the first heat exchange channels 610 and the second heat exchange channels 611 can be increased.

Referring to fig. 4, the heat exchanger 6 further comprises a header assembly 62, the header assembly 62 comprises a first header 621 and a second header 622, the first header 621 is provided with a first header passage, and the second header 622 is provided with a second header passage. The cross-sectional shape of the heat exchanger 6 is I-shaped, for example, the cross-sectional shape of the heat exchanger 6 along the flow direction of the refrigerant flow in the heat exchange body 61 is I-shaped. In other embodiments, the cross-sectional shape of the heat exchanger 6 along the flow direction of the refrigerant flow in the heat exchange body 61 may be L-shaped, U-shaped, G-shaped, or circular.

The first collecting channel is connected to the first microchannels 610 to provide a first refrigerant flow to the plurality of first microchannels 610 through the first collecting channel and/or to collect the first refrigerant flow flowing through the plurality of first microchannels 610. The number of the first collecting pipes 621 is two, and the two first collecting pipes 621 are respectively connected to two ends of the first pipe body 614, so that one of the two first collecting pipes 621 is used for providing a first refrigerant flow to the plurality of first microchannels 610; and the other of the two first headers 621 is used to collect the first refrigerant flow passing through the plurality of first microchannels 610.

The second collecting channel is connected to the second microchannels 611 to provide a second refrigerant flow to the plurality of second microchannels 611 through the second collecting channel and/or to collect the second refrigerant flow flowing through the plurality of second microchannels 611. The number of the second collecting pipes 622 is two, and the two second collecting pipes 622 are respectively connected to two ends of the second pipe 615, so as to provide a second refrigerant flow to the plurality of second microchannels 611 by using one of the two second collecting pipes 622; and the second refrigerant flow passing through the second microchannels 611 is collected by the other of the two second headers 622.

Alternatively, the heat exchange body 61 may include at least two sets of the first and second tubes 614 and 615, the at least two sets of the first and second tubes 614 and 615 being spaced apart from each other in a direction perpendicular to the extending direction. For example, the at least two sets of first and second tubes 614 and 615 may include a first set of first and second tubes 614 and 615 nested within each other, a second set of first and second tubes 614 and 615 nested within each other, the first and second sets of first and second tubes 614 and 615 nested within each other being spaced apart from the second set of first and second tubes 614 and 615 along a direction perpendicular to the extending direction.

The same end of the first tube 614 of the at least two groups of first tubes 614 and the same end of the second tube 615 of the at least two groups of first tubes 615 are connected to the same first header 621, and the same end of the second tube 615 of the at least two groups of first tubes 614 and the same end of the second tube 615 of the at least two groups of second tubes 615 are connected to the same second header 622, so that the cost can be reduced.

The manifold assembly 62 may also be provided in the various manifold arrangements described above, such as the first manifold 621 and the second manifold 622 spaced apart from each other, the manifold 623 and the cutoff 624, or the first manifold 621 and the second manifold 622 nested within each other, as described above. At this time, the first tube 614 with the first micro-channel 610 thereon and the second tube 615 with the second micro-channel 611 thereon can be matched with the above-mentioned header in the manner described above, and are not described herein again.

3. The heat exchanger has a first plate body and a second plate body which are arranged in a stacked manner

As shown in fig. 9, the heat exchanger 6 includes a heat exchange body 61, and the heat exchange body 61 includes a first plate body 631 and a second plate body 632, and the first plate body 631 and the second plate body 632 are stacked on each other.

A plurality of first microchannels 610 are disposed in the first plate 631, a plurality of second microchannels 611 are disposed in the second plate 632, and the plurality of first microchannels 610 and the plurality of second microchannels 611 are the same as the microchannels 612 shown in fig. 2, and are not described herein again. Therefore, the length of the heat exchange body 61 is shortened, and the volume of the heat exchanger 6 is reduced.

The first plurality of microchannels 610 of the first plate body 631 serves as a first heat exchange channel 610 of the heat exchanger 6 and the second plurality of microchannels 611 of the second plate body 632 serves as a second heat exchange channel 611 of the heat exchanger 6. Wherein, the extending direction of first microchannel 610 and the extending direction of second microchannel 611 are parallel to each other, for example, the extending direction of first microchannel 610 is the same as the extending direction of second microchannel 611. Since the first plate body 631 and the second plate body 632 are stacked on each other, the contact area between the first plate body 631 and the second plate body 632 is increased to increase the heat exchange area between the first heat exchange channel 610 and the second heat exchange channel 611, thereby improving the heat exchange efficiency.

In the air conditioning system shown in fig. 1, the first refrigerant flow may be a liquid-phase refrigerant flow, and the second refrigerant flow may be a gas-liquid two-phase refrigerant flow. The second refrigerant stream absorbs heat from the first refrigerant stream of the first microchannels 610 during flow along the second microchannels 611 and is further vaporized to further subcool the first refrigerant stream. In other embodiments, the first refrigerant flow and the second refrigerant flow may adopt other arrangements described above.

In an embodiment, the number of the first plate 631 may be two, and the second plate 632 is sandwiched between the two first plates 631, for example, the first plate 631, the second plate 632, and the first plate 631 are stacked in sequence. The second plate body 632 is clamped between the two first plate bodies 631, so that the second refrigerant flow of the second plate body 632 absorbs heat of the first refrigerant flows of the two first plate bodies 631 at the same time, and the first refrigerant flows of the two first plate bodies 631 are cooled. In addition, a heat dissipation element or an electronic element may be disposed in heat conductive connection with the first plate 631, for example, the heat dissipation element or the electronic element may be disposed on a surface of the first plate 631 away from the second plate 632 for easy installation. In an embodiment, the two first plates 631 may be two independent plates. In other embodiments, the two first plate bodies 631 may also be integrally connected in a U shape, and the first microchannels 610 in the two first plate bodies 631 are in U-shaped communication, so that the inlet and the outlet of the first microchannel 610 are located on the same side of the heat exchange body 61.

In other embodiments, the number of the second plate 632 may be two, and the first plate 631 is sandwiched between the two second plates 632. At this time, a heat dissipation element or an electronic element may be disposed in thermal conductive connection with the second board body 632.

As shown in fig. 10, the heat exchanger 6 further comprises a header pipe assembly 62, the header pipe assembly 62 comprises a first header 621 and a second header 622, the first header 621 is provided with a first header passage, and the second header 622 is provided with a second header passage. The cross-sectional shape of the heat exchanger 6 along the flow direction of the refrigerant flow in the heat exchange body 61 is I-shaped. In other embodiments, the cross-sectional shape of the heat exchanger 6 along the flow direction of the refrigerant flow in the heat exchange body 61 may be L-shaped, U-shaped, G-shaped, or circular.

The first collecting channel is connected to the first microchannels 610 to provide a first refrigerant flow to the plurality of first microchannels 610 through the first collecting channel and/or to collect the first refrigerant flow flowing through the plurality of first microchannels 610. The number of the first collecting pipes 621 is two, and the two first collecting pipes 621 are respectively connected to two ends of the first plate body 631, so as to provide a first refrigerant flow to the plurality of first microchannels 610 by using one of the two first collecting pipes 621; and the other of the two first headers 621 is used to collect the first refrigerant flow passing through the plurality of first microchannels 610.

The second collecting channel is connected to the second microchannels 611 to provide a second refrigerant flow to the plurality of second microchannels 611 through the second collecting channel and/or to collect the second refrigerant flow flowing through the plurality of second microchannels 611. The number of the second collecting pipes 622 is two, and the two second collecting pipes 622 are respectively connected to two ends of the second plate body 632, so as to provide a second refrigerant flow to the plurality of second microchannels 611 by using one of the two second collecting pipes 622; and the second refrigerant flow passing through the second microchannels 611 is collected by the other of the two second headers 622.

Alternatively, the heat exchange body 61 may include at least two sets of the first and second plate bodies 631 and 632 spaced apart from each other in a direction perpendicular to the extending direction. For example, as shown in fig. 10, the heat exchange body 61 includes three sets of first plate bodies 631 and second plate bodies 632, and the three sets of first plate bodies 631 and second plate bodies 632 are arranged at intervals in a direction perpendicular to the extending direction of the first microchannels 610 or the extending direction of the second microchannels 611.

The same end of the first plate 631 of the at least two groups of first plate 631 and the same end of the second plate 632 are connected to the same first collecting pipe 621, the same end of the second plate 632 of the at least two groups of first plate 631 and the second plate 632 are connected to the same second collecting pipe 622, for example, the same end of all the first plates 631 of the heat exchange main body 61 is connected to the same first collecting pipe 621, and the same end of all the second plates 632 of the heat exchange main body 61 is connected to the same second collecting pipe 622, so that the cost is reduced.

In this embodiment, the first header 621 and the second header 622 are disposed at intervals along the extending direction of the heat exchange body 61. The second plate body 632 penetrates through the first header 621 and is inserted into the second header 622, wherein the first header 621 is disposed between the second header 622 and the heat exchange main body 61, the second plate body 632 penetrates through the first header 621 and is inserted into the second header 622 and welded and fixed, and the first plate body 631 is inserted into the first header 621 and welded and fixed. In other embodiments, the first plate 631 may penetrate the second header 622 and then be connected to the first header 621.

The distance between the first header 621 and the second header 622 is R-2R, where R is the maximum cross-sectional dimension of the first header 621 along the direction of the interval between the first header 621 and the second header 622. The cross-sectional shapes of the first header 621 and the second header 622 may be both circular, and R is the diameter of the first header 621 or the diameter of the second header 622. Further, as described above, when the cross-sectional shapes of the first header 621 and the second header 622 are non-circular, R is the diameter of the circle circumscribed by the first header 621 or the second header 622.

The manifold assembly 62 may also be provided in the various manifold arrangements described above, such as the manifold 623 and cutoff 624 arrangement described above, or the first and second manifolds 621 and 622 nested within one another. At this time, the first plate 631 with the first micro-channels 610 thereon and the second plate 633 with the second micro-channels 611 thereon can be matched with the above-mentioned header in the manner described above, and will not be described again.

4. Auxiliary heat exchanger of air conditioner outdoor unit

As shown in fig. 11, the outdoor unit of the air conditioner includes a base plate 41, a casing 42, and an auxiliary heat exchanger 43, and the auxiliary heat exchanger 43 is the heat exchanger 6 disclosed in the above embodiment.

The housing 42 is disposed on the bottom plate 41 such that the housing 42 and the bottom plate 41 form a mounting chamber 421, and the auxiliary heat exchanger 43 is disposed in the mounting chamber 421. The auxiliary heat exchanger 43 includes a heat exchange body 61 and a header assembly 62, the header assembly 62 is used for providing a refrigerant flow to the heat exchange body 61, and the heat exchange body 61 is used for heating the installation cavity 421.

The heat exchange main body 61 includes a first heat exchange passage 610 and a second heat exchange passage 611, the header assembly 62 includes a first header 621 and a second header 622, the first header 621 is provided with a first header passage, and the second header 622 is provided with a second header passage. The first collecting channel is connected to the first heat exchanging channel 610 to provide the first refrigerant flow to the first heat exchanging channel 610 through the first collecting channel and/or to collect the first refrigerant flow flowing through the first heat exchanging channel 610. The second collecting channel is connected to the second heat exchanging channel 611 to provide the second refrigerant flow to the second heat exchanging channel 611 through the second collecting channel and/or to collect the second refrigerant flow flowing through the second heat exchanging channel 611.

The number of the first collecting pipes 621 is two, and the two first collecting pipes 621 are respectively connected to two ends of the first heat exchange passage 610, so that one of the two first collecting pipes 621 is used for providing a first refrigerant flow to the first heat exchange passage 610; and the other of the two first headers 621 is used to collect the first refrigerant flow passing through the first heat exchange channel 610. The number of the second collecting pipes 622 is two, and the two second collecting pipes 622 are respectively connected to two ends of the second heat exchange channel 611, so that one of the two second collecting pipes 622 is used for providing a second refrigerant flow to the second heat exchange channel 611; and the other of the two second headers 622 is used to collect the second refrigerant flow passing through the second heat exchanging channel 611.

The second refrigerant flow is a gas-liquid two-phase refrigerant flow, the first refrigerant flow is a liquid-phase refrigerant flow, and the second refrigerant flow absorbs heat from the first refrigerant flow in the flowing process along the second heat exchange channel 611 and is further gasified, so that the first refrigerant flow is further supercooled. For example, the first refrigerant flow is a medium-pressure medium-temperature refrigerant flow, and the temperature can be 40 °; the second refrigerant flow is a low-pressure and low-temperature refrigerant flow, the temperature of the second refrigerant flow can be 10 degrees, and because the temperature of the first refrigerant flow and the temperature of the second refrigerant flow are both different from the ambient temperature, the heat exchange main body 61 emits heat outwards to realize the heating installation cavity 421.

The outdoor unit is installed outdoors, and in a case where an ambient temperature is low (for example, the ambient temperature is-20 °), condensed water discharged from the outdoor unit is frozen, which causes a chassis 41 and a casing 42 of the outdoor unit to be frozen. Therefore, the auxiliary heat exchanger 43 is disposed in the installation chamber 421 to heat the installation chamber 421 through the heat exchange body 61 to prevent the bottom plate 41 and the housing 42 from being frozen or frosted. In addition, the auxiliary heat exchanger 43 does not need to be powered, so that potential safety hazards of electric leakage are avoided, and the safety performance of the air conditioner outdoor unit is improved.

In an embodiment, the auxiliary heat exchanger 43 is mounted on the base plate 41, and the auxiliary heat exchanger 43 may be mounted on the base plate 41 in a horizontal plane due to the small volume of the auxiliary heat exchanger 43, or the auxiliary heat exchanger 43 may be mounted on the base plate 41 in a direction perpendicular to the horizontal plane.

As shown in fig. 12, the base plate 41 is provided with a drain hole 411, and the drain hole 411 is used for draining water. The auxiliary heat exchanger 43 is installed near the drain hole 411, for example, the auxiliary heat exchanger 43 is installed on the drain hole 411 to heat the chassis 41 near the drain hole 411 to prevent the condensed water from freezing and blocking the drain hole 411, thereby affecting the drainage function of the drain hole 411.

The outdoor unit of the air conditioner further includes a mounting bracket 412, the mounting bracket 412 is provided with a supporting portion and a fixing portion, the supporting portion and the fixing portion are stepped, the auxiliary heat exchanger 43 is mounted on the supporting portion, and the fixing portion is fixed on the base plate 41, so that the auxiliary heat exchanger 43 is disposed on the drain hole 411, the auxiliary heat exchanger 43 is prevented from blocking the drain of the drain hole 411, and the mounting is easy and the cost is low. In other embodiments, the auxiliary heat exchanger 43 may be disposed on the chassis 41 by other fixing methods, such as welding or fixing methods such as sheet metal.

In an embodiment, the outdoor unit of the air conditioner further includes a main heat exchanger, and the main heat exchanger may be the outdoor heat exchanger 4 disclosed in the above embodiment. The main heat exchanger is disposed in the installation cavity 421, the main heat exchanger is frosted or frozen when the ambient temperature is low, and the auxiliary heat exchanger 43 is installed near the main heat exchanger, for example, the auxiliary heat exchanger 43 is installed at the bottom of the main heat exchanger or the housing 42 is near the main heat exchanger. Therefore, the main heat exchanger can be prevented from frosting or icing under the condition of low ambient temperature, so that the heat exchange efficiency of the main heat exchanger is improved.

5. Control method for heating of auxiliary heat exchanger

As shown in fig. 13, the air conditioning system 1 includes a compressor 2, a four-way valve 3, an outdoor heat exchanger 4, an indoor heat exchanger 5, an auxiliary heat exchanger 43, a first expansion valve 11, a second expansion valve 12, a third expansion valve 13, a first temperature detection device 14, and a second temperature detection device 15, the compressor 2 provides a refrigerant flow of a circulating flow between the outdoor heat exchanger 4 and the indoor heat exchanger 5 through the four-way valve 3, and the third expansion valve 13 is disposed between the outdoor heat exchanger 4 and the indoor heat exchanger 5. The outdoor heat exchanger 4 may be a main heat exchanger of the air conditioner outdoor unit in fig. 12, and the auxiliary heat exchanger 43 may be installed near the drain hole 411 or the main heat exchanger.

An inlet of the first heat exchange passage 610 of the auxiliary heat exchanger 43 is connected to the compressor 2 through the first expansion valve 11, and an outlet of the first heat exchange passage 610 is connected between the outdoor heat exchanger 4 and the indoor heat exchanger 5. An inlet of the first heat exchange passage 610 is connected to the discharge port 21 of the compressor 2 through the first expansion valve 11 via the first header 621, and an outlet of the first heat exchange passage 610 is connected between the outdoor heat exchanger 4 and the indoor heat exchanger 5 through the first header 621.

An inlet of the second heat exchange passage 611 is connected between the outdoor heat exchanger 4 and the indoor heat exchanger 5 through the second expansion valve 12, and an outlet of the second heat exchange passage 611 is connected to the compressor 2. Wherein, the inlet of the second heat exchange channel 611 is connected between the outdoor heat exchanger 4 and the indoor heat exchanger 5, i.e. the outlet of the first heat exchange channel 610, through the second expansion valve 12 via the second collecting pipe 622; the outlet of the second heat exchange channel 611 is connected to the suction port 22 of the compressor 2. In other embodiments, the compressor 2 may be provided with an injection port (not shown), and the outlet of the second heat exchanging channel 611 may be connected to the injection port of the compressor 2, so that the gasified second refrigerant flow passes through the injection port of the compressor 2 to perform enhanced vapor injection on the compressor 2.

The first temperature detecting device 14 may be disposed near the outdoor heat exchanger 4 for detecting the ambient temperature T of the air conditioning system 1. A second temperature detecting means 15 may be provided at the outlet of the first heat exchanging passage 610 for detecting the outlet temperature T1 of the first heat exchanging passage 610, for example, the second temperature detecting means 15 is provided at the first header 621 connected to the outlet of the first heat exchanging passage 610 to detect the outlet temperature T1 of the first heat exchanging passage 610. The first temperature detection device 14 and the second temperature detection device 15 may be thermometers or temperature sensors.

As shown in fig. 14, the control method is applied to the air conditioning system shown in fig. 13, and includes the steps of:

step S141: in response to the heating mode, the ambient temperature T and the outlet temperature T1 of the first heat exchange passage are detected.

The air conditioning system 1 is in the heating mode, and the ambient temperature T and the outlet temperature T1 of the first heat exchange passage 610 are detected in response to the heating mode. For example, the air conditioning system 1 detects the ambient temperature T of the air conditioning system 1 through the first temperature detecting device 14 and detects the outlet temperature T1 of the first heat exchanging channel 610 through the second temperature detecting device 15 in response to the heating mode.

The air conditioning system 1 is preset with a first preset temperature t1, a second preset temperature t2 and a third preset temperature t3, wherein the third preset temperature t3 is greater than the first preset temperature t 1.

Step S142: the ambient temperature T and the outlet temperature T1 are compared with a first preset temperature T1 and a second preset temperature T2, respectively.

The air conditioning system 1 detects the ambient temperature T and the outlet temperature T1 of the first heat exchange path 610, and compares the ambient temperature T and the outlet temperature T1 of the first heat exchange path 610 with the first preset temperature T1 and the second preset temperature T2, respectively. That is, the air conditioning system 1 compares the ambient temperature T with the first preset temperature T1, and compares the outlet temperature T1 of the first heat exchanging channel 610 with the second preset temperature T2.

Step S143: in response to the ambient temperature T being less than the first preset temperature T1 and the outlet temperature T1 of the first heat exchange passage 610 being less than the second preset temperature T2, the opening degree of the first expansion valve 11 is increased.

The air conditioning system 1 opens the opening degree of the first expansion valve 11 in response to the ambient temperature T being less than the first preset temperature T1 and the outlet temperature T1 of the first heat exchanging channel 610 being less than the second preset temperature T2.

The air conditioning system 1 responds to the ambient temperature T being less than the first preset temperature T1, that is, the ambient temperature T of the air conditioning system 1 is low, for example, the first preset temperature T1 is-5 °, the ambient temperature T of the air conditioning system 1 is less than-5 °, and frosting or icing of the outdoor unit of the air conditioner may occur. The air conditioning system 1 is further responsive to the outlet temperature T1 of the first heat exchanging channel 610 being less than the second preset temperature T2, i.e. the temperature of the first refrigerant flowing through the first heat exchanging channel 610 is less than the second preset temperature T2, for example, the second preset temperature T2 is 10 °. At this time, the air conditioning system 1 increases the opening degree of the first expansion valve 11 to increase the flow rate of the first refrigerant flow, increase the outlet temperature T1 of the first heat exchange channel 610, and increase the heat dissipation capacity of the first heat exchange channel 610, so that the auxiliary heat exchanger 43 heats, and frost or ice of the air conditioning outdoor unit is removed, thereby preventing the drain hole 411 of the air conditioning outdoor unit from being frozen, and the auxiliary heat exchanger 43 does not need to be powered on, thereby avoiding potential safety hazards of electric leakage.

Alternatively, the air conditioning system 1 opens the second expansion valve 12, and the second refrigerant flow absorbs heat from the first refrigerant flow of the first heat exchange channel 610 during the flowing process along the second heat exchange channel 611, and is further gasified, so that the first refrigerant flow is further supercooled.

In one embodiment, the air conditioning system 1 is in response to a non-heating mode, for example, the air conditioning system 1 is in a cooling mode, i.e., the ambient temperature T of the air conditioning system 1 is high, so that the outdoor unit of the air conditioner does not frost or ice. The air conditioning system 1 closes the first expansion valve 11 and the first heat exchange passage 610 is closed; the opening degree of the second expansion valve 12 is reduced to reduce the flow rate of the second refrigerant flowing through the second heat exchange channel 611.

In addition, the second refrigerant flow flowing through the second heat exchanging channel 611 may exchange heat with the environment of the air conditioning system 1, for example, the second refrigerant flow absorbs heat from the environment of the air conditioning system 1, so as to further gasify the second refrigerant flow. The gasified second refrigerant flow passes through the injection port or the suction port 22 of the compressor 2 to perform enhanced vapor injection on the compressor 2, thereby improving the heating capacity of the air conditioning system 1.

As shown in fig. 15, step S142 further includes the steps of:

step S151: the ambient temperature T is compared with a third preset temperature T3.

The air conditioning system 1 compares the ambient temperature T with a third preset temperature T3 in response to the ambient temperature T being greater than the first preset temperature T1, wherein the third preset temperature T3 is greater than the first preset temperature T1.

Step S152: in response to the ambient temperature T being greater than or equal to the third preset temperature T3, the opening degree of the first expansion valve 11 is closed.

The air conditioning system 1 is in the heating mode, and in response to the ambient temperature T being greater than or equal to the third preset temperature T3, the opening degree of the first expansion valve 11 is decreased to decrease the flow rate of the first refrigerant flowing through the first heat exchange channel 610, so as to decrease the heat dissipation capacity of the first heat exchange channel 610.

As shown in fig. 16, step S142 further includes the steps of:

step S161: the outlet temperature T1 is compared with a fourth preset temperature T4, the fourth preset temperature T4 being greater than the second preset temperature T2.

The air conditioning system 1 is preset with a fourth preset temperature t4, and the fourth preset temperature t4 is greater than the second preset temperature t 2; the air conditioning system 1 compares the outlet temperature T1 with a fourth preset temperature T4.

Step S162: in response to the outlet temperature T1 being greater than or equal to the fourth preset temperature T4, the opening degree of the first expansion valve 11 is closed down and the opening degree of the second expansion valve 12 is opened up.

In response to the outlet temperature T1 being greater than or equal to the fourth preset temperature T4, that is, the temperature of the first refrigerant flowing through the first heat exchange channel 610 is too high, the air conditioning system 1 turns the opening degree of the first expansion valve 11 small and turns the opening degree of the second expansion valve 12 large in order to achieve supercooling of the first refrigerant. Therefore, the air conditioning system 1 reduces the flow rate of the first refrigerant flowing through the first heat exchange channel 610 to reduce the heat dissipation capacity of the first heat exchange channel 610; the flow rate of the second refrigerant flowing through the second heat exchanging channel 611 is increased, so that the second refrigerant absorbs heat from the first refrigerant, and the first refrigerant is further supercooled.

The above description is only for the purpose of illustrating embodiments of the present application and is not intended to limit the scope of the present application, and all modifications of equivalent structures and equivalent processes, which are made by the contents of the specification and the drawings of the present application or are directly or indirectly applied to other related technical fields, are also included in the scope of the present application.

Claims (11)

1. An outdoor unit of an air conditioner, comprising:

a chassis;

the shell is arranged on the chassis and forms an installation cavity with the chassis;

the auxiliary heat exchanger is arranged in the installation cavity and comprises a heat exchange main body and a collecting pipe assembly, the collecting pipe assembly is used for providing refrigerant flow for the heat exchange main body, and the heat exchange main body is used for heating the installation cavity.

2. The outdoor unit of claim 1, wherein the auxiliary heat exchanger is installed on the base pan.

3. The outdoor unit of claim 1 or 2, wherein the base plate is provided with a drainage hole, and the auxiliary heat exchanger is installed adjacent to the drainage hole.

4. The outdoor unit of claim 1, further comprising a main heat exchanger disposed in the installation chamber, wherein the auxiliary heat exchanger is installed adjacent to the main heat exchanger.

5. The outdoor unit of claim 1, wherein the heat exchange body comprises a first heat exchange passage and a second heat exchange passage;

the collecting pipe assembly comprises a first collecting pipe and a second collecting pipe, wherein the first collecting pipe is provided with a first collecting channel, the first collecting channel is used for providing a first refrigerant flow for the first heat exchange channel and/or collecting the first refrigerant flow flowing through the first heat exchange channel, the second collecting pipe is provided with a second collecting channel, and the second collecting channel is used for providing a second refrigerant flow for the second heat exchange channel and/or collecting the second refrigerant flow flowing through the second heat exchange channel, so that heat exchange is carried out between the first refrigerant flow flowing through the first heat exchange channel and the second refrigerant flow flowing through the second heat exchange channel.

6. The outdoor unit of claim 5, wherein the first heat exchange channel is a plurality of first micro channels disposed in the heat exchange body, and the second heat exchange channel is a plurality of second micro channels disposed in the heat exchange body.

7. The outdoor unit of claim 6, wherein the heat exchange body comprises at least:

the first micro-channels are arranged in the first plate body;

the second plate body and the first plate body are arranged in a stacked mode, and the second micro channels are arranged in the second plate body.

8. The outdoor unit of claim 7, wherein the number of the first plate bodies is two, and the second plate bodies are interposed between the two first plate bodies, or the number of the second plate bodies is two, and the first plate bodies are interposed between the two second plate bodies.

9. The outdoor unit of claim 5, wherein the second refrigerant stream absorbs heat from the first refrigerant stream during a flow along the second heat exchange path to subcool the first refrigerant stream, or the first refrigerant stream absorbs heat from the second refrigerant stream during a flow along the first heat exchange path to subcool the second refrigerant stream.

10. An air conditioning system, comprising a compressor, a four-way valve, an indoor heat exchanger, an auxiliary heat exchanger and the outdoor unit of any one of claims 1 to 9, wherein the auxiliary heat exchanger is disposed in a mounting chamber of the outdoor unit for heating the mounting chamber, and the compressor provides a refrigerant flow circulating between the outdoor unit and the indoor heat exchanger through the four-way valve.

11. The air conditioning system of claim 10, wherein the auxiliary heat exchanger is an economizer.

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