Air treatment equipment and control method

Abstract

An air treatment device and a control method. The air handling equipment includes a connected compressor, a four-way valve, an indoor heat exchanger, a refrigerant radiator, an outdoor heat exchanger, a first throttle valve and a second throttle valve. The first throttle valve is located between the indoor heat exchanger and the refrigerant radiator, and the second throttle valve is located between the outdoor heat exchanger and the refrigerant radiator. The actual operating frequency of the compressor is P1, the set frequency of the compressor is P, the maximum flow of the first throttle valve is Q, and when the actual flow of the first throttle valve varies between 0 and Q, the pressure difference across the first throttle valve varies between 0 and D. The actual opening of the second throttle valve is k1, the maximum opening of the second throttle valve is k, and in the cooling mode, k2≤k1<k, k2 is the set opening of the second throttle valve; in the cooling mode, based on P1 being 0.1P~0.4P, the pressure difference across the first throttle valve is 0.08D~0.48D, and the flow of the first throttle valve is 0.05Q~0.3Q, which can avoid the compression ratio and △T being too low when the compressor is running.

Description

Technical Field

[0001] This article relates to electrical equipment technology, particularly an air handling device and a control method. Background Art

[0002] In existing air conditioners, when the compressor is operating at a medium or low frequency (for example: P1 is 0.1P~0.4P, P1 is the actual operating frequency of the compressor, and P is the maximum operating frequency of the compressor), due to the insufficient throttling effect of the overall refrigeration system, the compression ratio (the ratio of the compressor exhaust absolute pressure to the suction absolute pressure) and ΔT (the difference between the bottom temperature of the compressor and the middle temperature of the outdoor heat exchanger) of the compressor will be too low during operation, and the requirements for compressor operation reliability cannot be met. Summary of the Invention

[0003] The present application provides an air handling device that can better meet the requirements of compressor operation reliability.

[0004] The present application also provides a method for controlling an air treatment device.

[0005] The air treatment equipment provided in the present application includes a connected compressor, a four-way valve, an indoor heat exchanger, a refrigerant radiator, an outdoor heat exchanger, a first throttle valve and a second throttle valve, wherein the first throttle valve is located between the indoor heat exchanger and the refrigerant radiator, and the second throttle valve is located between the outdoor heat exchanger and the refrigerant radiator; wherein the actual operating frequency of the compressor is P1, the set frequency of the compressor is P, the maximum flow rate of the first throttle valve is Q, and when the actual flow rate of the first throttle valve varies between 0 and Q, the pressure difference at both ends of the first throttle valve varies between 0 and D, the actual opening of the second throttle valve is k1, the maximum opening of the second throttle valve is k, and in the cooling mode, k2≤k1<k, k2 is the set opening of the second throttle valve; in the cooling mode, based on P1 being 0.1P~0.4P, the pressure difference at both ends of the first throttle valve is 0.08D~0.48D, and the flow rate of the first throttle valve is 0.05Q~0.3Q.

[0006] In some exemplary embodiments, in cooling mode, based on P1 being 0.4P to 0.7P, the pressure difference across the first throttle valve is 0.48D to 0.83D, and the flow rate of the first throttle valve is 0.3Q to 0.48Q.

[0007] In some exemplary embodiments, in cooling mode, based on P1 being 0.7P to 0.9P, the pressure difference across the first throttle valve is 0.83D to 0.87D, and the flow rate of the first throttle valve is 0.48Q to 0.94Q.

[0008] In some exemplary embodiments, in the cooling mode, based on P1 being 0.9P~P, the pressure difference across the first throttle valve is 0.87D~D, and the flow rate of the first throttle valve is 0.94Q~Q.

[0009] In some exemplary embodiments, in cooling mode, based on P1 being 0.1P~0.4P, the pressure difference across the first throttle valve is 0.2MPa~1.1MPa, and the flow rate of the first throttle valve is 11L / min~65L / min; in cooling mode, based on P1 being 0.4P~0.7P, the pressure difference across the first throttle valve is 1.1MPa~1.9MPa, and the flow rate of the first throttle valve is 65L / min~103L / min; in cooling mode, based on P1 being 0.7P~0.9P, the pressure difference across the first throttle valve is 1.9MPa~2.0MPa, and the flow rate of the first throttle valve is 103L / min~202L / min; in cooling mode, based on P1 being 0.9P~P, the pressure difference across the first throttle valve is 2.0MPa~2.3MPa, and the flow rate of the first throttle valve is 202L / min~215L / min.

[0010] In some exemplary embodiments, based on P1 being 0.1P to 0.4P, the slope of the flow rate of the first throttle valve changing with the pressure difference at both ends of the first throttle valve is g1; based on P1 being 0.4P to 0.7P, the slope of the flow rate of the first throttle valve changing with the pressure difference at both ends of the first throttle valve is g2, g2<g1; based on P1 being 0.7P to 0.9P, the slope of the flow rate of the first throttle valve changing with the pressure difference at both ends of the first throttle valve is g3, g3>g1; based on P1 being 0.9P to P, the slope of the flow rate of the first throttle valve changing with the pressure difference at both ends of the first throttle valve is g4, g4<g1, g4<g2.

[0011] In some exemplary embodiments, the actual opening of the first throttle valve is q1, and in cooling mode, q1 ≤ k1. In some exemplary embodiments, both the first throttle valve and the second throttle valve are electronic expansion valves; the actual opening of the first throttle valve is q1; in cooling mode, based on P1 being 0.1P to 0.4P, q1 and / or k1 are adjusted to adjust the pressure differential across the first throttle valve to 0.08D to 0.48D, and the flow rate of the first throttle valve to 0.05Q to 0.3Q.

[0012] In some exemplary embodiments, the first throttle valve is a variable throttle valve, and the second throttle valve is an electronic expansion valve. The variable throttle valve includes a unidirectional throttle passage and a unidirectional second passage. In cooling mode, the throttle passage is open, and in heating mode, the second passage is open. The throttle passage includes a valve seat, a valve core, and a return spring used in conjunction with each other.

[0013] In the cooling mode, based on P1 being 0.1P to 0.4P, the pressure difference across the first throttle valve is 0.08D to 0.48D, and under the action of the return spring, the flow rate of the first throttle valve is 0.05Q to 0.3Q.

[0014] In some exemplary embodiments, the maximum opening of the first throttle valve is q, the actual opening of the first throttle valve is q1, and in the heating mode, q1=q, and k1<k.

[0015] The control method of the air handling equipment provided in this application includes:

[0016] In cooling mode, obtain P1;

[0017] Based on P1 being 0.1P-0.4P, q1 and / or k1 are adjusted so that the pressure difference across the first throttle valve is adjusted to 0.08D-0.48D, and the flow rate of the first throttle valve is adjusted to 0.05Q-0.3Q.

[0018] In some exemplary embodiments, the control method further includes:

[0019] Based on P1 being 0.4P-0.7P, q1 and / or k1 are adjusted so that the pressure difference across the first throttle valve is adjusted to 0.48D-0.83D, and the flow rate of the first throttle valve is adjusted to 0.3Q-0.48Q;

[0020] Based on P1 being 0.7P-0.9P, q1 and / or k1 are adjusted so that the pressure difference across the first throttle valve is adjusted to 0.83D-0.87D and the flow rate of the first throttle valve is adjusted to 0.48Q-0.94Q;

[0021] Based on P1 being 0.9P~P, q1 and / or k1 are adjusted to adjust the pressure difference across the first throttle valve to 0.87D~D, and the flow rate of the first throttle valve to 0.94Q~Q.

[0022] Compared with the related art, the air handling equipment provided in the present application, in the cooling mode, the refrigerant supplied by the compressor is cooled in the outdoor heat exchanger to become a high-pressure, medium-temperature saturated or supercooled liquid, and then enters the refrigerant radiator after throttling and reducing the pressure through the second throttle valve to dissipate heat for the electronic control device. By setting k2≤k1<k, the refrigerant radiator is prevented from generating condensed water, thereby ensuring the stability and reliability of the operation of the electronic control device; moreover, in the cooling mode, when P1 is 0.1P~0.4P, the pressure difference across the first throttle valve is 0.08D~0.48D, and the flow rate of the first throttle valve is 0.05Q~0.3Q, which can avoid the compression ratio and △T of the compressor being too low during operation, and can effectively ensure the operating reliability of the compressor.

[0023] Other features and advantages of the present application will be described in the following description, and in part will become apparent from the description, or will be understood by practicing the present application. Other advantages of the present application can be realized and obtained by the solutions described in the description and the drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] The accompanying drawings are used to provide an understanding of the technical solution of the present application and constitute a part of the specification. Together with the embodiments of the present application, they are used to explain the technical solution of the present application and do not constitute a limitation on the technical solution of the present application.

[0025] Figure 1 A schematic diagram of the structure of an air treatment device provided in some embodiments of the present application;

[0026] Figure 2 A schematic structural diagram of an air treatment device provided in some other embodiments of the present application;

[0027] Figure 3 for Figure 2 Schematic diagram of the structure of the variable throttle valve;

[0028] Figure 4 for Figure 3 Flow-pressure differential diagram of the variable throttle valve shown;

[0029] Figure 5 A flow chart of a control method provided for some embodiments of the present application;

[0030] Figure 6 Flowchart of control methods provided for other embodiments of the present application;

[0031] Figure 7 A flow chart of a control method provided for some further embodiments of the present application.

[0032] The corresponding relationship between the reference numerals and component names is as follows:

[0033] 100 compressor, 200 four-way valve, 300 indoor heat exchanger, 400 refrigerant radiator, 500 outdoor heat exchanger, 600 first throttle valve, 610 throttle passage, 611 valve seat, 612 valve core, 613 return spring, 620 second passage, 700 second throttle valve. DETAILED DESCRIPTION

[0034] This application describes multiple embodiments, but this description is exemplary rather than restrictive, and it will be apparent to those skilled in the art that there may be more embodiments and implementations within the scope of the embodiments described herein. Although many possible feature combinations are shown in the drawings and discussed in the detailed description, many other combinations of the disclosed features are also possible. Unless specifically limited, any feature or element of any embodiment may be used in combination with any other feature or element in any other embodiment, or may replace any other feature or element in any other embodiment.

[0035] This application includes and contemplates combinations of features and elements known to those of ordinary skill in the art. The embodiments, features, and elements disclosed in this application may also be combined with any conventional features or elements to form a unique inventive solution defined by the claims. Any features or elements of any embodiment may also be combined with features or elements from other inventive solutions to form another unique inventive solution defined by the claims. Therefore, it should be understood that any feature shown and / or discussed in this application may be implemented individually or in any appropriate combination. Therefore, except for the limitations made according to the appended claims and their equivalents, the embodiments are not subject to other limitations. In addition, various modifications and changes may be made within the scope of protection of the appended claims.

[0036] In addition, when describing representative embodiments, the specification may have presented the method and / or process as a specific sequence of steps. However, to the extent that the method or process does not rely on the specific order of the steps described herein, the method or process should not be limited to the steps in the specific order described. As will be understood by those skilled in the art, other orders of steps are also possible. Therefore, the specific order of the steps set forth in the specification should not be interpreted as a limitation to the claims. In addition, the claims for the method and / or process should not be limited to performing their steps in the order written, and those skilled in the art can readily understand that these orders can be changed and still remain within the spirit and scope of the embodiments of the present application.

[0037] The air handling equipment provided by this application, such as Figure 1 and Figure 2As shown, it includes a connected compressor 100, a four-way valve 200, an indoor heat exchanger 300, a refrigerant radiator 400, an outdoor heat exchanger 500, a first throttle valve 600 and a second throttle valve 700. The first throttle valve 600 is located between the indoor heat exchanger 300 and the refrigerant radiator 400, and the second throttle valve 700 is located between the outdoor heat exchanger 500 and the refrigerant radiator 400, that is, the outdoor heat exchanger 500, the second throttle valve 700, the refrigerant radiator 400, the first throttle valve 600 and the indoor heat exchanger 300 are connected in sequence, and the four-way valve 200 connects the compressor 100, the indoor heat exchanger 300 and the outdoor heat exchanger 500. Among them, the actual operating frequency of the compressor 100 is P1, the set frequency of the compressor 100 (such as the maximum operating frequency) is P, the maximum flow rate of the first throttle valve 600 (such as the flow rate when the first throttle valve is fully opened) is Q, and when the actual flow rate of the first throttle valve varies between 0 and Q, the pressure difference at both ends of the first throttle valve varies between 0 and D. The actual opening of the second throttle valve 700 is k1, the maximum opening of the second throttle valve 700 is k, and in the cooling mode, k2≤k1<k, k2 is the set opening of the second throttle valve 700; in the cooling mode, based on P1 being 0.1P~0.4P, the pressure difference at both ends of the first throttle valve 600 is 0.08D~0.48D, and the flow rate of the first throttle valve 600 is 0.05Q~0.3Q. In cooling mode, when k1 = k2, the refrigerant passing through the refrigerant radiator 400 can dissipate heat from the electronic control components, and the refrigerant radiator 400 does not produce condensed water. k2 can be a preset fixed value or determined based on the temperature and humidity of the environment in which the refrigerant radiator 400 is located. The electronic control components are coupled to the refrigerant radiator 400.

[0038] In the air handling equipment, in the cooling mode, the refrigerant supplied by the compressor 100 is cooled in the outdoor heat exchanger 500 to become a high-pressure, medium-temperature saturated or supercooled liquid, and then enters the refrigerant radiator 400 after throttling and reducing the pressure through the second throttle valve 700 to dissipate heat for the electronic control components. By setting k2≤k1<k, k1 is not less than the set opening k2 of the second throttle valve 700, so as to avoid the generation of condensed water in the refrigerant radiator 400 and ensure the stability and reliability of the operation of the electronic control components; moreover, in the cooling mode, when P1 is 0.1P~0.4P, the pressure difference at both ends of the first throttle valve 600 is 0.08D~0.48D, and the flow rate of the first throttle valve 600 is 0.05Q~0.3Q, so as to avoid the compression ratio and △T of the compressor 100 being too low during operation, and effectively ensure the operating reliability of the compressor 100.

[0039] In some examples, the actual opening of the first throttle valve 600 is q1, and the actual opening of the second throttle valve 700 is k1. In the cooling mode, q1≤k1. In this way, when the refrigerant flows through the second throttle valve 700, the refrigerant radiator 400 and the first throttle valve 600 in sequence during the cooling process, the refrigerant radiator 400 is cooled by the initial throttling and pressure reduction through the second throttle valve 700, and the secondary throttling through the first throttle valve 600 is also the main throttling to reduce the pressure to a low-temperature and low-pressure saturated state for use in the evaporator. Then the refrigerant enters the indoor heat exchanger 300 for evaporation and heat absorption to become a low-pressure and low-temperature gas. Finally, the refrigerant returns to the compressor 100.

[0040] In some examples, based on P1 being 0.1P to 0.4P, the pressure difference across the first throttle valve is 0.2MPa to 1.1MPa, and the flow rate of the first throttle valve is 11L / min to 65L / min, which can meet the product capacity and energy efficiency requirements.

[0041] In some examples, in cooling mode, based on P1 being 0.4P to 0.7P, the pressure differential across the first throttle valve is 0.48D to 0.83D, and the flow rate of the first throttle valve is 0.3Q to 0.48Q. In some examples, in cooling mode, based on P1 being 0.4P to 0.7P, the flow rate of the first throttle valve 600 is 65L / min to 103L / min, and the pressure differential across the first throttle valve 600 is 1.1MPa to 1.9MPa.

[0042] In the cooling mode, when P1 is 0.4P to 0.7P, the flow rate of the first throttle valve 600 and the pressure difference at both ends are within the above range, which can meet the requirements of the Chinese standard GB 21455 for product capacity and energy efficiency.

[0043] In some examples, in cooling mode, based on P1 being 0.7P to 0.9P, the pressure differential across the first throttle valve is 0.83D to 0.87D, and the flow rate of the first throttle valve is 0.48Q to 0.94Q. In some examples, in cooling mode, based on P1 being 0.7P to 0.9P, the flow rate of the first throttle valve 600 is 103L / min to 202L / min, and the pressure differential across the first throttle valve 600 is 1.9MPa to 2.0MPa.

[0044] In the cooling mode, when P1 is 0.7P to 0.9P, the flow rate of the first throttle valve 600 and the pressure difference at both ends are within the above range, which can meet the user's requirements for cooling capacity output in the actual usage mode.

[0045] In some examples, in cooling mode, based on P1 being 0.9P to P, the pressure differential across the first throttle valve is 0.87D to D, and the flow rate of the first throttle valve is 0.94Q to Q. In some examples, in cooling mode, based on P1 being 0.9P to P, the flow rate of the first throttle valve 600 is 202 L / min to 215 L / min, and the pressure differential across the first throttle valve 600 is 2.0 MPa to 2.3 MPa.

[0046] In the cooling mode, when P1 is 0.9P~P, the flow rate of the first throttle valve 600 and the pressure difference at both ends are within the above range, which can ensure the reliability requirements of the extreme exhaust temperature of the compressor 100 when the product is operating under extremely harsh environmental conditions.

[0047] In some examples, when the pressure difference across the first throttle valve exceeds D, the flow rate of the first throttle valve is maintained at Q, and the first throttle valve can maintain a maximum opening.

[0048] In some examples, in cooling mode, based on P1 being 0.1P to 0.4P, the slope of the flow rate of the first throttle valve changing with the pressure difference at both ends of the first throttle valve is g1; based on P1 being 0.4P to 0.7P, the slope of the flow rate of the first throttle valve changing with the pressure difference at both ends of the first throttle valve is g2, and g2 < g1; based on P1 being 0.7P to 0.9P, the slope of the flow rate of the first throttle valve changing with the pressure difference at both ends of the first throttle valve is g3, and g3 > g1; based on P1 being 0.9P to P, the slope of the flow rate of the first throttle valve changing with the pressure difference at both ends of the first throttle valve is g4, and g4 < g1, and g4 < g2. The slope of the flow rate of the first throttle valve as it changes with the pressure differential across the first throttle valve refers to the slope of the flow rate of the first throttle valve as it changes with the pressure differential across the first throttle valve, obtained when the pressure differential across the first throttle valve is the X-axis and the flow rate of the first throttle valve is the Y-axis. The flow rate of the first throttle valve as it changes with the pressure differential across the first throttle valve can be a straight line, a substantially straight line, or a curve. The slope can be an average slope or a slope at any point. When the slope of the flow rate as it changes with the pressure differential meets the above-mentioned limiting conditions, the refrigeration capacity requirements under various refrigeration operating conditions can be met.

[0049] In some exemplary embodiments, Figure 1 、 Figures 5 to 7 As shown, the first throttle valve 600 and the second throttle valve 700 are both configured as electronic expansion valves.

[0050] It can be, for example Figure 5As shown, in the cooling mode, based on P1 being 0.1P~0.4P, q1 and k1 are adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 0.05Q~0.3Q (11L / min~65L / min), and the pressure difference across the first throttle valve 600 is adjusted to 0.08D~0.48D (0.2MPa~1.1MPa); or it can be, as Figure 6 As shown, in the cooling mode, based on P1 being 0.1P~0.4P, q1 is adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 0.05Q~0.3Q (11L / min~65L / min), and the pressure difference across the first throttle valve 600 is adjusted to 0.08D~0.48D (0.2MPa~1.1MPa); or it can be, as Figure 7 As shown, in the refrigeration mode, based on P1 being 0.1P~0.4P, k1 is adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 0.05Q~0.3Q (11L / min~65L / min), and the pressure difference at both ends of the first throttle valve 600 is adjusted to 0.08D~0.48D (0.2MPa~1.1MPa), etc.; the above can all achieve the purpose of this application, and its purpose does not deviate from the design concept of the present invention, and will not be repeated here, and should all fall within the scope of protection of this application.

[0051] It can be, for example Figure 5 As shown, in the cooling mode, based on P1 being 0.4P to 0.7P, q1 and k1 are adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 0.3Q to 0.48Q (65L / min to 103L / min), and the pressure difference across the first throttle valve 600 is adjusted to 0.48D to 0.83D (1.1MPa to 1.9MPa); or it can be, as Figure 6 As shown, in the cooling mode, based on P1 being 0.4P to 0.7P, q1 is adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 0.3Q to 0.48Q (65L / min to 103L / min), and the pressure difference across the first throttle valve 600 is adjusted to 0.48D to 0.83D (1.1MPa to 1.9MPa); or it can be, as Figure 7As shown, in the cooling mode, based on P1 being 0.4P~0.7P, k1 is adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 0.3Q~0.48Q (65L / min~103L / min), and the pressure difference at both ends of the first throttle valve 600 is adjusted to 0.48D~0.83D (1.1MPa~1.9MPa), etc.; the above can all achieve the purpose of this application, and its purpose does not deviate from the design concept of the present invention, and will not be repeated here, and should all fall within the protection scope of this application.

[0052] It can be, for example Figure 5 As shown, in the cooling mode, based on P1 being 0.7P to 0.9P, q1 and k1 are adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 0.48Q to 0.94Q (103L / min to 202L / min), and the pressure difference across the first throttle valve 600 is adjusted to 0.83D to 0.87D (1.9MPa to 2.0MPa); or it can be, as Figure 6 As shown, in the cooling mode, based on P1 being 0.7P~0.9P, q1 is adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 0.48Q~0.94Q (103L / min~202L / min), and the pressure difference across the first throttle valve 600 is adjusted to 0.83D~0.87D (1.9MPa~2.0MPa); or it can be, as Figure 7 As shown, in the cooling mode, based on P1 being 0.7P~0.9P, k1 is adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 0.48Q~0.94Q (103L / min~202L / min), and the pressure difference at both ends of the first throttle valve 600 is adjusted to 0.83D~0.87D (1.9MPa~2.0MPa), etc.; the above can all achieve the purpose of this application, and its purpose does not deviate from the design concept of the present invention, and will not be repeated here, and should all fall within the scope of protection of this application.

[0053] It can be, for example Figure 5 As shown, in the cooling mode, based on P1 being 0.9P~P, q1 and k1 are adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 0.94Q~Q (202L / min~215L / min), and the pressure difference across the first throttle valve 600 is adjusted to 0.87D~D (2.0MPa~2.3MPa); or it can be, as Figure 6As shown, in the cooling mode, based on P1 being 0.9P~P, q1 is adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 0.94Q~Q (202L / min~215L / min), and the pressure difference across the first throttle valve 600 is adjusted to 0.87D~D (2.0MPa~2.3MPa); or it can be, as Figure 7 As shown, in the cooling mode, based on P1 being 0.9P~P, k1 is adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 0.94Q~Q (202L / min~215L / min), and the pressure difference at both ends of the first throttle valve 600 is adjusted to 0.87D~D (2.0MPa~2.3MPa), etc.; the above can all achieve the purpose of this application, and its purpose does not deviate from the design concept of the present invention, and will not be repeated here, and should all fall within the protection scope of this application.

[0054] In other exemplary embodiments, Figure 2 and Figure 3 As shown, the first throttle valve 600 is a variable throttle valve, and the second throttle valve 700 is an electronic expansion valve. The variable throttle valve includes a unidirectional throttle passage 610 and a unidirectional second passage 620. In cooling mode, the throttle passage 610 is open, and in heating mode, the second passage 620 is open. The throttle passage 610 includes a valve seat 611, a valve core 612, and a return spring 613 that cooperate with each other. The valve core 612 is located between the valve seat 611 and the return spring 613. When the refrigerant pushes the valve core 612 away from the valve seat 611, the opening of the throttle passage 610 increases. When the return spring 613 pushes the valve core 612 toward the valve seat 611, the opening of the throttle passage 610 decreases. The return spring 613 can include multiple springs or spring segments connected in parallel or in series, with the same or different elastic coefficients, to achieve different openings of the first throttle valve 600 under different pressure differentials.

[0055] In some examples, such as Figures 2 to 4 As shown, by designing the corresponding throttling passage 610, the following is achieved:

[0056] In cooling mode, based on P1 being 0.1P to 0.4P and the pressure difference across the first throttle valve 600 being 0.2MPa to 1.1MPa, the flow rate of the first throttle valve 600 is 11L / min to 65L / min under the action of the return spring 613;

[0057] In cooling mode, based on P1 being 0.4P to 0.7P and the pressure difference across the first throttle valve 600 being 1.1MPa to 1.9MPa, the flow rate of the first throttle valve 600 is 65L / min to 103L / min under the action of the return spring 613;

[0058] In cooling mode, based on P1 being 0.7P to 0.9P and the pressure difference across the first throttle valve 600 being 1.9MPa to 2.0MPa, the flow rate of the first throttle valve 600 is 103L / min to 202L / min under the action of the return spring 613;

[0059] In the cooling mode, based on P1 being 0.9P~P, the pressure difference across the first throttle valve 600 is 2.0MPa~2.3MPa. Then, under the action of the return spring 613, the flow rate of the first throttle valve 600 is 202L / min~215L / min.

[0060] like Figures 2 to 4 As shown, in the cooling mode: when P1 is 0.1P~0.4P, by adjusting k1 or due to changes in the compressor frequency, the pressure difference across the first throttle valve 600 is 0.2MPa~1.1Mpa, and the compression amount of the return spring 613 is within the first set compression amount range. At this time, the flow rate of the first throttle valve 600 is 11L / min~65L / min; when P1 is 0.4P~0.7P, by adjusting k1 or due to changes in the compressor frequency, the pressure difference across the first throttle valve 600 is 1.1MPa~1.9MPa, and the compression amount of the return spring 613 is within the second set compression amount range. At this time, the flow rate of the first throttle valve 600 is 65L / min~103L / min; when P1 is 0.7P~0.9P, by adjusting k1 or due to changes in the compressor frequency, the pressure difference at both ends of the first throttle valve 600 is 1.9MPa~2.0MPa, and the compression amount of the return spring 613 is within the third set compression amount range. At this time, the flow rate of the first throttle valve 600 is 103L / min~202L / min; when P1 is 0.9P~P, by adjusting k1 or due to changes in the compressor frequency, the pressure difference at both ends of the first throttle valve 600 is 2.0MPa~2.3MPa, and the compression amount of the return spring 613 is within the fourth set compression amount range. At this time, the flow rate of the first throttle valve 600 is 202L / min~215L / min.

[0061] In other examples, such as Figure 2 、 Figure 3 and Figure 7 As shown, in the cooling mode, based on P1 being 0.1P to 0.4P, k1 is adjusted so that the flow rate of the first throttle valve 600 is adjusted to 11L / min to 65L / min, and the pressure difference across the first throttle valve 600 is adjusted to 0.2MPa to 1.1MPa; Figure 2 、 Figure 3 and Figure 7As shown, in the cooling mode, based on P1 being 0.4P to 0.7P, k1 is adjusted so that the flow rate of the first throttle valve 600 is adjusted to 65L / min to 103L / min, and the pressure difference across the first throttle valve 600 is adjusted to 1.1MPa to 1.9MPa; Figure 2 、 Figure 3 and Figure 7 As shown, in the cooling mode, based on P1 being 0.7P to 0.9P, k1 is adjusted so that the flow rate of the first throttle valve 600 is adjusted to 103L / min to 202L / min, and the pressure difference across the first throttle valve 600 is adjusted to 1.9MPa to 2.0MPa; Figure 2 、 Figure 3 and Figure 7 As shown, in the cooling mode, based on P1 being 0.9P~P, k1 is adjusted so that the flow rate of the first throttle valve 600 is adjusted to 202L / min~215L / min, and the pressure difference across the first throttle valve 600 is adjusted to 2.0MPa~2.3MPa.

[0062] like Figure 2 、 Figure 3 and Figure 7 As shown, in cooling mode: in cooling mode, based on P1 being 0.1P~0.4P, the pressure difference across the first throttle valve 600 is adjusted to 0.2MPa~1.1MPa, the return spring 613 has a corresponding compression amount, and by adjusting k1, the flow rate of the first throttle valve 600 is adjusted to 11L / min~65L / min; in cooling mode, based on P1 being 0.4P~0.7P, the pressure difference across the first throttle valve 600 is adjusted to 1.1MPa~1.9MPa, the return spring 613 has a corresponding compression amount, and by adjusting k1, the flow rate of the first throttle valve 600 is adjusted to 65L / min~103L / min; in cooling mode, based on P1 being 0.7P to 0.9P, the pressure differential across the first throttle valve 600 is adjusted to 1.9MPa to 2.0MPa, and the return spring 613 has a corresponding amount of compression. By adjusting k1, the flow rate of the first throttle valve 600 is adjusted to 103L / min to 202L / min. In cooling mode, based on P1 being 0.9P to P, the pressure differential across the first throttle valve 600 is adjusted to 2.0MPa to 2.3MPa, and the return spring 613 has a corresponding amount of compression. By adjusting k1, the flow rate of the first throttle valve 600 is adjusted to 202L / min to 215L / min. Different P1s generally result in different amounts of compression for the return spring 613.

[0063] Through experimental testing, it is verified that the above-mentioned schemes can effectively control the condensation of the refrigerant radiator 400 when the outdoor ambient temperature is in the range of 18°C ​​to 60°C, and at the same time meet the requirements of the compression ratio and △T for the reliable operation of the compressor 100. The air treatment equipment has lower cost and better performance and reliability.

[0064] In some exemplary embodiments, Figures 1 to 3 As shown, in heating mode, the maximum opening of the first throttle valve 600 is q, q1 = q, k1 < k. During normal heating, k1 < k2 can be set. In heating mode, the high-temperature, high-pressure liquid refrigerant passes through the indoor heat exchanger 300 for heat exchange and cooling, then first passes through the first throttle valve 600, which is in a fully open state, and then dissipates heat from the electronic control components through the refrigerant radiator 400. This can simultaneously dissipate heat from the electronic control components without generating condensed water. Moreover, this process can meet the refrigerant flow requirements for defrosting when the light frost fast melting function is enabled.

[0065] The light frost quick melting function can solve the problems of large temperature fluctuation, valve group noise and abnormal sound caused by thermal expansion and contraction caused by frequent tangential defrosting (four-way valve 200) during winter heating at a low cost.

[0066] Light frost quick melting function: When light frost forms on the outdoor heat exchanger 500, the four-way valve 200 does not reverse, the second throttle valve 700 opens more, the compressor 100 is reduced to low-frequency operation, the fan used in conjunction with the outdoor heat exchanger 500 stops, and the fan used in conjunction with the indoor heat exchanger 300 reduces its speed; when the thickness of frost on the outdoor heat exchanger 500 is medium, the four-way valve 200 does not reverse, the second throttle valve 700 opens more, the compressor 100 is reduced to medium-frequency operation, the fan used in conjunction with the outdoor heat exchanger 500 stops, and the fan used in conjunction with the indoor heat exchanger 300 also stops.

[0067] When thick frost forms on the outdoor heat exchanger 500, the tangential defrost mode is triggered, and the outdoor heat exchanger 500 is defrosted by switching the conduction direction of the four-way valve 200.

[0068] The control method of the air treatment equipment proposed in the embodiment of the present invention is as follows: Figures 5 to 7 As shown, including:

[0069] In cooling mode, obtain P1;

[0070] Based on P1 being 0.1P to 0.4P, q1 and / or k1 are adjusted to adjust the flow rate of the first throttle valve 600 to 11L / min to 65L / min, and the pressure difference across the first throttle valve 600 to 0.2MPa to 1.1MPa.

[0071] This control method, in the cooling mode, when P1 is 0.1P~0.4P, adjusts q1 and / or k1 to adjust the flow rate of the first throttle valve 600 to 11L / min~65L / min, and the pressure difference across the first throttle valve 600 to 0.2MPa~1.1MPa. This can avoid the compression ratio and △T of the compressor 100 being too low during operation, and can effectively ensure the operating reliability of the compressor 100.

[0072] It can be, for example Figure 5 As shown, in the cooling mode, based on P1 being 0.1P to 0.4P, q1 and k1 are adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 11L / min to 65L / min, and the pressure difference across the first throttle valve 600 is adjusted to 0.2MPa to 1.1MPa, and then the step of obtaining P1 is performed; or it can be, as shown in FIG. Figure 6 As shown, in the cooling mode, based on P1 being 0.1P to 0.4P, q1 is adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 11L / min to 65L / min, and the pressure difference across the first throttle valve 600 is adjusted to 0.2MPa to 1.1MPa, and then the step of obtaining P1 is performed; or it can be, as Figure 7 As shown, in the cooling mode, based on P1 being 0.1P~0.4P, k1 is adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 11L / min~65L / min, and the pressure difference at both ends of the first throttle valve 600 is adjusted to 0.2MPa~1.1MPa, and then the steps of obtaining P1 are executed, etc.; the above can all achieve the purpose of this application, and its purpose does not deviate from the design concept of the present invention, and will not be repeated here, and should all fall within the scope of protection of this application.

[0073] In some examples, such as Figures 5 to 7 As shown, the control method also includes: based on P1 being 0.4P~0.7P, adjusting q1 and / or k1 so that the flow rate of the first throttle valve 600 is adjusted to 65L / min~103L / min, and the pressure difference across the first throttle valve 600 is adjusted to 1.1MPa~1.9MPa.

[0074] It can be, for example Figure 5 As shown, in the cooling mode, based on P1 being 0.4P to 0.7P, q1 and k1 are adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 65L / min to 103L / min, and the pressure difference across the first throttle valve 600 is adjusted to 1.1MPa to 1.9MPa, and then the step of obtaining P1 is performed; or it can be, as Figure 6As shown, in the cooling mode, based on P1 being 0.4P to 0.7P, q1 is adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 65L / min to 103L / min, and the pressure difference across the first throttle valve 600 is adjusted to 1.1MPa to 1.9MPa, and then the step of obtaining P1 is performed; or it can be, as Figure 7 As shown, in the cooling mode, based on P1 being 0.4P~0.7P, k1 is adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 65L / min~103L / min, and the pressure difference at both ends of the first throttle valve 600 is adjusted to 1.1MPa~1.9MPa, and then the steps of obtaining P1 are executed, etc.; the above can all achieve the purpose of this application, and its purpose does not deviate from the design concept of the present invention, and will not be repeated here, and should all fall within the scope of protection of this application.

[0075] In some examples, such as Figures 5 to 7 As shown, the control method also includes: based on P1 being 0.7P~0.9P, adjusting q1 and / or k1 so that the flow rate of the first throttle valve 600 is adjusted to 103L / min~202L / min, and the pressure difference across the first throttle valve 600 is adjusted to 1.9MPa~2.0MPa.

[0076] It can be, for example Figure 5 As shown, in the cooling mode, based on P1 being 0.7P to 0.9P, q1 and k1 are adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 103L / min to 202L / min, and the pressure difference across the first throttle valve 600 is adjusted to 1.9MPa to 2.0MPa, and then the step of obtaining P1 is performed; or it can be, as Figure 6 As shown, in the cooling mode, based on P1 being 0.7P to 0.9P, q1 is adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 103L / min to 202L / min, and the pressure difference across the first throttle valve 600 is adjusted to 1.9MPa to 2.0MPa, and then the step of obtaining P1 is performed; or it can be, as Figure 7 As shown, in the cooling mode, based on P1 being 0.7P~0.9P, k1 is adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 103L / min~202L / min, and the pressure difference across the first throttle valve 600 is adjusted to 1.9MPa~2.0MPa, and then the steps of obtaining P1 are executed, etc.; the above can all achieve the purpose of this application, and its purpose does not deviate from the design concept of the present invention, and will not be repeated here, and should all fall within the scope of protection of this application.

[0077] In some examples, such as Figures 5 to 7 As shown, the control method also includes: based on P1 being 0.9P~P, adjusting q1 and / or k1 so that the flow rate of the first throttle valve 600 is adjusted to 202L / min~215L / min, and the pressure difference across the first throttle valve 600 is adjusted to 2.0MPa~2.3MPa.

[0078] It can be, for example Figure 5 As shown, in the cooling mode, based on P1 being 0.9P~P, q1 and k1 are adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 202L / min~215L / min, and the pressure difference across the first throttle valve 600 is adjusted to 2.0MPa~2.3MPa, and then the step of obtaining P1 is performed; or it can be, as Figure 6 As shown, in the cooling mode, based on P1 being 0.9P~P, q1 is adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 202L / min~215L / min, and the pressure difference across the first throttle valve 600 is adjusted to 2.0MPa~2.3MPa, and then the step of obtaining P1 is performed; or it can be, as Figure 7 As shown, in the cooling mode, based on P1 being 0.9P~P, k1 is adjusted (according to a preset data table or a set formula) so that the flow rate of the first throttle valve 600 is adjusted to 202L / min~215L / min, and the pressure difference at both ends of the first throttle valve 600 is adjusted to 2.0MPa~2.3MPa, and then the steps of obtaining P1 are executed, etc.; the above can all achieve the purpose of this application, and its purpose does not deviate from the design concept of the present invention, and will not be repeated here, and should all fall within the scope of protection of this application.

[0079] To sum up, in the air handling equipment provided by the present application, in the cooling mode, the refrigerant supplied by the compressor is cooled in the outdoor heat exchanger to become a high-pressure, medium-temperature saturated or supercooled liquid, and then enters the refrigerant radiator after throttling and reducing the pressure through the second throttle valve to dissipate heat for the electronic control device. By setting k2≤k1<k, the refrigerant radiator is prevented from generating condensed water, thereby ensuring the stability and reliability of the operation of the electronic control device; moreover, in the cooling mode, when P1 is 0.1P~0.4P, the pressure difference across the first throttle valve is 0.08D~0.48D, and the flow rate of the first throttle valve is 0.05Q~0.3Q, which can avoid the compression ratio and △T of the compressor being too low during operation, thereby effectively ensuring the operating reliability of the compressor.

[0080] In the description of the present invention, it should be noted that the terms "upper", "lower", "one side", "the other side", "one end", "the other end", "side", "relative", "four corners", "periphery", ""mouth"-shaped structure", etc., indicating the orientation or position relationship, are based on the orientation or position relationship shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the structure referred to has a specific orientation, is constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention.

[0081] In the description of the embodiments of the present invention, unless otherwise expressly specified or limited, the terms "connection," "direct connection," "indirect connection," "fixed connection," "installation," and "assembly" should be understood in a broad sense. For example, they may refer to a fixed connection, a detachable connection, or an integral connection. The terms "installation," "connection," and "fixed connection" may refer to a direct connection, an indirect connection through an intermediate medium, or internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

[0082] It will be appreciated by those skilled in the art that all or some of the steps, systems, and functional modules / units in the methods disclosed above may be implemented as software, firmware, hardware, and appropriate combinations thereof. In hardware implementations, the division between the functional modules / units mentioned in the above description does not necessarily correspond to the division of physical components; for example, a physical component may have multiple functions, or a function or step may be performed by several physical components in cooperation. Some or all components may be implemented as software executed by a processor, such as a digital signal processor or a microprocessor, or implemented as hardware, or implemented as an integrated circuit, such as an application-specific integrated circuit. Such software may be distributed on a computer-readable medium, which may include a computer storage medium (or non-transitory medium) and a communication medium (or temporary medium). As is well known to those skilled in the art, the term computer storage medium includes volatile and non-volatile, removable, and non-removable media implemented in any method or technology for storing information (such as computer-readable instructions, data structures, program modules, or other data). Computer storage media include, but are not limited to, RAK, ROK, EEPROK, flash memory or other memory technology, CD-ROM, digital versatile disk (DVD) or other optical disk storage, magnetic cassettes, magnetic tape, magnetic disk storage or other magnetic storage devices, or any other medium that can be used to store the desired information and can be accessed by a computer. In addition, it is well known to those skilled in the art that communication media generally contain computer-readable instructions, data structures, program modules, or other data in a modulated data signal such as a carrier wave or other transport mechanism, and may include any information delivery media.

Claims

1. An air treatment device, characterized in that: The invention comprises a compressor, a four-way valve, an indoor heat exchanger, a refrigerant radiator, an outdoor heat exchanger, a first throttle valve and a second throttle valve connected to each other, wherein the first throttle valve is located between the indoor heat exchanger and the refrigerant radiator, and the second throttle valve is located between the outdoor heat exchanger and the refrigerant radiator; The actual operating frequency of the compressor is P1, the set frequency of the compressor is P, the maximum flow rate of the first throttle valve is Q, the pressure difference across the first throttle valve varies between 0 and Q when the actual flow rate of the first throttle valve varies between 0 and D, the actual opening of the second throttle valve is k1, the maximum opening of the second throttle valve is k, and in cooling mode, k2≤k1<k, k2 is the set opening of the second throttle valve, and the set frequency of the compressor is the maximum operating frequency of the compressor; In the cooling mode, based on P1 being 0.1P~0.4P, the pressure difference across the first throttle valve is 0.08D~0.48D, and the flow rate of the first throttle valve is 0.05Q~0.3Q.

2. The air treatment equipment according to claim 1, characterized in that In the cooling mode, based on P1 being 0.4P~0.7P, the pressure difference across the first throttle valve is 0.48D~0.83D, and the flow rate of the first throttle valve is 0.3Q~0.48Q.

3. The air treatment equipment according to claim 2, characterized in that In the cooling mode, based on P1 being 0.7P~0.9P, the pressure difference across the first throttle valve is 0.83D~0.87D, and the flow rate of the first throttle valve is 0.48Q~0.94Q.

4. The air treatment equipment according to claim 3, characterized in that In the cooling mode, based on P1 being 0.9P~P, the pressure difference across the first throttle valve is 0.87D~D, and the flow rate of the first throttle valve is 0.94Q~Q.

5. The air treatment equipment according to claim 4, characterized in that In cooling mode, based on P1 being 0.1P to 0.4P, the pressure difference across the first throttle valve is 0.2MPa to 1.1MPa, and the flow rate of the first throttle valve is 11L / min to 65L / min; In cooling mode, based on P1 being 0.4P to 0.7P, the pressure difference across the first throttle valve is 1.1MPa to 1.9MPa, and the flow rate of the first throttle valve is 65L / min to 103L / min; In cooling mode, based on P1 being 0.7P~0.9P, the pressure difference across the first throttle valve is 1.9MPa~2.0MPa, and the flow rate of the first throttle valve is 103L / min~202L / min; In the cooling mode, based on P1 being 0.9P~P, the pressure difference across the first throttle valve is 2.0MPa~2.3MPa, and the flow rate of the first throttle valve is 202L / min~215L / min.

6. The air treatment equipment according to claim 4, characterized in that Based on P1 being 0.1P-0.4P, the slope of the flow rate of the first throttle valve changing with the pressure difference across the first throttle valve is g1; Based on P1 being 0.4P-0.7P, the slope of the flow rate of the first throttle valve changing with the pressure difference across the first throttle valve is g2, g2<g1; Based on P1 being 0.7P-0.9P, the slope of the flow rate of the first throttle valve changing with the pressure difference across the first throttle valve is g3, where g3>g1; Based on P1 being 0.9P~P, the slope of the flow rate of the first throttle valve changing with the pressure difference at both ends of the first throttle valve is g4, g4<g1, g4<g2.

7. The air treatment equipment according to any one of claims 1 to 6, characterized in that: The actual opening of the first throttle valve is q1, and in the cooling mode, q1≤k1.

8. The air treatment equipment according to any one of claims 1 to 6, characterized in that: The first throttle valve and the second throttle valve are both electronic expansion valves; the actual opening of the first throttle valve is q1; In cooling mode, based on P1 being 0.1P~0.4P, q1 or q1 and k1 are adjusted so that the pressure difference across the first throttle valve is adjusted to 0.08D~0.48D and the flow rate of the first throttle valve is adjusted to 0.05Q~0.3Q.

9. The air treatment equipment according to any one of claims 1 to 6, characterized in that: The first throttle valve is a variable throttle valve, and the second throttle valve is an electronic expansion valve. The variable throttle valve includes a unidirectional throttle passage and a unidirectional second passage. In cooling mode, the throttle passage is conductive, and in heating mode, the second passage is conductive. The throttle passage includes a valve seat, a valve core, and a return spring used in conjunction with each other. In the cooling mode, based on P1 being 0.1P~0.4P, the pressure difference across the first throttle valve is 0.08D~0.48D, and under the action of the return spring, the flow rate of the first throttle valve is 0.05Q~0.3Q.

10. The air treatment equipment according to any one of claims 1 to 6, characterized in that: The maximum opening of the first throttle valve is q, and the actual opening of the first throttle valve is q1. In the heating mode, q1=q, and k1<k.

11. A control method for air handling equipment according to claim 8, characterized in that: include: In cooling mode, obtain P1; Based on P1 being 0.1P~0.4P, q1 or q1 and k1 are adjusted so that the pressure difference across the first throttle valve is adjusted to 0.08D~0.48D and the flow rate of the first throttle valve is adjusted to 0.05Q~0.3Q.

12. The control method according to claim 11, characterized in that: Also includes: Based on P1 being 0.4P~0.7P, q1 or q1 and k1 are adjusted so that the pressure difference across the first throttle valve is adjusted to 0.48D~0.83D and the flow rate of the first throttle valve is adjusted to 0.3Q~0.48Q; Based on P1 being 0.7P~0.9P, q1 or q1 and k1 are adjusted so that the pressure difference across the first throttle valve is adjusted to 0.83D~0.87D and the flow rate of the first throttle valve is adjusted to 0.48Q~0.94Q; Based on P1 being 0.9P~P, q1 or q1 and k1 are adjusted so that the pressure difference across the first throttle valve is adjusted to 0.87D~D, and the flow rate of the first throttle valve is adjusted to 0.94Q~Q.

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