Air treatment equipment and control method

Abstract

The invention discloses air treatment equipment and a control method. The air treatment equipment comprises a compressor, a four-way valve, an indoor heat exchanger, a refrigerant radiator, an outdoor heat exchanger, a first throttling valve and a second throttling valve which are connected, the first throttling valve is located between the indoor heat exchanger and the refrigerant radiator, and the second throttling valve is located between the outdoor heat exchanger and the refrigerant radiator; the actual operation frequency of the compressor is P1, the set frequency of the compressor is P, the maximum flow of the first throttling valve is Q, the pressure difference between the two ends of the first throttling valve changes between 0 and D when the actual flow of the first throttling valve changes between 0 and Q, the actual opening degree of the second throttling valve is k1, the maximum opening degree of the second throttling valve is k, and in the refrigeration mode, k1 is larger than or equal to k2 and smaller than k, k2 is the set opening degree of the second throttle valve; in the refrigeration mode, on the basis that P1 ranges from 0.1 P to 0.4 P, the pressure difference between the two ends of the first throttling valve ranges from 0.08 D to 0.48 D, and the flow of the first throttling valve ranges from 0.05 Q to 0.3 Q, the situation that any one of the compression ratio and T is too low during operation of the compressor can be avoided.

Description

Technical Field

[0001] The present invention relates to electrical equipment technology, and more particularly to an air handling device and a control method thereof. 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), the overall throttling effect of the refrigeration system is insufficient, which will cause the compression ratio (the ratio of the compressor exhaust absolute pressure to the suction absolute pressure) and △T (the difference between the compressor bottom temperature and the middle temperature of the outdoor heat exchanger) of the compressor to be too low, and cannot meet the requirements of compressor operation reliability. 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 control method for air handling equipment.

[0005] The air handling 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 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 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 of the first throttle valve is 0.05Q~0.3Q.

[0006] In some exemplary embodiments, in the 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 the 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 the cooling mode, q1≤k1. In some exemplary embodiments, 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 the cooling mode, based on P1 being 0.1P to 0.4P, q1 and / or k1 are adjusted so that the pressure difference across the first throttle valve is adjusted to 0.08D to 0.48D, and the flow rate of the first throttle valve is adjusted to 0.05Q to 0.3Q.

[0012] In some exemplary embodiments, the first throttle valve is a variable throttle valve, 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, 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; wherein:

[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 degree of the first throttle valve is q, the actual opening degree of the first throttle valve is q1, and in the heating mode, q1=q, k1<k.

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

[0016] In cooling mode, obtain P1;

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

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

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

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

[0021] Based on P1 being 0.9P~P, q1 and / or 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.

[0022] Compared with the related art, 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 to dissipate heat for the electronic control device after throttling and reducing the pressure through the second throttle valve. By setting k2≤k1<k, condensation water is avoided in the refrigerant radiator, 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, thereby avoiding the situation where either the compression ratio or △T of the compressor is too low during operation, thereby effectively ensuring the operating reliability of the compressor.

[0023] Other features and advantages of the present application will be described in the following description, and partly become apparent from the description, or be understood by implementing the present application. Other advantages of the present application can be realized and obtained by the schemes 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 for some embodiments of the present application;

[0026] Figure 2 A schematic diagram of the structure of air treatment equipment provided for 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 The flow-pressure difference 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 A flow chart of a control method 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 the 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] The present application describes multiple embodiments, but the description is exemplary rather than restrictive, and it is obvious to those skilled in the art that there may be more embodiments and implementations within the scope of the embodiments described in the present application. Although many possible feature combinations are shown in the drawings and discussed in the specific embodiments, 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] The present 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 the present application may also be combined with any conventional features or elements to form a unique invention scheme defined by the claims. Any features or elements of any embodiment may also be combined with features or elements from other invention schemes to form another unique invention scheme defined by the claims. Therefore, it should be understood that any feature shown and / or discussed in the present application may be implemented individually or in any appropriate combination. Therefore, except for the limitations made according to the attached claims and their equivalents, the embodiments are not subject to other restrictions. In addition, various modifications and changes may be made within the scope of protection of the attached 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 of the specific order described. As will be understood by those of ordinary skill in the art, other sequences of steps are also possible. Therefore, the specific sequence 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 the steps of performing them in the order written, and those skilled in the art can easily understand that these sequences 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 of the first throttle valve 600 (such as the flow when the first throttle valve is fully opened) is Q, when the actual flow 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 of 0.1P~0.4P, the pressure difference at both ends of the first throttle valve 600 is 0.08D~0.48D, and the flow of the first throttle valve 600 is 0.05Q~0.3Q. In the cooling mode, when k1=k2, the refrigerant passing through the refrigerant radiator 400 can dissipate heat for the electronic control device, and the refrigerant radiator 400 does not produce condensed water. k2 can be a preset fixed value or determined according to the temperature and humidity of the environment where the refrigerant radiator 400 is located. The electronic control device is 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 to dissipate heat for the electronic control components after throttling and reducing the pressure through the second throttle valve 700. 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 refrigeration process, the refrigerant radiator 400 is cooled by the second throttle valve 700 for preliminary throttling and pressure reduction, and the first throttle valve 600 is used for secondary throttling, which 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 requirements of product capacity and energy efficiency.

[0041] In some examples, 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. 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 difference 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 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. 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 difference across the first throttle valve 600 is 1.9MPa to 2.0MPa.

[0044] In the cooling mode, when P1 is 0.7P-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 requirements of the cooling capacity output in the actual use mode of the user.

[0045] In some examples, in cooling mode, based on P1 being 0.9P to P, the pressure difference 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 202L / min to 215L / min, and the pressure difference across the first throttle valve 600 is 2.0MPa to 2.3MPa.

[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 requirement of the extreme exhaust temperature of the compressor 100 when the product is operated 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 the 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 across 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 across 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 across 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 across the first throttle valve is g4, g4<g1, g4<g2. The slope of the flow rate of the first throttle valve as the pressure difference at both ends of the first throttle valve changes refers to the slope of the flow rate of the first throttle valve as the pressure difference at both ends of the first throttle valve changes when the pressure difference at both ends of 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 the pressure difference at both ends of the first throttle valve can be a straight line, a substantially straight line or a curve. The above slope can refer to the average slope or the slope of any point. When the slope of the flow rate as the pressure difference changes meets the above limiting conditions, it can meet the refrigeration capacity requirements under various refrigeration operating conditions.

[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 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 0.05Q to 0.3Q (11L / min to 65L / min), and the pressure difference across the first throttle valve 600 is adjusted to 0.08D to 0.48D (0.2MPa to 1.1MPa); or it can be, as 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 0.05Q to 0.3Q (11L / min to 65L / min), and the pressure difference across the first throttle valve 600 is adjusted to 0.08D to 0.48D (0.2MPa to 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 across the first throttle valve 600 is adjusted to 0.08D~0.48D (0.2MPa~1.1MPa), etc.; all of the above can achieve the purpose of the present 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 the present 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 refrigeration 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 across the first throttle valve 600 is adjusted to 0.48D~0.83D (1.1MPa~1.9MPa), etc.; all of the above can achieve the purpose of the present 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 the present 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 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 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 7 As shown, in the refrigeration 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.; all of the above can achieve the purpose of the present 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 the present 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 refrigeration 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 across the first throttle valve 600 is adjusted to 0.87D~D (2.0MPa~2.3MPa), etc.; all of the above can achieve the purpose of the present 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 the present application.

[0054] In some 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 the cooling mode, the throttle passage 610 is open, and in the 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 used in conjunction with each other. The valve core 612 is located between the valve seat 611 and the return spring 613. The refrigerant pushes the valve core 612 to move away from the valve seat 611, and the opening of the throttle passage 610 increases. The return spring 613 pushes the valve core 612 to move toward the valve seat 611, and the opening of the throttle passage 610 decreases. The return spring 613 may include a plurality of springs or spring segments with the same or different elastic coefficients connected in parallel or in series, so as to achieve different openings of the first throttle valve 600 under different pressure differences.

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

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

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

[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 the change of the compressor frequency, the pressure difference at both ends of the first throttle valve 600 is 0.2MPa~1.1Mpa, and the compression amount of the return spring 613 is in 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 the change of the compressor frequency, the pressure difference at both ends of the first throttle valve 600 is 1.1MPa~1.9MPa, and the compression amount of the return spring 613 is in 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 the cooling mode: 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 adjusted to 0.2MPa~1.1MPa, and the return spring 613 has a corresponding compression amount. By adjusting k1, the flow rate of the first throttle valve 600 is adjusted to 11L / min~65L / min; in the cooling mode, based on P1 being 0.4P~0.7P, the pressure difference at both ends of the first throttle valve 600 is adjusted to 1.1MPa~1.9MPa, and the return spring 613 has a corresponding compression amount. 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~0.9P, the pressure difference at both ends of the first throttle valve 600 is adjusted to 1.9MPa~2.0MPa, 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 103L / min~202L / min; in cooling mode, based on P1 being 0.9P~P, the pressure difference at both ends of the first throttle valve 600 is adjusted to 2.0MPa~2.3MPa, 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 202L / min~215L / min. If P1 is different, the compression amount of the return spring 613 is generally different.

[0063] Through experimental tests and verification, 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 the heating mode, the maximum opening of the first throttle valve 600 is q, q1=q, k1<k. In normal heating, it can be set to k1<k2. In the heating mode, after the high-temperature and high-pressure liquid refrigerant passes through the indoor heat exchanger 300 for heat exchange and cooling, it first passes through the first throttle valve 600, and the first throttle valve 600 is in a fully conductive state, and then the electronic control components are cooled through the refrigerant radiator 400, which can simultaneously meet the heat dissipation of the electronic control components and no condensed water is generated. Moreover, when the thin frost quick melting function is enabled, this process can meet the defrosting requirements for refrigerant flow.

[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 defrosting 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 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.

[0071] This control method, in the refrigeration 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 is adjusted 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 may be, as 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 may 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 11L / min~65L / min, and the pressure difference across the first throttle valve 600 is adjusted to 0.2MPa~1.1MPa, and then the steps of obtaining P1 are executed; the above can all achieve the purpose of the present 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 the present 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 may 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 may be, as Figure 7 As shown, in the refrigeration 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 across the first throttle valve 600 is adjusted to 1.1MPa~1.9MPa, and then the steps of obtaining P1 are executed; the above can all achieve the purpose of the present 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 the present 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 may 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 may be, as Figure 7 As shown, in the refrigeration 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; the above can all achieve the purpose of the present 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 the present 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, 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 refrigeration 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 across the first throttle valve 600 is adjusted to 2.0MPa~2.3MPa, and then the steps of obtaining P1 are executed; the above can all achieve the purpose of the present 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 the present application.

[0079] To summarize, in the air handling equipment provided by the present application, in the refrigeration 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 to dissipate heat for the electronic control device after throttling and reducing the pressure through the second throttle valve. By setting k2≤k1<k, condensation water is avoided in the refrigerant radiator, thereby ensuring the stability and reliability of the operation of the electronic control device; moreover, in the refrigeration 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, thereby avoiding the situation where either the compression ratio or △T of the compressor is 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" and the like indicate orientations or positional relationships based on the orientations or positional relationships 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 referred structure has a specific orientation, is constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0081] In the description of the embodiments of the present invention, unless otherwise clearly specified and limited, the terms "connection", "direct connection", "indirect connection", "fixed connection", "installation", and "assembly" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; the terms "installation", "connection", and "fixed connection" can be a direct connection, or an indirect connection through an intermediate medium, or the internal connection of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to 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 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-ROK, digital versatile disk (DVD) or other optical disk storage, magnetic cassettes, magnetic tapes, 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 of ordinary skill in the art that communication media typically 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 of the first throttle valve is Q, the pressure difference at both ends of the first throttle valve changes between 0 and D when the actual flow of the first throttle valve changes between 0 and Q, 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 to 0.4P, the pressure difference across the first throttle valve is 0.08D to 0.48D, and the flow rate of the first throttle valve is 0.05Q to 0.3Q.

2. The air treatment equipment according to claim 1, characterized in that: In the 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.

3. The air treatment equipment according to claim 2, characterized in that: In the 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.

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 to 0.9P, the pressure difference across the first throttle valve is 1.9MPa to 2.0MPa, and the flow rate of the first throttle valve is 103L / min to 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 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-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 device according to any one of claims 1 to 6, characterized in that: The actual opening degree of the first throttle valve is q1, and in the cooling mode, q1≤k1.

8. The air treatment device 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 the cooling mode, based on P1 being 0.1P to 0.4P, q1 and / or k1 are adjusted so that the pressure difference across the first throttle valve is adjusted to 0.08D to 0.48D, and the flow rate of the first throttle valve is adjusted to 0.05Q to 0.3Q.

9. The air treatment device according to any one of claims 1 to 6, characterized in that: The first throttle valve is a variable throttle valve, the second throttle valve is an electronic expansion valve, the variable throttle valve includes a unidirectional throttle passage and a unidirectional second passage, in the cooling mode, the throttle passage is conductive, in the heating mode, the second passage is conductive; the throttle passage includes a valve seat, a valve core and a return spring used in conjunction; wherein: 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.

10. The air treatment device 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 to 0.4P, q1 and / or k1 are adjusted so that the pressure difference across the first throttle valve is adjusted to 0.08D to 0.48D, and the flow rate of the first throttle valve is adjusted to 0.05Q to 0.3Q.

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