Air conditioning system, control method thereof, controller and computer storage medium

Abstract

The invention provides an air conditioning system, a control method of the air conditioning system, a controller and a computer storage medium. The control method comprises the steps that a temperature parameter delta T is determined, the temperature parameter delta T comprises an air supply temperature difference delta Tf or a supply and return water temperature difference value delta Ts, the air supply temperature difference delta Tf is the difference between an air supply temperature actual value Tf1 and an air supply temperature preset value Tf2 of the tail end of the air conditioning system, and the supply and return water temperature difference value delta Ts is the difference between a supply and return water temperature actual value Ts1 and a supply and return water temperature preset value Ts2 of the air conditioning system; determining an adjustment stride D1% on the basis of the determined temperature parameter [delta] T; and the opening degree of a water valve at the tail end of the air conditioning system is adjusted according to the determined adjusting stride D1%. In this way, the energy-saving performance and comfort of the air conditioning system can be improved.

Description

Technical Field

[0001] The present application relates to the technical field of air conditioning, and in particular to an air conditioning system and a control method thereof, a controller and a computer storage medium. Background Art

[0002] As energy conservation and carbon reduction become more stringent and people's requirements for environmental comfort increase, the energy efficiency and comfort of air-conditioning systems are becoming more and more important.

[0003] Traditional air-conditioning systems use a constant flow control method, which is difficult to effectively meet the needs of different loads and different comfort levels, and their energy saving and comfort levels are poor. Summary of the invention

[0004] A technical problem to be solved by the present application is to improve the energy saving and comfort of the air-conditioning system.

[0005] In order to solve the above technical problems, the present application provides a control method for an air conditioning system, which includes:

[0006] Determine the temperature parameter ΔT, which includes the supply air temperature difference ΔT f Or supply and return water temperature difference ΔT s , supply air temperature difference ΔT f is the actual value of the supply air temperature at the end of the air conditioning system T f1 The preset value of supply air temperature T f2 The difference between the supply and return water temperature difference ΔT s is the actual value of the supply and return water temperature difference of the air conditioning system T s1 The preset value T of the supply and return water temperature difference s2 difference;

[0007] Based on the determined temperature parameter ΔT, determining the adjustment step |D1|%;

[0008] According to the determined adjustment step |D1|%, the opening of the water valve at the end of the air-conditioning system is adjusted.

[0009] In some embodiments, based on the determined temperature parameter ΔT, determining the adjustment step |D1|% includes:

[0010] Determining a D value based on the determined temperature parameter ΔT;

[0011] Based on the determined D value, an adjustment step |D1|% is determined.

[0012] In some embodiments, a>1; and / or, f(ΔT)=ΔT*γ, γ>0; and / or, f(P)=P*δ, δ>0.

[0013] In some embodiments, 1<a≤10; and / or, γ≥0.5; and / or, δ>1.

[0014] In some embodiments, γ>1; and / or, δ=b*c, wherein, 2<b≤10, 0.5≤c≤10.

[0015] In some embodiments, 1<γ≤10; and / or, 2<b≤6; and / or, 0.5≤c≤5.

[0016] In some embodiments, 5s≤t 1 ≤30s; or, 5s≤t 2 ≤30s.

[0017] In some embodiments, 10s≤t 1 ≤30s; or, 10s≤t 2 ≤30s.

[0018] In some embodiments, based on the determined D value, determining the adjustment step |D1|% includes:

[0019] When 0<|D|<1, the adjustment step |D1|% is determined as a constant c; and / or,

[0020] When |D|≥1, the adjustment step |D1|% is determined as |D|%.

[0021] In some embodiments, 0.3%≤c≤0.8%.

[0022] In some embodiments, 0.5%≤c≤0.8%.

[0023] In some embodiments, when the opening of the water valve at the end of the air-conditioning system is adjusted according to the determined adjustment step |D1|%, the opening of the water valve at the end of the air-conditioning system is adjusted once per interval Δt.

[0024] In some embodiments, 3s≤Δt≤20s.

[0025] In some embodiments, 5s≤Δt≤20s.

[0026] In some embodiments, adjusting the opening of the water valve at the end of the air conditioning system according to the determined adjustment step |D1|% includes:

[0027] When D>0, increase the opening of the water valve at the end of the air conditioning system by |D1|%;

[0028] When D<0, reduce the opening of the water valve at the end of the air-conditioning system by |D1|%.

[0029] In some embodiments, determining the temperature parameter ΔT includes:

[0030] After the water valve at the end of the air conditioning system is opened, after a delay time t, the supply air temperature at the end of the air conditioning system is detected as the actual value T of the supply air temperature at the end of the air conditioning system. f1 Alternatively, the return water temperature and the supply water temperature at the end of the air conditioning system are detected, and the difference between the return water temperature and the supply water temperature at the end of the air conditioning system is used as the actual value T of the supply and return water temperature difference at the end of the air conditioning system. s1 ;

[0031] The actual value of the supply air temperature T at the end of the air conditioning system f1 The preset value of supply air temperature T f2 The difference between the supply air temperature difference ΔT f , and the supply air temperature difference ΔT f Determine as the temperature parameter ΔT, or, the actual value of the supply and return water temperature difference T at the end of the air conditioning system s1 The preset value T of the supply and return water temperature difference s2 The difference between the supply and return water temperatures is taken as the supply and return water temperature difference ΔT s , and the supply and return water temperature difference ΔT s Determined as the temperature parameter ΔT.

[0032] In some embodiments, 30s≤t≤90s.

[0033] In some embodiments, 60s≤t≤90s.

[0034] In some embodiments, the control method further comprises:

[0035] Divide multiple terminals of the air conditioning system into multiple control zones so that the total rated flow of each control zone in the multiple control zones is consistent;

[0036] According to the pressure difference of each control zone, the opening of the main water valve of each control zone is adjusted to ensure that the pressure difference of each control zone is kept stable.

[0037] In addition, the present application also provides a controller, which includes a memory and a processor coupled to the memory, and the processor is configured to execute the control method of any embodiment based on instructions stored in the memory.

[0038] In addition, the present application also provides an air conditioning system, which includes the controller of any embodiment.

[0039] In addition, the present application also provides a storage medium, which stores computer instructions, and the computer instructions are executed by a processor to implement the control method of any embodiment.

[0040] By determining the opening adjustment step of the terminal water valve according to temperature parameters including the supply air temperature difference or the supply and return water temperature difference, and dynamically adjusting the terminal water valve opening, accurate variable flow control can be easily achieved, flexibly meeting the needs of different loads and different comfort levels, and effectively improving the energy saving and comfort of the air-conditioning system.

[0041] Other features and advantages of the present application will become apparent from the following detailed description of exemplary embodiments of the present application with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0042] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0043] Figure 1 Schematic diagram of the water circuit of the air-conditioning system in the embodiment of the present application.

[0044] Figure 2 Schematic diagram of the control method in the embodiment of the present application.

[0045] Figure 3 Schematic diagram of supply air temperature change when using traditional control method.

[0046] Figure 4 Schematic diagram of heat exchange change when using traditional control method.

[0047] Figure 5 Schematic diagram of supply air temperature change when the supply air temperature difference control method of the embodiment of the present application is adopted.

[0048] Figure 6 Schematic diagram of the change in heat exchange amount when the air supply temperature difference control method of the embodiment of the present application is adopted.

[0049] Figure 7 Schematic diagram of the change in supply and return water temperature difference when using traditional control method.

[0050] Figure 8 Schematic diagram of the change in the supply and return water temperature difference when the supply and return water temperature difference control method of the embodiment of the present application is adopted.

[0051] Description of reference numerals:

[0052] 1. End; 2. Water supply pipe; 3. Return pipe; 4. Pressure difference control device; 5. Control area. DETAILED DESCRIPTION

[0053] The following will be combined with the drawings in the embodiments of the present application to clearly and completely describe the technical solutions in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all of the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is by no means intended to limit the present application and its application or use. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without carrying out creative work are within the scope of protection of this application.

[0054] Technologies, methods, and equipment known to ordinary technicians in the relevant art may not be discussed in detail, but where appropriate, the technologies, methods, and equipment should be considered as part of the specification.

[0055] In the description of the present application, it should be understood that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "lateral, vertical, perpendicular, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the drawings, and are only for the convenience of describing the present application and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the device or element referred to must have a specific direction or be constructed and operated in a specific direction, and therefore cannot be understood as limiting the scope of protection of the present application; the directional words "inside and outside" refer to the inside and outside relative to the contours of each component itself.

[0056] In the description of the present application, it should be understood that the use of terms such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be understood as limiting the scope of protection of the present application.

[0057] In addition, the technical features involved in the different embodiments of the present application described below can be combined with each other as long as they do not conflict with each other.

[0058] Figure 1-Figure 8 The air conditioning system and control method thereof of the present application are exemplarily shown.

[0059] See also Figure 1 The air conditioning system includes a terminal 1, a water supply pipe 2 and a water return pipe 3. When working, the supply water enters through the water supply pipe 2, and the return water flows through the terminal 1 through the water return pipe 3 and then flows out. Generally, the air conditioning system includes a plurality of (i.e., at least two, for example, at least three) terminals 1, and these terminals 1 are connected to the water return pipe 3 in parallel with each other, so that the return water can flow through each terminal 1 and then flow out.

[0060] Typically, each terminal 1 is equipped with a water valve (not shown) to control the water flow of each terminal 1. By adjusting the opening of the water valve of the terminal 1, the water flow of the terminal 1 can be adjusted. In some embodiments, the water valve of the terminal 1 is a proportional valve.

[0061] To improve the energy efficiency and comfort of air conditioning systems, see Figure 2 , the control method provided in this application includes:

[0062] Determine the temperature parameter ΔT, which includes the supply air temperature difference ΔT f Or supply and return water temperature difference ΔT s , supply air temperature difference ΔT f is the actual value of the supply air temperature T at the end 1 of the air conditioning system f1 The preset value of supply air temperature T f2 The difference (ie, ΔT f = Actual value of supply air temperature T f1 -Preset value of supply air temperature T f2 ), supply and return water temperature difference ΔT s is the actual value of the supply and return water temperature difference of the air conditioning system T s1 The preset value T of the supply and return water temperature difference s2 The difference (ΔT s = Actual value of supply and return water temperature difference T s1 -Preset value of supply and return water temperature difference T s2 );

[0063] Based on the determined temperature parameter ΔT, determining the adjustment step |D1|%;

[0064] According to the determined adjustment step |D1|%, the opening of the water valve at the end 1 of the air-conditioning system is adjusted.

[0065] Based on the above steps, the air-conditioning system no longer adopts a fixed flow control method, but a variable flow control method. By adjusting the opening of the water valve at the terminal 1, the water flow at the terminal 1 can be regulated as needed, and can be changed according to different loads and different comforts, effectively meeting the needs of different loads and different comforts. Therefore, the energy saving and comfort of the air-conditioning system can be effectively improved.

[0066] In particular, the variable flow control scheme includes the air supply temperature difference ΔT f Or supply and return water temperature difference ΔT s The temperature parameter ΔT is used to adjust the water valve opening of terminal 1, and the air supply temperature difference ΔT f Or supply and return water temperature difference ΔT s It can effectively reflect the changes in actual demands such as load and comfort, and therefore is conducive to achieving a more accurate variable flow control process, thereby more effectively improving the energy saving and comfort of the air-conditioning system.

[0067] Among them, according to the supply air temperature difference ΔT f The temperature parameter ΔT is used to adjust the water valve opening of terminal 1, which is beneficial to make the terminal water flow rate follow the air supply temperature difference ΔT f changes, so that the supply air temperature is stabilized at the preset value (i.e., the actual supply air temperature value T f1 The preset value of supply air temperature T f2 Roughly equal, the difference between the two is ΔT f Within the allowable range), accurately control temperature and humidity, prevent over-dehumidification and over-cooling, effectively meet indoor temperature and humidity requirements, improve indoor comfort, and reduce energy consumption. Taking night as an example, due to the temperature difference between day and night, the temperature at night will be lower, the indoor load will be reduced, and the human body's demand for temperature and humidity will also change compared to daytime. In this case, according to the air supply temperature difference ΔT f To adjust the opening of the water valve at terminal 1, the opening of the water valve at terminal 1 can be dynamically adjusted with the changes in indoor load and comfort. This can reduce terminal energy consumption while meeting comfort requirements, thereby effectively improving the energy saving and comfort of the air-conditioning system.

[0068] According to the supply and return water temperature difference ΔT s The temperature parameter ΔT is used to adjust the water valve opening of the terminal 1, which is conducive to making the terminal water flow rate follow the supply and return water temperature difference ΔT s Changes, so that the supply and return water temperature difference is stable at the set value (that is, the actual value of the supply and return water temperature difference T s1 The preset value T of the supply and return water temperature difference s2 Roughly equal, the difference between the two is ΔT s Within the allowable range), it can effectively meet the current indoor temperature and humidity requirements, improve indoor comfort, and reduce terminal energy consumption. Therefore, it can effectively improve the energy saving and comfort of the air-conditioning system.

[0069] It can be seen that the above scheme, by including the air supply temperature difference ΔT f Or supply and return water temperature difference ΔT s The temperature parameter ΔT is used to determine the opening adjustment step |D1|% of the terminal water valve 1. The opening of the terminal water valve 1 can be dynamically adjusted to easily realize accurate variable flow control, flexibly meet the needs of different loads and different comfort, and effectively improve the energy saving and comfort of the air-conditioning system.

[0070] In some embodiments, based on the determined temperature parameter ΔT, determining the adjustment step |D1|% comprises:

[0071] Determining a D value based on the determined temperature parameter ΔT;

[0072] Based on the determined D value, an adjustment step |D1|% is determined.

[0073] The above scheme includes the air supply temperature difference ΔT f Or supply and return water temperature difference ΔT s When the temperature parameter ΔT is used to adjust the water valve opening of the terminal 1, the D value is first determined according to the determined temperature parameter ΔT, so that D becomes a function with the temperature parameter ΔT as a variable, that is, D = f 1 (ΔT), and then determine the adjustment step |D1|% according to the determined D value, and then adjust the opening of the terminal 1 water valve according to the determined adjustment step |D1|%. This makes the terminal water valve opening adjustment step |D1|% and the supply air temperature difference ΔT f Or supply and return water temperature difference ΔT s Related, with the supply air temperature difference ΔT f Or supply and return water temperature difference ΔT s In this way, the entire opening adjustment process is simpler, more convenient and more accurate. It is not only more feasible, but also can achieve a more accurate dynamic adjustment process, and more effectively improve the energy saving and comfort of the air-conditioning system.

[0074] In the above solution, there are many specific ways to determine the D value according to the determined temperature parameter ΔT.

[0075] For example, in some embodiments, determining the D value based on the determined temperature parameter ΔT includes: determining the D value based on ΔT*a, where a is a correction coefficient, a>0, for example, a≥0.5.

[0076] The above scheme, when determining D based on the temperature parameter ΔT, not only takes the temperature parameter ΔT into consideration, but also uses a correction coefficient a greater than 0 to correct and compensate the temperature parameter ΔT. This is conducive to obtaining a D value and |D1|% value that are more in line with the actual situation, and realizing a dynamic adjustment process of water flow that is more in line with actual needs. Therefore, it is more conducive to improving the energy saving and comfort of the air-conditioning system.

[0077] The size of a can be set according to actual conditions.

[0078] As an example, a>1. At this time, a is used to correct and compensate the temperature parameter ΔT, and the originally smaller ΔT (for example, when the terminal 1 is running at a small flow rate, the actual value of the supply air temperature T f1 The preset value of supply air temperature T f2 The difference ΔT f And the actual value of the supply and return water temperature difference T s1 The preset value T of the supply and return water temperature difference s2 The difference ΔT s Small, that is, ΔT is small) to prevent the failure to respond in time due to ΔT being too small, resulting in inaccurate adjustment and control failure, which affects the reliability of variable flow control. Therefore, when a> When it is 1, it can effectively adapt to the characteristics of low flow rate operation at the end, obtain the D value and |D1|% value that better meet the actual needs of the end with low flow rate operation, realize the dynamic adjustment process of water flow rate more in line with the low flow rate operation situation, improve the situation of inaccurate regulation or even control failure during low flow rate operation, improve the accuracy and reliability of the variable flow rate adjustment process, realize a more accurate and reliable variable flow rate adjustment process, and more effectively improve the energy efficiency and comfort of the air conditioning system.

[0079] Among them, according to different situations, a can take different values within a range greater than 1.

[0080] Exemplarily, in some embodiments, 1 < a ≤ 10. For example, 1 < a ≤ 5, or 5 < a ≤ 10. Specifically, for example, a is 2, 3, 4, 4.5, 6, 7, 8, or 9, etc. At this time, the value of a is more appropriate, can meet the flow rate adjustment requirements in most low flow rate operation situations, magnify ΔT to a more appropriate degree, and more effectively improve the energy efficiency and comfort of the air conditioning system.

[0081] Again, for example, in some embodiments, based on the determined temperature parameter ΔT, determining the D value includes: determining the D value based on f(ΔT) + f(P). Wherein, f(ΔT) is a function with ΔT as the variable; f(P) is a function with P as the variable. When ΔT includes the supply air temperature difference ΔT f , P is the actual value T of the current supply air temperature f1 and the actual value T of the supply air temperature 1 before the preset time t f1 The difference, that is, P = the actual value T of the current supply air temperature f1 - the actual value T of the supply air temperature 1 before the preset time t f1 , when ΔT includes the difference ΔT between the supply and return water temperature differences s , P is the actual value T of the current supply and return water temperature difference s1 and the actual value T of the supply and return water temperature difference 2 before the preset time t s1 The difference, that is, P = the actual value T of the current supply and return water temperature difference s1 - the actual value T of the supply and return water temperature difference 2 before the preset time t s1 .

[0082] In the above solution, when determining D based on the temperature parameter ΔT, not only the temperature parameter ΔT is considered, but also the change in the supply air temperature before and after the preset time t 1 or the difference between the supply and return water temperatures before and after the preset time t (that is, the return water temperature T 2 - the supply water temperature T 回 can be characterized 供) based on which the determined D value is not only related to the difference between the actual value and the preset value of the supply air temperature or the supply and return water temperature difference, but also related to the change of the supply air temperature or the supply and return water temperature difference within the preset time, so that the subsequent terminal water valve opening adjustment step |D1|% is affected by both the difference between the actual value and the preset value of the supply air temperature or the supply and return water temperature difference and the change of the supply air temperature or the supply and return water temperature difference within the preset time, thereby realizing a variable flow regulation process which comprehensively considers the deviation between the actual value and the preset value of the supply air temperature or the supply and return water temperature difference and the change of the supply air temperature or the supply and return water temperature difference within the preset time. This is conducive to further improving the accuracy and reliability of the variable flow regulation process, so that the terminal flow can be more accurately and reliably adjusted dynamically with the different needs of indoor load and comfort, and therefore, is more conducive to improving the energy saving and comfort of the air-conditioning system.

[0083] Moreover, from another perspective, determining the D value based on f(ΔT)+f(P) is equivalent to using f(P) to correct and compensate the D value determined based on f(ΔT). This is conducive to obtaining a D value and |D1|% value that are more in line with the actual situation, and realizing a dynamic adjustment process of water flow that is more in line with actual needs. Therefore, it is more conducive to improving the energy saving and comfort of the air-conditioning system.

[0084] It can be seen that determining the D value based on f(ΔT)+f(P) is conducive to further improving the energy saving and comfort of the air-conditioning system.

[0085] Among them, f(ΔT) and f(P) can be in various forms.

[0086] For example, in some embodiments, f(ΔT)=ΔT*γ. Wherein, γ is a correction coefficient, and γ>0. At this time, using the correction coefficient γ to correct and compensate the temperature parameter ΔT is conducive to obtaining a D value and |D1|% value that are more in line with the actual situation, and realizing a dynamic adjustment process of water flow that is more in line with actual needs, thereby helping to improve the energy saving and comfort of the air-conditioning system. In particular, the correction coefficient γ can be used together with f(P) to correct and compensate the temperature parameter ΔT, and more effectively prevent inaccurate adjustment and control failure, thereby helping to further improve the accuracy and reliability of the variable flow adjustment process.

[0087] The size of γ can be set according to actual conditions.

[0088] As an example, γ≥0.5. At this time, the size of γ is appropriate and not too small, which is conducive to better correction and compensation of ΔT, obtaining a D value and |D1|% value that are more in line with the actual situation, realizing a dynamic adjustment process of water flow that is more in line with actual needs, and better improving the energy saving and comfort of the air-conditioning system.

[0089] Furthermore, in some embodiments, γ>1. At this time, by using γ to correct and compensate the temperature parameter ΔT, the originally small ΔT can be amplified to prevent the failure to respond in time due to too small ΔT, inaccurate regulation and control failure, etc., which affect the reliability of variable flow control, thereby achieving a more accurate and reliable variable flow regulation process.

[0090] According to different situations, γ can take different values ​​within a range greater than 1. Exemplarily, in some embodiments, 1<γ≤10, for example, 1<γ≤5, or, 5<γ≤10, specifically, for example, γ is 1.1, 1.2, 1.3, 1.5, 2, 3, 4, 4.5, 6, 7, 8 or 9, etc. At this time, the size of γ is more appropriate, and ΔT can be appropriately enlarged, which can not only meet the flow regulation requirements under most small flow operation conditions, but also appropriately enlarge ΔT to prevent inaccurate regulation and control failure, etc., and not over-enlarge it, resulting in over-regulation. Therefore, it is beneficial to improve the accuracy and reliability of variable flow regulation and improve the energy saving and comfort of the air-conditioning system.

[0091] In addition, in some embodiments, f(P)=P*δ. Wherein, δ is a correction coefficient, δ>0. At this time, using a correction coefficient δ greater than 0 to correct and compensate the parameter P is conducive to obtaining a D value and |D1|% value that are more in line with the actual situation, and realizing a dynamic adjustment process of water flow that is more in line with actual needs. Therefore, it is more conducive to improving the energy saving and comfort of the air-conditioning system.

[0092] For example, in some embodiments, δ>1. In this case, by using δ to correct and compensate the parameter P, the originally small P value can be amplified to prevent the situation that the P value is too small, which leads to the inability to respond in time, inaccurate adjustment and control failure, etc., affecting the reliability of variable flow control. 1 Internal air supply temperature or preset time t 2 The change of the internal supply and return water temperature difference is small, so the P value is generally small. Therefore, setting δ to be greater than 1 can effectively adapt to the characteristics of the small P value under normal circumstances, prevent inaccurate adjustment or even control failure, improve the accuracy and reliability of the variable flow regulation process, achieve a more accurate and reliable variable flow regulation process, and effectively improve the energy saving and comfort of the air-conditioning system.

[0093] Further, in some embodiments, δ = b * c. Herein, both b and c are correction factors, where 2 < b ≤ 10 and 0.5 ≤ c ≤ 10. In this way, δ can be greater than 1 to amplify P, and at the same time, δ can be less than or equal to 100, so as not to be too large to over-amplify P and cause excessive adjustment. That is to say, at this time, the magnitude of δ is appropriate, and P can be amplified to an appropriate extent to achieve a more reasonable correction of P, enabling more accurate and reliable dynamic adjustment of the flow rate, and further improving the energy efficiency and comfort of the air-conditioning system.

[0094] Furthermore, in some embodiments, 2 < b ≤ 6; and / or, 0.5 ≤ c ≤ 5. At this time, the magnitudes of b and c are more appropriate. Correspondingly, the magnitude of δ is more appropriate, and P can be amplified to a more appropriate extent, enabling more accurate and reliable flow rate adjustment at a more appropriate frequency, thereby more effectively improving the energy efficiency and comfort of the air-conditioning system.

[0095] As described above, P is a parameter characterizing the change in the supply air temperature before and after the preset time t 1 or the change in the supply-return water temperature difference before and after the preset time t 2 wherein the values of t 1 and t 2 can be set according to the actual situation.

[0096] For example, in some embodiments, 5s ≤ t 1 ≤ 30s. At this time, the value of t 1 is more appropriate. The time is neither too short nor too long, facilitating the acquisition of the parameter P that can effectively characterize the change in the supply air temperature over time, and realizing a more practical flow rate dynamic adjustment process.

[0097] Specifically, in some embodiments, 10s ≤ t 1 ≤ 30s. At this time, the value of t 1 is more appropriate, which is more conducive to obtaining the parameter P that can effectively characterize the change in the supply air temperature over time, and realizing a more practical flow rate dynamic adjustment process.

[0098] In addition, in some embodiments, 5s ≤ t 2 ≤ 30s. At this time, the value of t 2 is more appropriate. The time is neither too short nor too long, facilitating the acquisition of the parameter P that can effectively characterize the change in the supply-return water temperature difference over time, and realizing a more practical flow rate dynamic adjustment process.

[0099] Specifically, in some embodiments, 10s ≤ t 2 ≤ 30s. For example, t 2 is 10s, 15s, 20s or 25s. At this time, t 2The value of is more appropriate, which is more conducive to obtaining the parameter P that can effectively characterize the change of the supply and return water temperature difference over time, and realize a dynamic flow adjustment process that is more in line with actual needs.

[0100] In the aforementioned embodiments, based on the determined D value, determining the adjustment step |D1|% includes:

[0101] When 0<|D|<1, the adjustment step |D1|% is determined as a constant c; and / or,

[0102] When |D|≥1, the adjustment step |D1|% is determined as |D|%.

[0103] Among them, |D|≥1, indicating that the gap between the actual value of the supply air temperature or the supply and return water temperature difference at the terminal 1 and the preset value is large. In this case, the requirement for the adjustment speed is higher. Therefore, the adjustment step |D1|% is determined to be |D|%, which can quickly adjust the water flow to meet the actual load and comfort requirements, better improve comfort and reduce energy consumption.

[0104] 0<|D|<1, which means that the gap between the actual value of the supply air temperature or the supply and return water temperature difference at the terminal 1 and the preset value is small, and the actual value of the water flow rate does not deviate much from the actual demand. In this case, the requirements for the adjustment speed and adjustment accuracy can be appropriately reduced. Therefore, the adjustment step |D1|% is determined as a constant c, which can effectively simplify the adjustment process and achieve a simpler variable flow adjustment process while meeting the requirements of the actual load and comfort for the adjustment speed and adjustment accuracy.

[0105] The size of the constant c can be set according to actual conditions.

[0106] For example, in some embodiments, 0.3%≤c≤0.8%. In this way, the adjustment step |D1|% when 0<|D|<1 can be greater than or equal to 0.3% and less than or equal to 0.8%, that is, 0.3%≤|D1|%≤0.8%. At this time, the size of the adjustment step |D1|% is relatively appropriate, neither too large nor too small, which is conducive to realizing a relatively simple and relatively accurate variable flow adjustment process.

[0107] Furthermore, in some embodiments, 0.5%≤c≤0.8%. At this time, 0.5%≤|D1|%≤0.8%, and the adjustment step|D1|% is more appropriate, which is conducive to realizing a simpler and more accurate variable flow adjustment process.

[0108] In the above embodiments, when the opening of the water valve at the terminal 1 of the air-conditioning system is adjusted according to the determined adjustment step |D1|%, the opening of the water valve at the terminal 1 of the air-conditioning system can be adjusted once every interval Δt. In this way, the frequency of regulation can be reduced, which is not only conducive to preventing the water valve at the terminal 1 from moving back and forth and affecting its service life, but also conducive to simplifying the control process and reducing costs.

[0109] Among them, Δt can be set according to actual conditions.

[0110] As an example, in some embodiments, 3s≤Δt≤20s, for example, 3s-5s, or 5s-20s, specifically, for example, 4, 6, 9, 10, 13, 15, 18 or 19s, etc. At this time, the size of Δt is more appropriate, the action frequency is more appropriate, and it is more conducive to extending the life of the terminal water valve, simplifying the control process, and reducing costs.

[0111] In the above embodiment, adjusting the opening of the water valve at the end 1 of the air conditioning system according to the determined adjustment step |D1|% includes:

[0112] When D>0, increase the opening of the water valve at the end 1 of the air conditioning system by |D1|%;

[0113] When D<0, the opening of the water valve at the end 1 of the air-conditioning system is reduced by |D1|%.

[0114] In the above steps, whether D is greater than 0 is used as the dividing line for whether the terminal water valve is adjusted up or down. Whether D is greater than 0 can indicate whether the actual heat exchange at the terminal 1 is higher or lower than the actual demand. > When D is 0, it indicates that the indoor load is large and the current actual heat exchange cannot meet the indoor heat exchange demand. In other words, the actual heat exchange at the terminal 1 is lower than the actual demand. In this case, increasing the opening of the water valve at the terminal 1 can increase the water flow rate and increase the actual heat exchange, which is consistent with the actual demand. < When the value is 0, it indicates that the indoor load is small and the current actual heat exchange exceeds the indoor heat exchange demand. In other words, the actual heat exchange at terminal 1 is higher than the actual demand. In this case, reducing the opening of the water valve at terminal 1 can reduce the water flow and reduce the actual heat exchange, which is consistent with the actual demand.

[0115] It can be seen that in the above steps, whether D is greater than 0 is used as the dividing line for whether the end water valve is adjusted up or down, which can adjust the actual heat exchange amount to be consistent with the actual demand, effectively improving energy saving and comfort.

[0116] In the aforementioned embodiments, determining the temperature parameter ΔT may include:

[0117] After the water valve at the end 1 of the air conditioning system is opened, after a delay time t, the supply air temperature at the end 1 of the air conditioning system is detected as the actual value T of the supply air temperature at the end 1 of the air conditioning system f1 Alternatively, the return water temperature and the supply water temperature of the terminal 1 of the air-conditioning system are detected, and the difference between the return water temperature and the supply water temperature of the terminal 1 of the air-conditioning system is used as the actual value T of the supply and return water temperature difference of the terminal 1 of the air-conditioning system. s1 ;

[0118] The actual value of the supply air temperature T at the end 1 of the air conditioning system f1 The preset value of supply air temperature T f2 The difference between the supply air temperature difference ΔT f , and the supply air temperature difference ΔT f Determine as the temperature parameter ΔT, or, the actual value of the supply and return water temperature difference T at the end 1 of the air conditioning system s1 The preset value T of the supply and return water temperature difference s2 The difference between the supply and return water temperatures is taken as the supply and return water temperature difference ΔT s , and the supply and return water temperature difference ΔT s Determined as the temperature parameter ΔT.

[0119] In the above steps, the supply air temperature or the supply and return water temperature is not detected immediately after the terminal water valve is opened, but the supply air temperature or the supply and return water temperature is detected after a delay time t. In this way, it can prevent the supply air temperature or the supply and return water temperature from fluctuating greatly due to the initial stage of the water valve opening, when the terminal 1 has not yet worked stably, thereby affecting the detection accuracy. Therefore, it is conducive to detecting and obtaining a more accurate supply air temperature or supply and return water temperature, and then obtaining a more accurate temperature parameter ΔT. In this way, it is conducive to achieving a more accurate variable flow regulation process and more effectively improving energy saving and comfort.

[0120] The delayed time t can be set according to actual conditions.

[0121] As an example, 30s≤t≤90s, for example, 30s≤t<60s, or 60s≤t≤90s, specifically, for example, t is 40, 45, 50, 52, 55, 63, 65, 68, 70, 75, 80, 85s, etc. At this time, the delay time t is more appropriate, which is conducive to detecting and obtaining more accurate supply air temperature or supply and return water temperature under a stable working state, and is also conducive to preventing delay for too long, which leads to untimely adjustment, waste of energy, and impact on comfort.

[0122] As a further improvement to the above embodiments, see Figure 1 In some embodiments, the control method further comprises:

[0123] Divide the multiple terminals 1 of the air conditioning system into multiple control zones 5, so that the total rated flow of each control zone 5 in the multiple control zones 5 is consistent;

[0124] Based on the pressure difference of each control zone 5, the opening of the main water valve of each control zone 5 is adjusted to keep the pressure difference of each control zone 5 stable.

[0125] In the above steps, according to the flow rate of the terminal 1, the zoning control is performed so that the total rated flow rate of each control area 5 is basically the same, and the opening of the main water valve of each control area 5 (located on the main line of each control area 5 and used to control the total water flow of each control area 5) is adjusted based on the pressure difference of each control area 5, so that the pressure difference of each control area 5 is kept stable, which can prevent the pressure difference of each control area 5 from fluctuating too much and causing local water imbalance. This method of monitoring and adjusting the pressure difference by zoning can realize the controllable regulation of the overall water channel, optimize the water flow, reduce energy consumption, improve energy efficiency, and improve the reliability of system operation.

[0126] The control methods of the above-mentioned embodiments can be completed under the control of a controller of the air conditioning system. The corresponding controller includes a memory and a processor coupled to the memory, and the processor is configured to execute the control method of any embodiment based on the instructions stored in the memory.

[0127] In addition, the present application also provides a storage medium, and the corresponding storage medium stores computer instructions, and the computer instructions are executed by a processor to implement the control method of any embodiment.

[0128] Next, combine Figure 1-Figure 2 The embodiments shown are used to further illustrate the present application.

[0129] like Figure 1 As shown, in this embodiment, the air conditioning system is a HVAC system, which includes a plurality of terminals 1, which are divided into two control areas 5, each of which includes a plurality of terminals 1 connected in parallel, and the rated flow rates of the various control areas 5 are substantially the same (the same, or different, but the deviation is within the allowable range, for example, the deviation is within ±5%). Specifically, Figure 1 The first control area 5 on the left side includes 5 terminals 1, and the rated flow rates of the 5 terminals 1 are q1, q2, q3, q4 and q5 respectively. The total rated flow rate Q1 of the first control area 5 is the sum of the rated flow rates of the 5 terminals 1, that is, Q1=q1+q2+q3+q4+q5. At the same time, the total pressure difference of the first control area 5 (that is, the pressure difference from the water inlet to the water outlet of the corresponding control area 5) is △P1, and the flow adjustment range is 20%~30%Q1~Q1. In addition, Figure 1The second control area 5 located on the right side includes four terminals 1, and the rated flow rates of the four terminals 1 are q1, q5, q4 and q5 respectively. The total rated flow rate Q2 of the second control area 5 is the sum of the rated flow rates of the four terminals 1, that is, Q2 = q1 + q5 + q4 + q5, Q2 is consistent with Q1, and the total pressure difference of the second control area 5 is ΔP2, and the flow adjustment range is 20% ~ 30% Q2 ~ Q2. Among them, each control area 5 is equipped with a main water valve (not shown) located on the main road, and at the same time, each terminal 1 of each control area 5 is equipped with a water valve (not shown) located on the branch road where the corresponding terminal 1 is located. The main water valve and the water valve of the terminal 1 are both proportional valves. In addition, each control area 5 is also equipped with a pressure difference control device 4 for detecting and controlling the total pressure difference of each control area 5. At the same time, each terminal 1 is provided with a temperature measuring component (such as a temperature sensing package) to detect the outlet air temperature, return water temperature and supply water temperature in real time.

[0130] Based on the above settings, this embodiment uses the supply air temperature difference ΔT f And the supply and return water temperature difference ΔT s , variable flow regulation is performed on each terminal 1 so that each terminal 1 can effectively meet the needs of different loads and different comforts. Moreover, during the variable flow regulation process, the pressure difference of each control area 5 is monitored and adjusted to achieve the goals of energy saving and emission reduction, and improving comfort and reliability.

[0131] Next, according to the supply air temperature difference ΔT f The variable flow rate adjustment mode (which can be called the supply air temperature difference control variable flow rate adjustment operation mode) is based on the supply and return water temperature difference ΔT s The variable flow regulation mode (which may be called the supply and return water temperature difference control variable flow regulation operation mode) and the zoning control process are introduced.

[0132] First, the supply air temperature difference control variable flow regulation operation mode is introduced.

[0133] In this operation mode, according to the supply air temperature difference ΔT f , adjust the opening of the water valve at the end 1, and adjust it every 5s.

[0134] After entering this operation mode, the water valve of terminal 1 is opened, and the supply air temperature detection is started after a delay of 60s to obtain the actual value T of the supply air temperature of terminal 1. f1 ;

[0135] According to the formula, the air supply temperature difference ΔT f = Actual value of supply air temperature T f1 -Preset value of supply air temperature T f2 , determine the supply air temperature difference ΔT f , and according to the formula P = actual value of supply air temperature T f1- Actual value of the supply air temperature T before - 10s f1 , determine parameter P;

[0136] According to the formula D = ΔT f *γ + P * b * c, calculate the value of D, where 1 < γ ≤ 10, b = 6, 0.5 < c ≤ 10;

[0137] According to the calculated value of D, determine whether to increase or decrease the water valve of terminal 1, and determine the adjustment increment each time, that is, the adjustment step |D1|%.

[0138] Specifically, judge whether the value of D is greater than 0 to determine whether to increase or decrease the opening of the water valve of terminal 1, and judge whether |D| is greater than or equal to 1 to determine the size of the adjustment step |D1|%.

[0139] More specifically, when D > 0, the actual value of the supply air temperature T f1 > preset value of the supply air temperature T f2 , the indoor temperature has not dropped to the required temperature, the indoor load is large, and the current heat exchange capacity cannot meet the actual heat exchange demand. Therefore, increase the opening of the water valve 1, and determine the adjustment step |D1|% for each increase as follows:

[0140] When 0 < D < 1, the actual value of the supply air temperature T f1 and the preset value of the supply air temperature T f2 The difference between them is small. At this time, determine the adjustment step |D1|% as 0.5%, that is, increase the opening of the water valve of terminal 1 in steps of 0.5%;

[0141] When D ≥ 1, the actual value of the supply air temperature T f1 and the preset value of the supply air temperature T f2 The difference between them is large. At this time, determine the adjustment step |D1|% as |D|%, that is, increase the opening of the water valve of terminal 1 in steps of |D|% to make the actual heat exchange capacity quickly and infinitely approach the actual heat exchange demand.

[0142] When D > 0, the actual value of the supply air temperature T f1 <preset value of the supply air temperature T f2 , the indoor load is small, the current heat exchange capacity has exceeded the actual heat exchange demand, the indoor temperature has dropped below the required temperature, the indoor is in a supercooled state, there is a risk of condensation, and there is unnecessary energy waste, which will also bring an uncomfortable experience. Therefore, decrease the opening of the water valve 1, and determine the adjustment step |D1|% for each decrease as follows:

[0143] When - 1 < D < 0, the actual value of the supply air temperature T f1 and the preset value of the supply air temperature T f2The difference between them is small. At this time, the adjustment step |D1|% is determined to be 0.5%, that is, the water valve opening of the end 1 is reduced according to the step of 0.5%;

[0144] When D≤-1, the actual value of the supply air temperature is T f1 The preset value of supply air temperature T f2 The difference between them is large. At this time, the adjustment step |D1|% is determined to be |D|%, that is, the water valve opening of the end 1 is reduced according to the step of |D|%, so that the actual heat exchange amount quickly and infinitely approaches the actual heat exchange demand.

[0145] It can be seen that in this embodiment, the supply air temperature difference controls the variable flow rate adjustment operation mode, by collecting the supply air temperature, determining the difference between it and the set value, and compensating and correcting the terminal water valve adjustment step according to the difference, adjusting the terminal water valve opening, and controlling the water flow rate, the flow rate can be dynamically adjusted with the load size to achieve the indoor load processing target set value. In this way, the temperature and humidity can be accurately controlled, the problem of over-dehumidification and over-refrigeration can be effectively solved, the indoor comfort can be improved, and the terminal energy consumption can be reduced. The corresponding effect is Figure 3-Figure 6 There is a direct reflection in it.

[0146] Figure 3-Figure 4 as well as Figure 5-Figure 6 The air supply and heat exchange conditions when the traditional control method and the air supply temperature difference control method of this embodiment are respectively shown.

[0147] Depend on Figure 3 and Figure 5 It can be seen that the case where the preset value of the supply air temperature is 14° C. is used as an example for explanation here.

[0148] like Figure 3 and Figure 4 As shown, when the traditional control method is adopted, the terminal 1 has a slow feedback during operation. After it runs continuously for a period of time, the indoor load decreases, and the supply air temperature deviates negatively from the preset value and the actual heat exchange deviates from the indoor load. This is overcooling and part of the energy consumption is unnecessary. After the outdoor unit receives the signal and performs frequency conversion adjustment, the system can gradually stabilize and meet the indoor load demand again. Such an operation process is not energy-efficient and has a certain lag, which affects comfort.

[0149] And as Figure 5 and Figure 6 As shown, when the supply air temperature difference control method of this embodiment is adopted, the water valve opening is adjusted according to the supply air temperature difference to realize the flow regulation process with the supply air temperature as the target. The system can adjust the flow size as the real-time indoor load changes, so that the supply air temperature and the actual heat exchange amount are infinitely close to and stable at the set value.

[0150] Compare Figure 3 and Figure 5 as well as Figure 4 and Figure 6 It can be seen that, compared with the conventional method, after adopting the supply air temperature difference control method of this embodiment, the deviation between the actual value and the set value of the supply air temperature, as well as the deviation between the actual heat exchange amount and the indoor load, are effectively reduced, and the consistency is effectively enhanced. Therefore, the comfort can be effectively improved, the energy consumption can be reduced, and the energy saving performance can be improved.

[0151] Next, the variable flow regulation operation mode of the supply and return water temperature difference control is introduced.

[0152] In this operation mode, according to the supply and return water temperature difference ΔT s , the opening degree of the water valve of terminal 1 is adjusted, and it is adjusted once every 5 s.

[0153] After entering this operation mode, the water valve of terminal 1 is opened, and the detection of the supply and return water temperatures starts after a delay of 60 s;

[0154] According to the formula "supply and return water temperature difference = return water temperature - supply water temperature", the actual value T of the supply and return water temperature difference is calculated s1 , and according to the formula for the supply and return water temperature difference ΔT s = actual value T of the supply and return water temperature difference s1 - preset value T of the supply and return water temperature difference s2 , the supply and return water temperature difference ΔT s is calculated. Moreover, according to the formula P = actual value T of the supply and return water temperature difference s1 - actual value T of the supply and return water temperature difference 10 s ago s1 , the parameter P is determined;

[0155] According to the formula D = ΔT f *γ + P * b * c, the value of D is calculated, where 1 < γ ≤ 10, 1b = 6, 0.5 ≤ c ≤ 10;

[0156] According to the calculated value of D, it is determined whether the water valve of terminal 1 is to be adjusted larger or smaller, and the adjustment increment each time, that is, the adjustment step |D1|%, is determined.

[0157] Specifically, it is judged whether the value of D is greater than 0 to determine whether to adjust the opening degree of the water valve of terminal 1 larger or smaller, and it is judged whether |D| is greater than or equal to 1 to determine the size of the adjustment step |D1|%.

[0158] More specifically, when D > 0, the actual value T of the supply and return water temperature difference s1 > preset value T of the supply and return water temperature difference s2 , the indoor load is large, and the current heat exchange amount cannot meet the actual heat exchange demand. Therefore, the opening degree of water valve 1 is adjusted larger, and the adjustment step |D1|% for each larger adjustment is determined as follows:

[0159] When 0 < D < 1, the actual value T of the supply and return water temperature differences1 The preset value T of the supply and return water temperature difference s2 The difference between them is small. At this time, the adjustment step |D1|% is determined to be 0.5%, that is, the water valve opening of the end 1 is increased according to the step of 0.5%;

[0160] When D≥1, the actual value of the supply and return water temperature difference is T s1 The preset value T of the supply and return water temperature difference s2 The difference between them is large. At this time, the adjustment step |D1|% is determined to be |D|%, that is, the water valve opening of the end 1 is increased according to the step of |D|%, so that the actual heat exchange amount quickly and infinitely approaches the actual heat exchange demand.

[0161] When D>0, the actual value of the supply and return water temperature difference is T s1 >Preset value of supply and return water temperature difference T s2 , the indoor load is small, and the current heat exchange has exceeded the actual heat exchange demand. Therefore, the opening of water valve 1 is reduced, and the adjustment step |D1|% of each reduction is determined as follows:

[0162] When -1<D<0, the actual value of the supply and return water temperature difference is T s1 The preset value T of the supply and return water temperature difference s2 The difference between them is small. At this time, the adjustment step |D1|% is determined to be 0.5%, that is, the water valve opening of the end 1 is reduced according to the step of 0.5%;

[0163] When D≤-1, the actual value of the supply and return water temperature difference is T s1 The preset value T of the supply and return water temperature difference s2 The difference between them is large. At this time, the adjustment step |D1|% is determined to be |D|%, that is, the water valve opening of the end 1 is reduced according to the step of |D|%, so that the actual heat exchange amount quickly and infinitely approaches the actual heat exchange demand.

[0164] It can be seen that in this embodiment, the supply and return water temperature difference controls the variable flow regulation operation mode, by collecting the indoor supply and return water temperatures, calculating the real-time supply and return water temperature difference, determining the difference between the temperature difference and the set value, and compensating and correcting the terminal water valve adjustment step according to the difference, adjusting the terminal water valve opening, and controlling the water flow rate, the flow rate can be dynamically adjusted with the load size to achieve the indoor load processing target setting value, so that energy consumption can be reduced and indoor comfort can be improved. The corresponding effect is Figure 7-Figure 8 There is a direct reflection in it.

[0165] Figure 7 and Figure 8 The supply and return water temperature differences when the traditional control method and the supply and return water temperature difference control method of this embodiment are respectively shown.

[0166] Depend on Figure 7 and Figure 8It can be seen that the case where the preset value of the supply and return water temperature difference is 5° C. (for example, the supply water temperature is 12° C. and the return water temperature is 17° C.) is used as an example for explanation.

[0167] like Figure 7 As shown, when the traditional control method is used, there is a lag, and the actual value of the supply and return water temperature difference at the end 1 will deviate greatly from the preset value, causing overcooling and condensation problems, affecting comfort, and wasting energy.

[0168] And as Figure 8 As shown, when the supply and return water temperature difference control method of this embodiment is adopted, the water valve opening is adjusted according to the supply and return water temperature difference, so as to realize the flow regulation process with the supply and return water temperature difference as the target, so that the terminal can adjust the flow size as the real-time indoor load changes, so that the actual value of the supply and return water temperature difference is infinitely close to and stabilized at the set value.

[0169] Compare Figure 7 and Figure 8 It can be seen that compared with the conventional method, after adopting the supply and return water temperature difference control method of this embodiment, the deviation between the actual value of the supply and return water temperature difference and the set value is effectively reduced, and the consistency is effectively enhanced. Therefore, it can effectively improve comfort, reduce energy consumption, and improve energy saving.

[0170] The above-mentioned supply air temperature difference control variable flow rate regulation operation mode and supply and return water temperature difference control variable flow rate regulation operation mode can be selected according to actual needs to achieve variable flow rate control.

[0171] Next, we will introduce partition control.

[0172] When the terminal flow is dynamically adjusted, the pressure difference of each control area 5 is monitored, and the actual value of the pressure difference of each control area 5 is compared with the set value. When a discrepancy occurs, the opening of the main water valve of the corresponding control area 5 is adjusted. Specifically, if the pressure difference is too large, the opening of the main water valve is reduced to reduce the pressure difference. Conversely, if the pressure difference is too small, the opening of the main water valve is increased to increase the pressure difference. In this way, the overall pressure difference of the system is maintained stable.

[0173] Whether the pressure difference of each control area 5 is stable is related to whether the hydraulic power of each control area 5 is balanced. The stronger the pressure difference stability, the higher the hydraulic balance. If the hydraulic power is unbalanced, the same driving force may not be able to drive the required amount of water into the control area 5, affecting the flexibility and response speed of the variable flow regulation process, and affecting comfort, energy saving and reliability. Therefore, corresponding zoning control can reduce the problem of hydraulic imbalance, improve the flexibility and response speed of the variable flow regulation process, and achieve energy saving and emission reduction, and improve comfort and reliability.

[0174] It can be seen that this embodiment can collect the supply air temperature or the supply and return water temperature in real time, and control it in conjunction with the terminal water valve. According to the indoor load demand, the terminal water valve opening is dynamically adjusted in a compensation and correction manner to adjust the water flow rate, so as to realize dynamic adjustment of the terminal flow with the indoor load size, and effectively improve the situation of inaccurate adjustment and out-of-control adjustment when the terminal is operating in a small flow range. At the same time, combined with the zoning control of the water system, the zoning control is carried out according to the terminal flow size to achieve basically consistent flow in each area. When the terminal flow changes, the local hydraulic balance is maintained to achieve controllable regulation of the overall water system, and the pressure difference is accurately controlled to optimize the water flow, reduce energy consumption, and improve the overall energy efficiency and reliability of the system.

[0175] The above description is only an exemplary embodiment of the present application and is not intended to limit the present application. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present application shall be included in the protection scope of the present application.

Claims

1. A control method for an air conditioning system, characterized in that: include: Determine the temperature parameter ΔT, which includes the supply air temperature difference ΔT f Or the supply and return water temperature difference ΔT s , supply air temperature difference ΔT f is the actual value of the supply air temperature T at the end (1) of the air conditioning system f1 and the preset value of supply air temperature T f2 The difference between the supply and return water temperature difference ΔT s is the actual value of the supply and return water temperature difference of the air conditioning system T s1 The preset value T of the supply and return water temperature difference s2 difference; Based on the determined temperature parameter ΔT, determining the adjustment step |D1|%; According to the determined adjustment step |D1|%, the opening of the water valve at the end (1) of the air-conditioning system is adjusted.

2. The control method according to claim 1, characterized in that: Based on the determined temperature parameter ΔT, determining the adjustment step |D1|% includes: Determining a D value based on the determined temperature parameter ΔT; Based on the determined D value, an adjustment step |D1|% is determined.

3. The control method according to claim 2, characterized in that: Based on the determined temperature parameter ΔT, determining the D value includes: Determine the D value based on ΔT*a, or f(ΔT)+f(P); Where a>0; f(ΔT) is a function with ΔT as a variable; f(P) is a function with P as the variable. When ΔT includes the supply air temperature difference ΔT f When P is the actual value of the current supply air temperature T f1 The actual value of the supply air temperature T before the preset time t1 f1 When ΔT includes the supply and return water temperature difference ΔT s When P is the actual value of the current supply and return water temperature difference T s1 The actual value of the supply and return water temperature difference T before the preset time t2 s1 difference.

4. The control method according to claim 3, characterized in that: a>1; and / or, f(ΔT)=ΔT*γ, γ>0; and / or, f(P)=P*δ, δ>0.

5. The control method according to claim 4, characterized in that: 1<a≤10; and / or, γ≥0.5; and / or, δ>1.

6. The control method according to claim 5, characterized in that: γ>1; and / or, δ=b*c, wherein, 2<b≤10, 0.5≤c≤10.

7. The control method according to claim 6, characterized in that: 1<γ≤10; and / or, 2<b≤6; and / or, 0.5≤c≤5.

8. The control method according to claim 3, characterized in that: 5s≤t1≤30s; or, 5s≤t2≤30s.

9. The control method according to claim 8, characterized in that: 10s≤t1≤30s; or, 10s≤t2≤30s.

10. The control method according to any one of claims 2 to 9, characterized in that: Based on the determined D value, determining the adjustment step |D1|% includes: When 0<|D|<1, the adjustment step |D1|% is determined as a constant c; and / or, When |D|≥1, the adjustment step |D1|% is determined as |D|%.

11. The control method according to claim 10, characterized in that: 0.3％≤c≤0.8％。 12. The control method according to claim 11, characterized in that: 0.5％≤c≤0.8％。 13. The control method according to any one of claims 2 to 9, characterized in that: When the opening of the water valve at the end (1) of the air-conditioning system is adjusted according to the determined adjustment step |D1|%, the opening of the water valve at the end (1) of the air-conditioning system is adjusted once every time interval Δt.

14. The control method according to claim 13, characterized in that: 3s≤Δt≤20s.

15. The control method according to claim 14, characterized in that: 5s≤Δt≤20s.

16. The control method according to any one of claims 2 to 9, characterized in that: According to the determined adjustment step |D1|%, adjusting the opening of the water valve at the end (1) of the air conditioning system comprises: When D>0, the opening of the water valve at the end (1) of the air conditioning system is increased by |D1|%; When D<0, the opening of the water valve at the end (1) of the air conditioning system is reduced by |D1|%.

17. The control method according to any one of claims 1 to 9, characterized in that: Determining the temperature parameter ΔT includes: After the water valve at the end (1) of the air conditioning system is opened, after a delay time t, the supply air temperature at the end (1) of the air conditioning system is detected as the actual value T of the supply air temperature at the end (1) of the air conditioning system. f1 Alternatively, the return water temperature and the supply water temperature of the terminal (1) of the air conditioning system are detected, and the difference between the return water temperature and the supply water temperature of the terminal (1) of the air conditioning system is used as the actual value T of the supply and return water temperature difference of the terminal (1) of the air conditioning system. s1 ; The actual value T of the air supply temperature at the end (1) of the air conditioning system f1 and the preset value of supply air temperature T f2 The difference is taken as the supply air temperature difference ΔT f , and the air supply temperature difference ΔT f Determine as the temperature parameter ΔT, or, the actual value of the supply and return water temperature difference T at the end (1) of the air conditioning system s1 The preset value T of the supply and return water temperature difference s2 The difference between the supply and return water temperatures is taken as the supply and return water temperature difference ΔT s , and the supply and return water temperature difference ΔT s Determined as the temperature parameter ΔT.

18. The control method according to claim 17, characterized in that: 30s≤t≤90s.

19. The control method according to claim 18, characterized in that: 60s≤t≤90s.

20. The control method according to any one of claims 1 to 9, characterized in that: The control method further comprises: Dividing the plurality of terminals (1) of the air conditioning system into a plurality of control zones (5), so that the total rated flow of each control zone (5) in the plurality of control zones (5) is consistent; According to the pressure difference of each control zone (5), the opening degree of the main water valve of each control zone (5) is adjusted to ensure that the pressure difference of each control zone (5) is kept stable.

21. A controller, characterized in that: The invention comprises a memory and a processor coupled to the memory, wherein the processor is configured to execute the control method according to any one of claims 1 to 20 based on instructions stored in the memory.

22. An air conditioning system, characterized in that: Comprising a controller as claimed in claim 21.

23. A storage medium, characterized in that: The storage medium stores computer instructions, and the computer instructions are executed by the processor as the control method according to any one of claims 1-20.

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