Automobile air conditioner multi-zone air volume control method and vehicle

Abstract

The present application relates to the field of automobile air conditioner control, and particularly provides a kind of automobile air conditioner multi-zone air volume control method and vehicle, to solve the problem of low control precision and high cost in the prior art for automobile air conditioner multi-zone air volume control.To this end, the control method of the present application is based on the independent components of air conditioning system, by constructing pressure-flow coupling model and calculating the air volume and pressure of each partition air duct based on the balance relationship between pressure and flow according to the model, by comparing with the target air volume, the best duty cycle of blower and the best opening position of damper are obtained, so as to realize the rapid and accurate control of automobile air conditioner multi-zone air volume.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of automobile air conditioner control, and particularly provides a multi-zone air volume control method for an automobile air conditioner and a vehicle. BACKGROUND

[0002] With the rapid development of modern transportation, automobiles have become the first choice for modern people to travel. As an important part of automobiles, automobile air conditioners improve the comfort of people riding in automobiles. With the development of technology, people's demand for air conditioners is not only to simply control the temperature, but also to be fine and economical. Therefore, the control of automobile air conditioners has become a trend in the development of modern automobile air conditioners.

[0003] At present, the partition in the automobile air conditioner is mainly temperature partition, mode partition and air volume partition. The temperature partition and the mode partition can be respectively controlled in a closed loop through the feedback of the temperature sensor and the feedback of the driving motor position in the air conditioner box. Unlike the above two partitions, the air volume partition has no related feedback signal. One solution is to rely on experiments to obtain the air volume data under various mode and gear combinations and then fill in the table for subsequent software calling. This table lookup method requires a large amount of experimental data and calibration work, and it is difficult to implement as the mode and air volume gears increase. Taking a double-zone mode + double-zone air volume combination as an example, the mode and air volume combination can reach tens of thousands. On this basis, the increase of each zone mode or air volume will bring an increase of tens to hundreds of times of work. In order to reduce the workload, the commonly used processing method is to test and then interpolate. Ultimately, the table lookup method has the problems of low precision of air volume control and large mutual interference of air volume between different zones. In addition, due to the limited amount of data relied on by the table lookup method, the discrete gears between the data cannot realize continuous and stable control of the air volume. In addition, if the air conditioning system is changed at a later stage, all the air volumes involved need to be measured again, and the control method has poor reusability.

[0004] Another solution is to set an additional air speed or differential pressure sensor for single-zone air volume measurement in each air volume partition. The air volume can be controlled through the feedback value. On the one hand, the air volume control method based on feedback takes a long time to adjust before reaching the target air volume, and the adjustment process is easy to cause air volume shock in each zone. In addition, with the increase of each air volume partition, a set of air speed or air volume sensor is added, which will also increase the system complexity and cost. At present, there is no mature vehicle air speed or differential pressure sensor application.

[0005] Correspondingly, there is a need in the art for a new automobile air conditioner control method to solve the above problems. SUMMARY

[0006] The present application aims to solve the above technical problems, i.e. to solve the problem of low control precision and high cost in the prior art for multi-zone air volume control of an automobile air conditioner. To this end, the present application provides a method for controlling the air volume of a multi-zone automobile air conditioner, wherein the air conditioner comprises a blower, an air duct and air doors, the blower is used to deliver air volume to the air duct, the air duct has a plurality of sub-ducts, the air doors are arranged at the outlet ends of the sub-ducts and control the air volume at the outlet ends of the sub-ducts by adjusting the opening degree,

[0007] The control method comprises:

[0008] S100: obtaining the target air volume of each sub-duct according to the current mode and air volume position of the air conditioner, setting the initial duty cycle of the blower, and obtaining the air pressure at the sub-duct intersection of the air duct;

[0009] S200: obtaining the sub-duct pressure of each sub-duct by the air pressure at the sub-duct intersection of the air duct and the target air volume according to the pressure-flow coupling model and mathematical equation expression of the blower to each sub-duct;

[0010] S300: comparing the maximum air volume of each sub-duct at the sub-duct pressure with the target air volume of the sub-duct one by one, judging whether the duty cycle of the blower meets the performance requirement, if not, adjusting the duty cycle of the blower, re-obtaining the air pressure at the sub-duct intersection of the air duct, and then executing the step S200; if yes, adjusting the opening degree position of the air door to make the air volume at the outlet end of the sub-duct equal to the target air volume.

[0011] In the above embodiment with the control method, the mathematical equation expression in the step S200 is calculated based on the balance relationship between pressure drop and air volume.

[0012] In the above embodiment with the control method, the balance relationship between pressure drop and air volume comprises the pressure drop balance relationship of each sub-duct, and / or the balance relationship between the air volume of each sub-duct and the target air volume.

[0013] In the above embodiment with the control method, the pressure drop of each sub-duct is obtained according to the function relationship between the pressure drop and the air volume of the sub-duct, the mathematical equation expression is calculated according to the pressure drop balance relationship of each sub-duct, and / or

[0014] The mathematical equation expression is calculated according to the balance between the effective air volume, leakage air volume and the target air volume of each sub-duct.

[0015] In the above embodiment with the control method, the step S400 specifically comprises:

[0016] determining whether there is at least any of the sub-ducts whose maximum air flow under the sub-duct pressure is less than the target air flow, if yes, the performance requirement is not met, the duty ratio of the air blower is increased, and the step S100 is returned until the maximum air flow under the sub-duct pressure of all the sub-ducts is not less than the target air flow; if no, determining whether there is at least any of the sub-ducts whose maximum air flow under the sub-duct pressure is equal to the target air flow, if no, the performance requirement is not met, the duty ratio of the air blower is decreased, and the step S100 is returned until there is at least any of the sub-ducts whose maximum air flow under the sub-duct pressure is equal to the target air flow; if yes, the performance requirement is met, and the damper opening position is adjusted to make the outlet air flow of the sub-duct equal to the target air flow.

[0017] In the above embodiment with the control method, the maximum air flow under the sub-duct pressure of the sub-duct is the air flow when the damper is fully opened.

[0018] In the above embodiment with the control method, the air conditioner further comprises an evaporator, a condenser, and an electric heater.

[0019] The pressure-flow coupling model is a coupling model of air passing through the air blower, the evaporator, the condenser, the electric heater, and each of the sub-ducts.

[0020] In the above embodiment with the control method, in the step S100, “obtaining the air pressure at the sub-duct intersection of the air duct” further comprises:

[0021] obtaining the air blower pressure according to the initial duty ratio of the air blower, obtaining the pressure drop of the evaporator, the condenser, and the electric heater respectively, and obtaining the air pressure at the sub-duct intersection of the air duct according to the air blower pressure, the pressure drop of the evaporator, and / or the pressure drop of the condenser, and / or the pressure drop of the electric heater.

[0022] In the above embodiment with the control method, the air blower pressure and the pressure drop of the evaporator, the condenser, and the electric heater are obtained by a table lookup method or a functional relationship.

[0023] A vehicle comprising a controller configured to perform the air conditioner multi-zone air flow control method of the above scheme.

[0024] In the case of adopting the above technical solutions, the present application is based on independent parts of the air conditioning system, the air volume and pressure of each partition air duct are calculated based on the balance relationship of pressure drop and flow according to the pressure-flow coupling model, the best duty ratio of the blower and the best opening position of the damper are obtained by comparing with the target air volume, so as to realize the rapid and accurate control of the multi-zone air volume of the automobile air conditioner. The present application only relies on the establishment and solution of the mathematical physical model, and does not rely on additional sensors to realize the accurate continuous and stable control of the multi-mode and multi-zone air volume, thereby reducing the control cost. Compared with the table lookup method, the present application does not rely on a large number of mode and air volume position combination air volume tests, and can realize the accurate continuous and stable control under the combination of multi-zone mode and air volume. Compared with the method relying on real sensor feedback, the blower duty ratio and damper position meeting the target air volume in the control method of the present application can be quickly output through virtual iteration, the blower and damper are controlled to the target position meeting the air volume request of each zone in one step, and there is no problem of adjustment shock and long convergence time. The control method has high reusability, and only the model and parameters of the corresponding change points need to be updated when replacing parts and systems, without affecting the logical framework of the whole control method. The expansibility of the air volume control method is improved, and when the multi-zone air volume control method based on the mathematical physical model proposed in the present application is expanded in the automobile air conditioner, only the corresponding part model needs to be added to the pressure-flow network model for solution. Through the control method of the present application, the pressure-flow distribution of each part of the air conditioning box can be calculated, which can support the subsequent optimization of the structure and parts of the air conditioning box. BRIEF DESCRIPTION OF DRAWINGS

[0025] The preferred embodiments of the present application will be described below with reference to the accompanying drawings, in which:

[0026] Figure 1 is a schematic view of the structure of the automobile air conditioning box in one embodiment of the present application;

[0027] Figure 2 is a schematic view of the main control steps in the present application;

[0028] Figure 3 is a schematic view of the pressure-flow coupling model of the air conditioning system in the present application;

[0029] Figure 4 is a schematic view of the part pressure-flow coupling model of the partition air duct in the present application;

[0030] In the figure: 1, inner circulation air door, 2, outer circulation air door, 3, filter core, 4, air blower, 5, evaporator, 6, internal condenser, 7, positive temperature coefficient resistance heater, 8, defrosting air door, 9, front row blowing face air door, 10, left and right partition plate, 11, front blowing foot air door, 12, front bypass air door, 13, upper and lower partition air door, 14, rear bypass air door, 15, rear blowing foot air door, 16, rear row blowing face air door. DETAILED DESCRIPTION

[0031] The preferred embodiments of the present application will be described below with reference to the accompanying drawings and in conjunction with the air volume control of a four-zone automobile air conditioner. It should be understood by those skilled in the art that these embodiments are only used for explaining the technical principles of the present application, and are not used for limiting the protection scope of the present application. Those skilled in the art can make adjustments to them as needed in order to adapt to specific application occasions. For example, although the description is made in conjunction with the air volume control of a four-zone automobile air conditioner, this is not limiting, and those skilled in the art can apply the present application to the air volume control of other multi-zone automobile air conditioners as needed, as long as the automobile air conditioner needs to control the air volume of each zone to achieve the best operating state.

[0032] It should be noted that in the description of the present application, the terms indicating the direction or positional relationship such as "upper", "lower", "left", "right", "inner", "outer", etc. are based on the direction or positional relationship shown in the drawings, which is only for the convenience of description, and does not indicate or imply that the related devices or elements must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present application. In addition, the ordinal numbers "first", "second", etc. are only for the purpose of description and cannot be understood as indicating or implying relative importance.

[0033] In addition, it should also be noted that in the description of the present application, unless otherwise explicitly specified and limited, the terms "mounting", "connection" should be understood broadly, for example, it can be fixed connection, or detachable connection or integral connection; it can be mechanical connection, or electrical connection; it can be direct connection, or indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in the present application according to the specific circumstances.

[0034] Furthermore, in order to more clearly show the core technical solutions of the present application, the description below omits the description of the known structure of the automobile air conditioner, but this omission is only for the convenience of description and does not mean that the automobile air conditioner can not have these structures.

[0035] As shown in Fig. 1, it is a schematic diagram of the structure of an automobile air conditioner box. The present embodiment will be described in conjunction with Fig. 2, which is a schematic diagram of the air volume control of a four-zone automobile air conditioner. Figure 1 As shown in Fig. 1, it is a schematic diagram of the structure of an automobile air conditioner box. The present embodiment will be described in conjunction with Fig. 2, which is a schematic diagram of the air volume control of a four-zone automobile air conditioner. Figure 1The control of the four-zone air duct of the automobile air conditioner is described, and it should be noted that this does not limit the protection scope of the present application, and those skilled in the art can apply the control method of the present application to the control of the air volume of other multi-zone automobile air conditioners without deviating from the technical concept of the present application.

[0036] As shown in Figure 1 The automobile air conditioner box structure of the present embodiment integrates the components into one body through the box structure, the box body is designed with an air duct, and a damper capable of controlling the opening degree is installed on the box body, wherein an inner circulation damper 1 and an outer circulation damper 2 are installed on the air inlet side to control the air volume ratio of the inner circulation and the outer circulation respectively, a filter element 3 is installed on the air outlet side of the inner circulation damper 1 and the outer circulation damper 2 to filter the circulating air, a blower 4 is installed in the box body to pressurize the filtered air, the filtered air passes through an evaporator 5 to achieve cooling, dehumidification and cooling, and then passes through an internal condenser 6, in the heat pump mode, the air is heated, and then passes through a positive temperature coefficient resistance heater 7 to heat the air by using electric energy, in the present embodiment, the air volume is delivered by dividing the box body into four zones by left and right partition plates 10 and upper and lower partition plates, the dampers communicating with the four zones are defrosting damper 8, front discharge face damper, front foot blowing damper 11, front bypass damper 12, rear bypass damper 14, rear foot blowing damper 15 and rear discharge face blowing damper 16, the above-mentioned dampers can control the size of the air volume by adjusting the opening degree, in the present embodiment, the inner circulation of the above-mentioned automobile air conditioning system is taken as an example to describe the control method of the present application.

[0037] Referring to Figure 2 The control method of the present application includes the following steps:

[0038] S100: obtaining the target air volume of each zone air duct according to the current mode and air volume position of the air conditioner, setting the initial duty cycle of the blower, and obtaining the air pressure at the intersection of the zone air duct;

[0039] S200: obtaining the zone air duct pressure of each zone air duct by the air pressure at the intersection of the zone air duct and the target air volume according to the pressure-flow coupling model and mathematical equation expression of the blower to each zone air duct;

[0040] S300: comparing the maximum air volume of each zone air duct under the zone air duct pressure with the target air volume one by one to determine whether the duty cycle of the blower meets the efficiency requirement;

[0041] S310: if the efficiency requirement is not met, adjusting the duty cycle of the blower, re-obtaining the air pressure at the intersection of the zone air duct, and then executing step S200;

[0042] S320: If the performance requirement is met, adjust the damper opening position to make the outlet end air volume of the partition air duct equal to the target air volume.

[0043] Further, the step 300 specifically comprises:

[0044] determining whether there is at least any of the partition air ducts whose maximum air volume under the partition air duct pressure is less than the target air volume.

[0045] If yes, the performance requirement is not met, the duty cycle of the air blower is increased, and the step S100 is returned until the maximum air volume of all the partition air ducts under the partition air duct pressure is not less than the target air volume.

[0046] If no, it is determined whether there is at least any of the partition air ducts whose maximum air volume under the partition air duct pressure is equal to the target air volume; if no, the performance requirement is not met, the duty cycle of the air blower is decreased, and the step 100 is returned until there is at least any of the partition air ducts whose maximum air volume under the partition air duct pressure is equal to the target air volume; if yes, the performance requirement is met, and the damper opening position is adjusted to make the outlet end air volume of the partition air duct equal to the target air volume.

[0047] In the embodiment, first, the target air volume Q of the partition air duct is obtained according to the mode and the air volume position of the automobile air conditioning system in the above embodiment i.目标 , and the obtaining method specifically can be a table lookup method. It needs to be noted that the parameters obtained by the table lookup method are different from those of the air volume partition control, and the data capacity is much smaller than that of the air volume control. The subsequent table lookup method is the same as described herein, and will not be described in detail. Then, the initial duty cycle of the air blower is set, and the air pressure at the intersection of the partition air duct of the air duct is obtained. Then, according to the pressure-flow coupling model from the air blower to the outlet end of the partition air duct, the air volume value and the pressure value at each position in the automobile air conditioning system can be calculated according to the pressure-flow coupling model. First, this mathematical equation expression is solved on the premise of meeting the target air volume, so it must meet the air volume requirement. Next, the duty cycle of the air blower is judged on the basis of the initial duty cycle of the air blower, to determine whether it is in the best performance working state. When the duty cycle of the air blower does not reach the best duty cycle, continuous iterative optimization can be realized to quickly and accurately calculate the optimal duty cycle of the air blower. By adjusting the opening degree of the damper, the air blower is in the best performance, and all the partition air ducts meet the target air volume output.

[0048] Based on the above embodiment, refer to Figures 2 to 4Specifically, in the present embodiment, the air duct subsequent to the positive temperature coefficient resistance heater is divided into four parts, and the target air volume corresponding to the four sub-ducts is Q 1.目标 , Q 2.目标 , Q 3.目标 , and Q 4.目标 , respectively. The total target air volume of the air blower is Q 总.目标 . The air in the vehicle is pressurized by the air blower, and the pressure rises from P 车 to P 鼓 , then drops to P 蒸 after passing through the evaporator, and drops to P 冷 after passing through the internal condenser. After being blown out from the internal condenser, the air is divided into four sub-areas after passing through the positive temperature coefficient resistance heater, and the air volume in the four sub-areas is q1, q2, q3, and q4, respectively. In addition, due to the gaps between the left and right dividing plates, the upper and lower dividing plates, and the positive temperature coefficient resistance heater, there is air leakage between the four areas at the outlet of the positive temperature coefficient resistance heater, and the leakage air volume is q5, q6, q7, and q8, respectively. The air volume at the outlet of the four sub-ducts is the target air volume, and the balance of the air volume is formed. When passing through the positive temperature coefficient resistance heater, pressure drops ΔP1, ΔP2, ΔP3, and ΔP4 occur, and the pressure corresponding to the target air volume at the outlet is P1, P2, P3, and P4, respectively. Finally, Q 总.目标 is returned to the vehicle through the air door. According to the relationship between the flow rate and the pressure, the automobile air conditioning system in the present embodiment is constructed into a pressure-flow network model, as shown in Figure 3 .

[0049] After the pressure-flow network model is built, the air conditioning system needs to be solved to obtain the sub-duct pressure under the target air volume. Specifically, the initial duty ratio of the air blower is set. Under the premise that the total target air volume and the duty ratio on the air blower side are known, the air blower outlet pressure P 鼓 can be obtained by table lookup or function relationship. The pressure drop of the evaporator and the pressure drop of the internal condenser can be calculated by table lookup or function fitting based on experimental data. The first and second attenuated air pressures at the outlet of the evaporator and the internal condenser are subtracted to obtain the pressure P 电 at the inlet of the positive temperature coefficient resistance heater, which is equivalent to P 冷 . According to the above pressure and air volume relationship and combined with the overall pressure-flow network model, the pressure-flow model of the sub-duct can be constructed, as shown in Figure 4 . Since there is air leakage between the sub-ducts, they cannot be solved separately. The function relationship expression between the pressure drop and the air volume of the sub-duct can be constructed, i.e., f i (q i), the function relationship expression is a nonlinear expression, and the pressure-flow model at the partition air duct can be obtained based on the balance relationship between the pressure drop and the flow rate, thereby obtaining an 8-element quadratic nonlinear equation group, as follows:

[0050]

[0051] The above equation group is solved by using a numerical iteration method of a nonlinear equation group to obtain q1, q2, q3, q4, q5, q6, q7 and q8, and the pressure drops of the four zones of the positive temperature coefficient resistance heater can be obtained, and the pressure P at the inlet of the positive temperature coefficient resistance heater can be obtained. 电 Under the known condition, the outlet pressures P1, P2, P3 and P4 of the four partition channels can also be obtained.

[0052] Further, based on the solution of the above embodiment, it is necessary to judge the duty ratio of the blower, and under the premise that the target air volume of the partition air duct has been met, the initial duty ratio of the blower is not necessarily the optimal duty ratio, and further judgment and verification are needed, specifically, under the condition that the partition air duct pressures of the four partition air ducts are known, the air volume of the corresponding partition air duct under the condition that the damper is fully open can be obtained by table lookup or function fitting relationship, and the fully open damper is the maximum possible air volume of the partition, and the outlet air volume under this condition is compared with the target air volume to make the first judgment, and it is judged whether all the outlet air volumes are lower than the target air volume, if all the air volumes of the partition air ducts under the condition that the damper is fully open are lower than the target air volume, it means that the duty ratio of the blower is too low, and the duty ratio of the blower needs to be increased, if the outlet air volumes of all the zones under the condition that the damper is fully open are not lower than the target air volume, then the second judgment process can be carried out, in which it is further judged whether the outlet air volume of at least any partition air duct is equal to the target air volume, if this condition is not met, it means that the air volumes of all the outlet ends of the partition air ducts are greater than the target air volume, at this time, it is indicated that the duty ratio of the blower is too high, and the duty ratio needs to be reduced, if this condition is met, it is considered that the blower has reached the optimal duty ratio, i.e., the highest efficiency state, at this time, the damper opening position greater than the target air volume needs to be adjusted to reduce the opening to meet the target air volume of the outlet end of the partition air duct, and the opening position of the corresponding damper and the duty ratio of the blower at this time are output, and the air conditioning system is controlled to operate according to the parameters, so that the target air volume can be output under the optimal efficiency of the blower, and energy consumption is not lost.

[0053] Further, the present application also provides a car.

[0054] In the embodiment, the element for controlling the air conditioner multi-zone air volume of the automobile can be a controller or a medium capable of carrying the corresponding program of the air conditioner multi-zone air volume control method. If it is a controller, the controller needs to be configured to be capable of executing the air conditioner multi-zone air volume control method.

[0055] So far, the technical solutions of the present application have been described in combination with the preferred embodiments shown in the drawings, but it is easy for those skilled in the art to understand that the protection scope of the present application is obviously not limited to these specific embodiments. Those skilled in the art can make equivalent changes or replacements to the related technical features without departing from the principles of the present application, and the technical solutions after the changes or replacements will all fall within the protection scope of the present application.

Claims

1. A method for controlling air volume in a plurality of zones in an automotive air conditioner, characterized by, The air conditioner comprises a blower, an air duct and dampers, the blower is used to deliver air volume to the air duct, the air duct has a plurality of sub-ducts, the dampers are arranged at the outlet ends of the sub-ducts and control the air volume at the outlet ends of the sub-ducts by adjusting the opening degree, and the control method comprises: S100: obtaining the target air volume of each sub-duct according to the current mode and air volume position of the air conditioner, setting the initial duty ratio of the blower, and obtaining the air pressure at the sub-duct intersection of the air duct; S200: obtaining the sub-duct pressure of each sub-duct by the air pressure at the sub-duct intersection of the air duct and the target air volume according to the pressure-flow coupling model and mathematical equation expression of the blower to each sub-duct; S300: comparing the maximum air volume of each sub-duct at the sub-duct pressure with the target air volume one by one, judging whether the duty ratio of the blower meets the performance requirement, if not, adjusting the duty ratio of the blower, re-obtaining the air pressure at the sub-duct intersection of the air duct, and then executing the step S200; if yes, adjusting the opening degree position of the damper to make the air volume at the outlet end of the sub-duct equal to the target air volume.

2. The automobile air conditioning multi-zone air volume control method according to claim 1, characterized in that, The mathematical equation expression in the step S200 is calculated based on the balance relationship between pressure drop and air volume.

3. The automobile air conditioning multi-zone air volume control method according to claim 2, characterized in that, The balance relationship between pressure drop and air volume comprises the pressure drop balance relationship of each sub-duct, and / or the balance relationship between the air volume of each sub-duct and the target air volume.

4. The automobile air conditioning multi-zone air volume control method according to claim 3, characterized in that, The pressure drop of each sub-duct is obtained according to the function relationship between the pressure drop and air volume of the sub-duct, the mathematical equation expression is calculated according to the pressure drop balance relationship of each sub-duct, and / or The mathematical equation expression is calculated according to the balance between the effective air volume, leakage air volume of each sub-duct and the target air volume.

5. The automobile air conditioning multi-zone air volume control method according to any one of claims 1 to 4, characterized by, The step S300 specifically comprises: judging whether there is at least any sub-duct whose maximum air volume at the sub-duct pressure is less than the target air volume, if yes, not meeting the performance requirement, increasing the duty ratio of the blower, and returning to the step S100 until the maximum air volume of all the sub-ducts at the sub-duct pressure is not less than the target air volume; if no, judging whether there is at least any sub-duct whose maximum air volume at the sub-duct pressure is equal to the target air volume, if no, not meeting the performance requirement, decreasing the duty ratio of the blower, and returning to the step S100 until there is at least any sub-duct whose maximum air volume at the sub-duct pressure is equal to the target air volume; if yes, meeting the performance requirement, and adjusting the opening degree position of the damper to make the air volume at the outlet end of the sub-duct equal to the target air volume.

6. The automobile air conditioning multi-zone air volume control method according to claim 5, characterized in that, The maximum air volume of the sub-duct at the sub-duct pressure is the air volume when the damper is fully opened.

7. The automobile air conditioning multi-zone air volume control method according to claim 6, characterized by, The air conditioner further comprises an evaporator, a condenser and an electric resistance heater. The pressure-flow coupling model is a coupling model of air passing through the air blower, the evaporator, the condenser, the resistance heater to each of the zoning air ducts.

8. The automobile air conditioning multi-zone air volume control method according to claim 7, characterized in that, In the step S100, "obtaining the air pressure at the zoning intersection of the air duct" further comprises: obtaining the air blower pressure according to the initial duty ratio of the air blower, obtaining the pressure drop of each of the evaporator, the condenser and the resistance heater, and obtaining the air pressure at the zoning intersection of the air duct according to the air blower pressure, the pressure drop of the evaporator and / or the pressure drop of the condenser and / or the pressure drop of the resistance heater.

9. The automobile air conditioning multi-zone air volume control method according to claim 8, characterized by, The air blower pressure and the pressure drop of each of the evaporator, the condenser and the resistance heater are obtained by a table lookup method or a functional relationship.

10. A vehicle characterized by comprising: The vehicle comprises a controller configured to be capable of performing the air conditioning multi-zone air volume control method according to any one of claims 1 to 9.

Images