JP3826549B2 - Air conditioner - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention provides a first passage for the first air-conditioning zone and a second passage for the second air-conditioning zone in the air-conditioning apparatus, and can variably control the amount of the conditioned air flowing through the first and second passages. It is suitable for.
[0002]
[Prior art]
2. Description of the Related Art Conventionally, it is well known that a driver seat side passage and a passenger seat side passage are formed by dividing an air conditioning case into two passages as described in JP-A-9-39544. In the conventional apparatus, the evaporator and the heater core are arranged so as to straddle the two passages, the driver side air mix door is provided in the driver seat side passage, and the passenger seat side passage is provided in the passenger seat side passage. By arranging an air mix door, the temperature of the conditioned air can be obtained according to the preference of the driver and assistant.
[0003]
Moreover, in the said conventional apparatus, the upstream site | part of an air-conditioning case is not divided by the above-mentioned two channel | paths, The one air conditioning fan is arrange | positioned in this site | part. For this reason, the airflows flowing through the two passages are the same.
[0004]
[Problems to be solved by the invention]
By the way, in the said conventional apparatus, the air-conditioning feeling is improved by controlling each conditioned air blown by the driver's seat side and the passenger seat side independently, but the air-conditioner blown by each air-conditioning zone Since the wind volume is the same, it does not respond to requests from the driver and passengers in terms of air volume.
[0005]
Then, an object of this invention is to provide the air conditioning apparatus which can control each air volume of two channel | paths to a different value.
[0006]
[Means for Solving the Problems]
In order to achieve the above object, the present inventor examined and examined an air conditioner capable of controlling the air volume of each passage to a different value. Then, the following problems occurred. Usually, a cooling degree detection means for detecting the degree of air cooling in the cooling heat exchanger is arranged on the downstream side of the cooling heat exchanger, and the detection signal of this detection means is generally used as air conditioning control information. Is. When the airflow in each passage is controlled to a different value as described above, the conditioned air in the two passages passes through the cooling heat exchanger. There are many cases where the remaining air volume is low.
[0007]
Therefore, in order to obtain accurate air conditioning control information corresponding to each of the two passages, the air volume of the two passages is different as described above, and the degree of air cooling in each passage is different. Correspondingly, it is necessary to install on the air downstream side of the cooling heat exchanger.
However, providing two detection means in this way has problems such as an increase in the number of parts, an increase in assembly man-hours, and an increase in cost.
[0008]
It is an object of the present invention to provide an air conditioner having two passages and capable of recognizing the degree of air cooling in the other passage in an air conditioner in which a cooling degree detecting means is arranged in one passage for cost reduction. In the invention of claim 1, based on at least the first air volume blown into the first passage (10a), the second air volume blown into the second passage (10b), and the first cooling degree (Te1). And a cooling degree estimating means (S180) for estimating a second cooling degree (Te2) of air in the cooling heat exchanger (13) in the second passage (10b).
[0009]
Thereby, since the second cooling degree of the air in the heat exchanger for cooling in the second passage is estimated by the estimating means, even when the cooling degree detecting means is arranged only in the first passage for cost reduction, The degree of air cooling in the second passage can be recognized.
As a specific configuration, as described in claim 2, the estimation means (S 180) sets the second cooling degree (Te 2) to the first cooling degree (Te 1) when the first air volume is larger than the second air volume. If the first air volume is smaller than the second air volume, the second cooling degree (Te2) may be estimated to be smaller than the first cooling degree (Te1).
[0010]
Further, in the invention described in claim 3, among the intermittent means (104) for intermittently supplying the refrigerant to the cooling heat exchanger (13), the first cooling degree (Te 1), and the second cooling degree (Te 2). In this case, the cooling heat exchanger (13) is provided with intermittent control means (S220, S230) for stopping the refrigerant supply by the intermittent means (104) when the degree of cooling becomes larger than the predetermined cooling degree to which frost adheres. Yes.
[0011]
Thereby, it can prevent beforehand that frost adheres in the whole region of a heat exchanger required for cooling.
In the fourth aspect of the invention, the first temperature control means (S210) controls the first temperature adjusting member (17a) based on at least the first target temperature (TAO (Dr)) and the first cooling degree (Te1). ) And second temperature control means (S210) for controlling the second temperature adjusting member (17b) based on at least the second target temperature and the second cooling degree (Te2).
[0012]
Thereby, also in the 2nd channel | path which has not arrange | positioned the cooling degree detection means, the temperature of an air conditioned wind can be controlled to 2nd target temperature.
Further, in the invention according to claim 5, the estimating means (S180) is based on the difference between the intake air temperature of the air flowing into the cooling heat exchanger (13) and the first cooling degree (Te1). It is characterized by estimating the air cooling degree (Te2).
[0013]
By the way, in order to estimate the second cooling degree with high accuracy, it is necessary to know how much heat (heat transfer amount) is absorbed by the cooling heat exchanger from the air passing through the cooling heat exchanger.
Therefore, in the present invention, the amount of heat transfer can be determined from the difference between the intake air temperature sucked into the cooling heat exchanger and the first cooling degree, so that the second cooling degree can be accurately estimated.
[0014]
Further, in the invention described in claim 6, the blowout mode can be set independently so that the blowout portions of the conditioned air are different in the first air conditioning zone and the second air conditioning zone. The two air volumes are characterized by being corrected and calculated according to the blowing mode of the first air conditioning zone and the blowing mode of the second air conditioning zone.
By the way, ventilation resistance changes with blowing modes, and the air volume which flows through a 1st channel | path and a 2nd channel | path differs. Therefore, according to the present invention, since the first blowing mode and the second blowing mode are corrected according to the blowing mode, it is possible to calculate accurate first air volume and second air volume. As a result, the second cooling degree with higher accuracy can be estimated.
[0015]
In addition, the code | symbol in the bracket | parenthesis of each said means shows a corresponding relationship with the specific means of embodiment description later mentioned.
[0016]
DETAILED DESCRIPTION OF THE INVENTION
(First embodiment)
Next, an example in which the present invention is applied to a vehicle air conditioner that independently controls the temperature of the driver's seat side space (first air conditioning zone) and the passenger seat side space (second air conditioning zone) of the vehicle will be described. . First, the overall configuration of the present embodiment will be described with reference to FIG.
[0017]
In FIG. 1, 1 shows the whole ventilation system of the vehicle air conditioner, and the main body of this ventilation system 1 is disposed in the lower part of the interior instrument panel of the automobile. The vehicle air conditioner has an air conditioning case 12 that forms an air passage into the vehicle interior. As shown in FIG. 1, the air conditioning case 12 is roughly divided into an inside / outside air blowing unit 200 and an air conditioner unit 300.
[0018]
The inside / outside air blowing unit 200 is for sucking inside air or outside air into the air conditioning case 12. The inside / outside air blowing unit 200 is formed with a well-known inside air inlet 3 and outside air inlet 4, and the two inlets are selectively provided in a portion where the inside air inlet 3 and the outside air inlet 4 are separated. An inside / outside air switching door 50 (not shown) that opens and closes is provided. The inside / outside air switching door 50 is driven by a servo motor 90 (see FIG. 2) as electric drive means. As a result, the inside / outside air blowing unit 200 can suck inside air from the inside air inlet 3 or outside air from the outside air inlet 4. Thereby, in this example, the inside air mode for introducing only the inside air into the air conditioning case 12 and the outside air mode for introducing only the outside air can be switched. The servo motor 90 is controlled by an ECU 30 (control device, see FIG. 2) described later.
[0019]
In the inside / outside air blowing unit 200, one electric blower 7 is accommodated on the downstream side of the inside air inlet 3 and the outside air inlet 4. The blower 7 includes a fan 8 and a blower motor 9 (electric motor) for driving the fan 8. The blower voltage applied to the blower motor 9 is controlled by an ECU 30 (control device, see FIG. 2) described later.
In the air conditioner unit 300, an evaporator 13, which is a cooling heat exchanger for cooling the air passing therethrough, is accommodated. The evaporator 13 is a component of a well-known refrigeration cycle 400 that is pipe-coupled together with the compressor 2, the condenser 101, the liquid receiver 102, and the decompressor 103, and dehumidifies and cools the air in the air conditioning case 12. The compressor 2 is connected to an engine E / G of an automobile via an electromagnetic clutch 104. The compressor 2 stops driving by intermittently controlling the electromagnetic clutch 104. That is, when the electromagnetic clutch 104 is on, the power of the engine E / G is transmitted to the compressor 2 and the supply of refrigerant to the evaporator 103 is started. On the other hand, when the electromagnetic clutch 104 is off, the power of the engine E / G is cut off, the compressor 2 is stopped, and the refrigerant supply to the evaporator 103 is stopped. The electromagnetic clutch 104 constitutes the intermittent means of the present invention.
[0020]
In the air conditioner unit 300, a heater core 14 that is a heat exchanger for heating is disposed on the air downstream side of the evaporator 13. The heater core 14 is a heating heat exchanger that uses the cooling water of the engine E / G as a heat source, and heats the cold air cooled by the evaporator 13.
In the air conditioner unit 300, as shown in FIG. 1, a partition plate 15 is provided from the air upstream side to the most downstream side of the evaporator 13. Thereby, in the air conditioner unit 300, the two passages 12a and 12b are formed by the partition plate 15. The evaporator 13 and the heater core 14 are arranged so as to straddle both the first and second passages 10a and 10b.
[0021]
The first passage 10a is for sending conditioned air to the first air conditioning zone on the driver's seat side, and the second passage 10b is for sending conditioned air to the second air conditioning zone on the passenger seat side. is there.
The air conditioner unit 300 includes air mix doors 17a and 17b for adjusting the air temperature in each passage corresponding to the first and second passages 10a and 10b on the downstream side of the evaporator 13 and on the upstream side of the heater core 14. Is provided. These doors 17a and 17b are driven by driving means 27a and 27b (specifically, servo motors, see FIG. 2).
[0022]
The air mix door 17a adjusts the air heating amount (first air heating amount) in the heat core 14 in the first passage 10a, thereby adjusting the temperature of the conditioned air in the first passage 10a. Is configured. The air mix door 17b constitutes a second temperature adjusting means for adjusting the temperature of the conditioned air by adjusting the air heating amount (second air heating amount) in the heater core 14 in the second passage 10a.
[0023]
Specifically, a first bypass passage 30a that bypasses the heater core 14 is formed in the first passage 12a, and a second bypass passage 30b that bypasses the heater core 14 is formed in the second passage 12b. The air mix doors 17a and 17b adjust the temperature of the conditioned air in the first and second passages 12a and 12b by adjusting the ratio of the amount of air that passes through the heater core 14 and the amount of air that bypasses the heater core 14, respectively. .
[0024]
On the downstream side of the heater core 14 in the first passage 12a, driver seat openings 50a to 52a are formed for guiding the conditioned air whose temperature is adjusted by the opening degree of the air mix door 17a to the respective outlets on the driver's side in the passenger compartment. ing.
The driver seat opening 50a is for blowing conditioned air toward the driver's feet, and is for blowing the conditioned air toward the driver seat opening 51a and the driver's upper body. The driver seat opening 52a is for blowing conditioned air toward the inner surface of a vehicle windshield (not shown) on the driver seat side.
[0025]
The driver seat opening 50 a is opened and closed by a plate-like first foot door 53, and the driver seat opening 51 a is opened and closed by a plate-like first face door 54. The driver seat opening 52 a is opened and closed by a plate-like first defroster door 55. And these doors 53-55 are driven by the servomotor 56 (refer FIG. 2) as a drive means. Thereby, in the first air conditioning zone, the face mode (FACE), the bi-level mode (B / L), and the foot mode (FOOT) can be switched by automatic blow mode control described later.
[0026]
Here, these blowing modes will be briefly described. In the face mode, the conditioned air flowing through the first passage 10a is blown only from the driver seat opening 51a. In the bi-level mode, the driver seat opening is defined. In this mode, the conditioned air is blown only to both the parts 51a and 50a. The foot mode is a mode in which conditioned air is blown only to both the driver seat openings 50a and 52a.
[0027]
Further, on the downstream side of the heater core 14 in the second passage 12b, passenger seat openings 50b to 52b for guiding the conditioned air whose temperature is adjusted by the opening degree of the air mix door 17b to the respective outlets on the passenger side of the passenger compartment. Is formed. The air outlets 50a to 52a are connected to the air outlets by ducts (not shown).
The opening 50b for the passenger seat is for blowing the conditioned air toward the feet of the passenger seat, and is for blowing the conditioned air toward the upper body of the passenger seat opening 51a and the passenger seat. . The passenger seat opening 52a is for blowing conditioned air toward the inner surface of the front windshield (not shown) of the passenger seat.
[0028]
The passenger seat opening 50 b is opened and closed by a plate-like second foot door 57, and the driver seat opening 51 a is opened and closed by a plate-like second face door 58. The driver seat opening 52 a is opened and closed by a plate-like second defroster door 59. And these doors 57-58 are driven by the servomotor 60 (refer FIG. 2) as a drive means. Thus, in the second air conditioning zone, the face mode (FACE), the bi-level mode (B / L), and the foot mode (FOOT) can be switched by automatic blow-out mode control described later. In the face mode, the conditioned air flowing through the second passage 10b is blown only from the passenger seat opening 51b. In the bi-level mode, the conditioned air is supplied to only the passenger seat openings 51b, 50b. Is a mode for blowing air. Further, the foot mode is a mode in which conditioned air is blown only to both the passenger seat openings 50b and 52b.
[0029]
Here, as shown in FIG. 1, an air volume adjusting door 70 (air volume ratio control member) is installed on the downstream side of the blower 7 and upstream of the air mix doors 17a and 17b and further on the upstream end of the partition section 15. Has been. The air volume adjusting door 70 distributes the conditioned air generated by the blower 7 to the first passage 10a and the second passage 10b, and controls the air volume ratio to the first passage 10a and the second passage 10b.
[0030]
The air volume adjusting door 70 is rotated in the direction of the arrow in the figure by a rotating shaft 70 a rotatably disposed in the air conditioning case 12. The rotating shaft 70a is driven by a servo motor 70c (see FIG. 2) as a driving means.
Next, a control device (ECU) 30 that controls the vehicle air conditioner will be described.
The control device 30 is a well-known device including an A / D converter, a microcomputer, etc. (not shown) inside, and signals from the sensors 31 to 35 are A / D converted by the A / D converter. It is configured to be input to the microcomputer later. .
[0031]
The microcomputer is a well-known microcomputer having a CPU, ROM, RAM, I / O, etc. (not shown). When an ignition switch (not shown) of the engine E / G is turned on, power is supplied from a battery (not shown). .
As shown in FIG. 2, the control device 30 is connected to a means for detecting an air conditioning environment factor. Specifically, the inside air temperature sensor 31 that detects the temperature inside the vehicle, the outside air temperature sensor 32 that detects the temperature outside the vehicle interior, the solar radiation sensor 33 that detects the amount of solar radiation irradiated into the vehicle interior, and the air immediately after passing through the evaporator 13. The post-evaporator sensor 34 that detects the temperature, that is, the degree of air cooling in the evaporator 13, the water temperature sensor 35 that detects the engine cooling water temperature flowing into the heater core 14, and the like are input-connected. In the present example, as shown in FIG. 1, the post-evaporator sensor 34 is disposed in the first passage 10a, and therefore, the air temperature (first cooling degree) immediately after passing through the evaporator 13 in the first passage 10a. Is detected. In addition, the solar radiation sensor 33 of this example is the 1st solar radiation detection part which detects the 1st solar radiation amount which injects into a 1st air conditioning zone, and the 2nd solar radiation detection part which detects the 2nd solar radiation amount which injects into a 2nd air conditioning zone. It is comprised with the 2 surface sensor which has.
[0032]
Further, the control device 30 includes a driver side temperature setting device 36a for setting a set temperature Tset (Dr) in the driver side passenger compartment, which is a first air conditioning environment factor of the first air conditioning zone, and a second air conditioning zone 2nd. A passenger seat side temperature setting device 36b for setting a set temperature Tset (Pa) in the passenger seat side passenger compartment, which is an air conditioning environment factor, is connected to the input. The driver seat side temperature setter 36a and the passenger seat side temperature setter 36b are installed on an air conditioning operation panel (not shown) provided in front of the passenger compartment. The air conditioning operation panel is provided with an inside / outside air switching switch for manually switching the inside / outside air mode, a blowing mode switching switch for manually switching the blowing mode, and the like.
[0033]
The control device 30 is connected as an output terminal to the motors 27 a, 27 b to 56, 60, 70 c, 80 and a clutch circuit 80 that drives and controls the electromagnetic clutch 104. Next, the operation of this embodiment will be described based on the flowchart of FIG.
First, when the automatic control process of the air conditioner is started, data is reset (initialized) in step S110. In step S120, signals (Tr, Tam, Ts (Dr), Ts (Pa), Te1, Tw) obtained by A / D converting the values of the sensors 31 to 35 are read, and the driver side temperature setting device 36a is read. And the set temperature Tset (Dr) set by the passenger side temperature setter 36b are read. Ts (Dr) is the first solar radiation amount incident on the first air conditioning zone, and Ts (Pa) is the second solar radiation amount incident on the second air conditioning zone.
[0034]
In step S130, the target temperature of the conditioned air to be blown through the first passage 10a, that is, the first target blowing temperature of the conditioned air blown to the driver's seat (hereinafter referred to as TAO (Dr)) and the first passage 10a are blown. A target temperature of the conditioned air, that is, a second target blowing temperature (hereinafter referred to as TAO (Pa)) of the conditioned air blown out to the passenger seat side is calculated. Specifically, TAO (Dr) and TAO (Pa) are calculated based on the following formulas 1 and 2 stored in the ROM.
[0035]
[Expression 1]
TAO (Dr) = Kset × Tset (Dr) −Kr × Tr−Kam × Tam−Ks × Ts (Dr) + C
[0036]
[Expression 2]
TAO (Pa) = Kset * Tset (Pa) -Kr * Tr-Kam * Tam-Ks * Ts (Pa) + C
(Kset, Kr, Kam, Ks are gains, C is a constant for correction)
Subsequently, at step S140, the driver's seat side required blower of the target airflow value of the conditioned air blown from the TAO (Dr) and TAO (Pa) to the first passage 10a using the characteristics of FIG. 4 stored in the ROM. A voltage VM (Dr) (first target air volume) and a passenger seat side required blower voltage VM (Pa) (second target air volume) that is a target air volume value of the conditioned air blown to the second passage 10b are determined.
[0037]
The characteristic shown in FIG. 4 is that when the target blowing temperatures TAO (Dr) and TAO (Pa) are in the region (1), the air blowing unit cannot produce these target blowing temperatures, so that the cooling capacity is gained. Therefore, when the air volume is increased and TAO (Dr) and TAO (Pa) are in the region (2), the air volume is kept constant in order to change the amount of heat supplied to the passenger compartment by changing the blowing temperature.
[0038]
Furthermore, the characteristic of FIG. 4 is that when the TAO (Dr) and TAO (Pa) are in the region (3), the air flow cannot be generated by the air conditioner so that the air volume is increased to increase the heating capacity. As described above, the relationship between TAO and VM is set to a non-linear relationship.
Next, in step S150, the ratio between the driver's seat side required blower voltage VM (Dr) and the passenger's seat side required blower voltage VM (Pa) determined in step S140, that is, the first passage 10a and the second passage 10b. The air volume ratio (air distribution ratio X) of the conditioned air is determined, and the opening degree (operating position) of the air volume adjusting door 70 is determined.
[0039]
In step S160, according to the operation position of the air volume adjustment door 70, the final air volume is blown to the first and second passages 10a and 10b so that the air volume determined in step S140 is the same. The required blower voltage VM of the typical blower motor 9 is calculated.
As a result, the amount of air blown to the first and second passages 10a and 10b satisfies the requirements of VM (Dr) and VM (Pa), respectively, and the first passage 10a and the second passage 10b Each air volume of the conditioned air to be blown can be controlled to a different value. The air volume adjusting door 70, the servo motor 70c, and the ECU 30 constitute the air volume control means of the present invention.
[0040]
Next, in step S170, each blowing mode on the driver seat side and the passenger seat side is determined from the above TAO (Dr) and TAO (Pa) and the characteristics shown in FIG. 5 stored in the ROM. That is, in this example, the blowout mode can be set independently so that the blowout parts of the conditioned air are different in the first air conditioning zone and the second air conditioning zone.
In addition, the defroster mode can be set as the blowing mode. This defroster mode is a mode in which conditioned air is always blown only from both driver seat openings 52a and 52b, and is switched when the defroster switch installed on the air conditioning operation panel is turned on.
[0041]
Next, in step S180, the air cooling degree Te2 (hereinafter, air temperature Te2) in the evaporator 13 in the second passage 10b is estimated. That is, as described above, since the post-evaporator sensor 34 is disposed in the first passage 10a in the present example, in step S180, the air temperature Te2 immediately after passing through the evaporator 13 in the second passage 10b is estimated. Specifically, as shown in FIG. 6, in step S180a, from the required blower voltage VM and the air distribution ratio X, the first air volume blown into the first passage 10a and the second air blown into the second passage 10b. 2 Calculate the air volume.
[0042]
Next, in step S180b, the magnitude relationship between the first air volume and the second air volume is recognized, and the difference between these is calculated. Subsequently, in step S180c, the air temperature Te2 is estimated based on the calculation result in step S180a. For example, when the air temperature Te1 (detected temperature of the sensor 34) is 5 ° C. and the first air volume is larger than the second air volume, the air is cooled in the second passage 10b, so the air temperature Te2 is The value is estimated to be lower than the air temperature Te1. In this case, the air temperature Te2 is estimated to be smaller than the air temperature Te1 as the difference between the first air volume and the second air volume is larger.
[0043]
On the other hand, for example, when the air temperature Te1 is 5 ° C. and the first air volume is smaller than the second air volume, the air is not cooled in the second passage 10b than the first passage 10a. Estimate higher value. In this case, the air temperature Te2 is estimated to be higher than the air temperature Te1 as the difference between the first air volume and the second air volume is larger. Thus, in this example, in the air conditioner in which the post-evaporator sensor 34 is arranged in the first passage 10a for cost reduction, the air cooling degree (Te2) in the second passage 10b can be estimated and recognized.
[0044]
Next, in step S190, the air mix door 17a opening degree SW (Dr) is calculated based on the following mathematical formula 3 stored in the ROM.
[0045]
[Equation 3]
SW (Dr) = {(TAO (Dr) −Te1) / (Tw−Te1)} × 100 (%)
In step S190, the air mix door 17b opening degree SW (Pa) is calculated using Te2 estimated in step S180 based on the following mathematical formula 4 stored in the ROM.
[0046]
[Expression 4]
SW (Pa) = {(TAO (Pa) −Te2) / (Tw−Te2)} × 100 (%)
In step S210 (first temperature control means, second temperature control means of the present invention), the blower voltage VM determined and calculated in steps S150 to 180, the opening degree of the air volume adjusting door 70, the air mix doors 17a and 17b. Is output to each air conditioner so as to be in the opening degree SW (Dr), SW (Pa), and the blowing mode. In this example, the air temperature Te2 estimated as described above is used as the air conditioning information signal of the second passage 10b as apparent from the above formula 5, and therefore the second passage 10b in which the post-evaporator sensor 34 is not disposed. The temperature of the conditioned air in the second passage 10b can be controlled to the target blowing temperature TAO (Pa).
[0047]
Although not described in detail, the servo motor 10 is controlled so that the inside / outside air mode also becomes the control target value calculated in the ECU 30. Further, when the inside / outside air mode is selected as the inside / outside air mode with the inside / outside air switching switch, the inside / outside air mode is set.
(Second Embodiment)
By the way, in a normal vehicle air conditioner, when the detected value of the post-evaporator sensor 34 falls below a predetermined cooling degree (predetermined temperature, for example, 3 ° C.), the compressor 2 is stopped in order to prevent frosting on the evaporator 13. To do. However, when a sensor is installed only in the first passage 10a as in this example, if the compressor 2 is turned on / off by comparing the detected value (Te1) with the predetermined temperature in the sensor 34, the following problem occurs. There is.
[0048]
That is, since the air temperature Te2 in the second passage 10b may be lower than the air temperature Te1 in the first passage 10a as described above, frost adheres at the passage portion of the evaporator 13 corresponding to the first passage 10a. Although it is not, frost may have adhered in the passage part of the evaporator 13 corresponding to the 2nd channel | path 10b.
Therefore, in this example, the air temperature Te2 used in the first embodiment is used to control the electromagnetic clutch 104. FIG. 7 shows a flowchart showing the contents of this control. The estimation of the air temperature Te2 is the same as described above and will not be described here.
[0049]
First, in step S220, the lower value of the air temperature Te1 and the air temperature Te2 is selected and set as the air temperature Te3. In step S230, the operation of the compressor 2, that is, the on / off state of the electromagnetic clutch 104 is determined from the map shown in FIG. 7 based on the air temperature Te3. Here, TeLo is a temperature (degree of air cooling) at which frost adheres to the evaporator 13 and is a compressor stop temperature at which the electromagnetic clutch 104 is turned off and the compressor 2 is stopped. In this example, TeLo is 3 ° C. On the other hand, TeHi is a compressor operating temperature at which the electromagnetic clutch 104 is turned on to operate the compressor 2. In this example, it is 4 ° C. Thus, in this example, when the air temperature Te3 becomes lower than TeLo, the compressor 2 is stopped. For this reason, it can prevent beforehand that frost adheres in the whole area of the evaporator 13, and air volume falls.
[0050]
FIG. 8 is a flowchart showing the map of FIG. 7, which will be briefly described below. In step S231, it is determined whether or not the air temperature Te1 is lower than the air temperature Te2. If the air temperature Te1 is lower than the air temperature Te2, the process proceeds to step S232. In step S232, it is determined whether or not the air temperature Te1 is equal to or lower than TeLo. If YES is determined in this step, the process proceeds to step S233 to turn off the compressor 2.
[0051]
If it is determined as NO in step S232, the process proceeds to step S234, and it is determined whether or not the air temperature Te1 is equal to or higher than TeHi. When it is determined YES in step S234, the compressor 2 is turned on in step S235. If NO is determined in step S234, the process proceeds to step S233.
If NO is determined in step S231, that is, if the air temperature Te2 is lower than the air temperature Te1, the process proceeds to step S236. In step S236, it is determined whether or not the air temperature Te2 is equal to or lower than TeLo. If YES is determined in this step, the process proceeds to step S233.
[0052]
If it is determined as NO in step S236, the process proceeds to step S237 to determine whether or not the air temperature Te2 is equal to or higher than TeHi. When it is determined YES in step S237, the compressor 2 is turned on in step S238. If NO is determined in step S237, the process proceeds to step S233. Steps S220 and 230 constitute the intermittent control means of the present invention.
[0053]
(Third embodiment)
This example is a modification of step S180 in the first and second embodiments. That is, in the first and second embodiments, the air temperature Te2 is estimated based on the air volume of each passage and the air temperature Te1, but in order to accurately estimate the air temperature Te2, the air passing through the evaporator 13 is estimated. Therefore, it is necessary to know how much heat is absorbed by the evaporator 13 (heat transfer amount). Therefore, in this example, the temperature efficiency is used as the index of the heat transfer amount, and the air temperature Te2 is estimated based on the difference between the intake air temperature Tain sucked into the evaporator 13 and the air temperature Te1.
[0054]
The intake air temperature Tain is detected using an existing sensor in this example. Specifically, the ECU 30 recognizes the state of the inside / outside air mode. In the ECU 30, if the inside / outside air mode is the inside air mode, the intake air temperature Tain is the inside air temperature, and therefore, the detected value of the inside air temperature sensor 31 is used as the intake air temperature Tain. On the other hand, when the outside air mode is selected, since the intake air temperature Tain is the outside air temperature, the detected value of the outside air temperature sensor 32 is used as the intake air temperature Tain.
[0055]
In the first and second embodiments, the first air volume and the second air volume are calculated from the air distribution ratio X and the required blower voltage VM. These are the ventilation resistances of the passages 10a and 10b, that is, It depends on the blowing mode. For this reason, in this example, the first and second air volumes are accurately grasped according to the blowing mode.
FIG. 9 is a flowchart showing how the air temperature Te2 is estimated in this example. FIG. 10 is an explanatory diagram showing the temperature state of the air passing through the evaporator 13.
[0056]
In step S180d, the first air volume and the second air volume are calculated according to the blowing mode. Here, basically, the first air volume and the second air volume are calculated as in the above-described embodiments, but in this example, the first air volume and the second air volume are determined according to the blowing mode. In order to correct, the first air volume and the second air volume are multiplied by a coefficient to be converted into a final value.
[0057]
For example, in this example, in the blowing mode, the face mode, the bi-level mode, the foot mode, and the defroster mode are in order of decreasing ventilation resistance, so that the air volume is less likely to be output in the reverse order as shown in FIG. Yes. Therefore, when each of the blowing modes in the first passage and the second passages 10a and 10b is the face mode, the coefficient is 1, 0.8 in the bi-level mode, 0.7 in the foot mode, and 0 in the defroster mode. 6 is set in advance. By doing in this way, exact 1st air volume and 2nd air volume can be calculated according to each blowing mode.
[0058]
Next, in step S180e, the air side temperature efficiency η1 of the first passage 10a and the air side temperature efficiency η2 of the second passage 10b are determined. Here, the temperature efficiency η is generally used in the field of heat exchangers, and can be expressed as Equation 6 below.
[0059]
[Formula 6]
Temperature efficiency η =
(Suction air temperature Tain of the evaporator 13−Air temperature after passing through the evaporator 13) / (Suction air temperature Tain at the evaporator 13−Refrigerant temperature Trin of the evaporator 13)
And although this temperature efficiency (eta) changes on various conditions, as shown in FIG. 12, it becomes small, so that the airflow which passes the evaporator 13 becomes large. Then, the temperature efficiencies η1 and η2 are determined from FIG. 12 from the first air volume and the second air volume calculated in step S180d.
[0060]
In step S180f, the air temperature Te is estimated based on the first air volume, the second air volume, and the temperature efficiencies η1 and η2 calculated and determined in steps S180d and 180e. Specifically, this is performed as follows.
First, the temperature efficiencies η1 and η2 can be calculated not only from the map shown in FIG. 12 but also from equations 7 and 8 corresponding to the equation 6.
[0061]
[Expression 7]
Temperature efficiency η1 = (Tain-Te1) / (Tain-Trin)
[0062]
[Equation 8]
Temperature efficiency η2 = (Tain-Te2) / (Tain-Trin)
However, since the refrigerant temperature in the evaporator 13 changes substantially isothermally, the same inlet side refrigerant temperature Trin is used on both the first passage 10a and the second passage 10b.
When Equation 7 is modified, Trin is expressed by three of η1, Tain, and Te1. Next, when the above-mentioned Trin is substituted into Equation 8 and transformed, Te2 is finally expressed by Equation 9 below.
[0063]
[Equation 9]
Te2 = Tain-η2 / η1 (Tain-Te1)
For example, if Tain is 20 ° C., Te 1 is 10 ° C., the first air volume is larger than the second air volume and η 2> η 1, η 2 = 0.6 and η 1 = 0.3, Te 2 is 0 ° C. On the other hand, in this condition, if the first air volume is smaller than the second air volume and η2 <η1, η2 = 0.3, and η1 = 0.6, Te2 is 15 ° C.
[0064]
In this way, in this example, since the first air volume and the second air volume are calculated according to each blowing mode, the first air volume and the second air volume can be calculated with high accuracy, and the air temperature Te2 can be estimated with higher accuracy. In this example, since the air temperature Te2 is estimated based on the difference between the intake air temperature Tain and the air temperature Te1, the air temperature Te2 can be estimated with higher accuracy.
[0065]
(Other embodiments)
In each of the above embodiments, the present invention is applied to the left and right independent control type in which the air conditioning case 12 is partitioned into two passages, but the present invention is not limited to this and can be applied to the following.
For example, when the air conditioning case is not divided into two partitions and the air mixing door has one air conditioner and the air volume adjusting door 70 as described above is arranged and the solar radiation enters the right side of the vehicle, The air distribution door may be controlled so as to increase the amount of air blown from the air outlet on the right side of the vehicle so as to cancel the amount of heat.
[0066]
In the above embodiment, the temperature of the conditioned air is controlled by the air mix doors 17a and 17b that adjust the mixing ratio of the cold air and the hot air, but the present invention adjusts the amount of hot water supplied to the heater core 14 so-called reheat type. The present invention may be applied to an air conditioner, or may be one that controls the temperature of hot water supplied to the heater core 14.
Moreover, in each said embodiment, you may install the air volume adjustment door 70 in the upstream of the air mix doors 17a and 17b). For example, the air volume adjustment door 70 may be disposed on the downstream side of the evaporator 13. In this case, the partition part 15 becomes unnecessary on the upstream side of the evaporator 13.
[0067]
Moreover, in each said embodiment, although the air volume of the 1st channel | path 10a and the 2nd channel | path 10b was controlled by the air volume adjustment door 70, even if it arrange | positions a fan in each of the 1st channel | path 10a and the 2nd channel | path 10b, this The invention is applicable.
Moreover, in each said embodiment, although the applied voltage of the blower motor 9 of the said air blower 7 was varied, you may make it control the rotation speed of the blower mode 9 by pulse width modulation, for example.
[0068]
In each of the above embodiments, when the first air volume and the second air volume are calculated, the air suction resistance differs depending on the inside / outside air mode, so the inside / outside air mode may be considered.
Further, in each of the embodiments described above, the air conditioning control is independently performed on the driver seat side and the passenger seat side. However, the present invention uses the vehicle air conditioner, for example, to conditioned air in the first passage 12a. Can be applied to an air conditioning zone on the front side of the vehicle interior, and the conditioned air in the second passage 12b is sent to the air conditioning zone on the rear side of the vehicle interior.
[0069]
Further, in each of the embodiments described above, the post-evaporator sensor 34 detects the air temperature immediately after passing through the evaporator 13, but it may detect the temperature of the cooling fins of the evaporator 34.
In each of the above embodiments, the compressor 2 may be of a variable capacity type. If the compressor 2 is of the external variable capacity type, the compressor capacity may be varied based on the lower air temperature determined in step S231 so that frost does not adhere to the evaporator 13.
[0070]
Moreover, although the example which applied this invention to the vehicle air conditioner was given in each said embodiment, this invention is not limited to a vehicle air conditioner, It can apply to any air conditioner.
[Brief description of the drawings]
FIG. 1 is an overall configuration diagram of a vehicle air conditioner according to each embodiment of the present invention.
FIG. 2 is a diagram illustrating a control system in each of the embodiments.
FIG. 3 is a flowchart showing the contents of control in each of the embodiments.
FIG. 4 is a map diagram showing how to determine the blower voltages VM (Dr) and VM (Pa) in each of the embodiments.
FIG. 5 is a map diagram for determining a blowing mode in each of the embodiments.
FIG. 6 is a flowchart showing how to estimate an air temperature Te1 in the first and second embodiments.
FIG. 7 is a flowchart showing an example of using the air temperature Te1 in the second embodiment.
FIG. 8 is a flowchart showing an example of use of air temperature Te1 in the second embodiment.
FIG. 9 is a flowchart showing how to estimate an air temperature Te1 in the third embodiment.
FIG. 10 is an explanatory diagram for explaining a method of estimating an air temperature Te1 in the third embodiment.
FIG. 11 is an explanatory diagram showing that the first air volume and the second air volume differ according to the blowing mode in the third embodiment.
FIG. 12 is a map diagram showing how to set the temperature efficiency, the first air volume, and the second air volume in the third embodiment.
[Explanation of symbols]
10a ... 1st passage, 10b ... 2nd passage, 13 ... Evaporator,
30 ... Control device, 34 ... Sensor after evaporator, 70 ... Air volume adjustment door.

Claims (7)

A first passage (10a) for blowing conditioned air toward the first air-conditioning zone;
A second passage (10b) for blowing conditioned air toward the second air-conditioning zone;
A cooling heat exchanger (13) disposed in the first passage (10a) and the second passage (10b) for cooling the air passing therethrough;
These are applied to an air conditioner having air volume control means (70, 70c, 30) for controlling the air volume of the conditioned air blown into the first passage (10a) and the second passage (10b) to different values,
Cooling that is arranged in the first passage (10a) on the downstream side of the cooling heat exchanger (13) and detects the first cooling degree (Te1) of air in the cooling heat exchanger (13). A degree detection means (34);
Based on at least the first air volume blown into the first passage (10a), the second air volume blown into the second passage (10b), and the first cooling degree (Te1), the second passage. An air conditioner comprising: a cooling degree estimating means (S180) for estimating a second cooling degree (Te2) of air in the cooling heat exchanger (13) in (10b). The estimation means (S180)
When the first air volume is greater than the second air volume, the second cooling degree (Te2) is estimated to be greater than the first cooling degree (Te1), and when the first air volume is less than the previous second air volume, The air conditioner according to claim 1, wherein the second cooling degree (Te2) is estimated to be smaller than the first cooling degree (Te1). Intermittent means (104) for intermittently supplying the refrigerant to the cooling heat exchanger (13);
When the larger one of the first cooling degree (Te1) and the second cooling degree (Te2) becomes larger than a predetermined cooling degree in which frost adheres to the cooling heat exchanger (13), the intermittent means (104) The air conditioner according to claim 1 or 2, further comprising an intermittent control means (S220, S230) for stopping the refrigerant supply. Of the first passage (10a) and the second passage (10b), disposed on the air downstream side of the cooling heat exchanger (13), heats the air that has passed through the cooling heat exchanger (13). A heat exchanger (14) for heating,
A first temperature adjustment member that adjusts the temperature of the air in the first passage (10a) by adjusting the first air heating amount in the first passage (10a) by the heating heat exchanger (14). 17a)
First target temperature calculation means (S190) for calculating a first target temperature (TAO (Dr)) of air in the first passage (10a);
First temperature control means (S210) for controlling the first temperature adjusting member (17a) based on at least the first target temperature (TAO (Dr)) and the first cooling degree (Te1);
A second temperature adjusting member that adjusts the temperature of the air in the second passage (10b) by adjusting the second air heating amount in the second passage (10b) by the heating heat exchanger (14). 17b)
Second target temperature calculating means (S200) for calculating a second target temperature (TAO (Pa)) of air in the second passage (10b);
The second temperature control means (S210) for controlling the second temperature adjusting member (17b) based on at least the second target temperature and the second cooling degree (Te2). 4. The air conditioner according to any one of 4. The estimation means (S180) is configured to determine the second air cooling degree based on the difference between the intake air temperature (Tain) of the air flowing into the cooling heat exchanger (13) and the first cooling degree (Te1). (Te2) is estimated, The air conditioner as described in any one of Claim 1 thru | or 4 characterized by the above-mentioned. The blowing mode can be set independently so that the blowing part of the conditioned air is different in the first air-conditioning zone and the second air-conditioning zone,
6. The first and second air volumes are calculated with corrections according to the blowing mode of the first air conditioning zone and the blowing mode of the second air conditioning zone. The air conditioner as described in any one. A blower (7) that generates conditioned air to be blown into the first passage (10a) and the second passage (10b) and is driven by one electric motor (9);
First air volume determining means (S140) for determining a first target air volume (VM (Dr)) of the conditioned air blown into the first passage (10a);
Second air volume determining means (S140) for determining a second target air volume (VM (Pa)) of the conditioned air blown into the second passage (10b);
The conditioned air generated by the blower is distributed to the first passage (10a) and the second passage (10b), and the amount of air that controls the proportion of the air flow to the first passage (10a) and the second passage (10b). A ratio control member (70),
The air volume control means (70, 70c, 30) is configured so that the blower (7) and the air volume ratio satisfy the first target air volume (VM (Dr)) and the second target air volume (VM (Pa)). The air conditioner according to any one of claims 1 to 6, wherein the control member (70) is controlled.

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