JPH0979652A - Air conditioning equipment - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make the temperature of air let out into a room approximate to a prescribed target indoor temperature in an optimum state at all times, irrespective of the quantity of air passing through an indoor heat exchanger. SOLUTION: In a cooling mode, a control device 39 determines a target increased-decreased number Δfz of revolutions in accordance with the deviation of an actual temperature of air having passed through an indoor heat exchanger 22 from a target temperature thereof and further determines a corrective target increased-decreased number Δf of revolutions so that the Δfz be made large as the quantity of the air becomes large, on the basis of a set position of an air quantity setting lever. Then, it controls an inverter 38 so that the number of revolutions of a compressor 25 be increased or decreased by the Δf. According to this constitution, the temperature of the air having passed the indoor heat exchanger 22 is fixed substantially irrespective of the quantity of the air passing through the indoor heat exchanger 22 and, therefore, the temperature of air let out into a room is made to approximate to a prescribed target indoor temperature in an optimum state at all times.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention controls the number of revolutions of a compressor in a refrigeration cycle according to a deviation between a predetermined target room temperature and the temperature of air blown into the room, thereby blowing air into the room. An air conditioner configured to regulate temperature.

[0002]

2. Description of the Related Art As a conventional technique of the above air conditioner, there is one disclosed in Japanese Patent Laid-Open No. 6-174291. According to this, for example, when the set outlet air temperature and the outlet air temperature of the indoor heat exchanger are both stable at T0 and the set outlet air temperature is changed to Ts, Ts
If the absolute value of the deviation between | and T0 (| Ts-T0 |) is greater than the predetermined value, the increase / decrease amount of the compressor speed is determined according to this deviation (| Ts-T0 |), and only this increase / decrease amount is determined. By changing the number of revolutions of the compressor, the blown air temperature is made to approach the set blown air temperature Ts.

[0003]

However, in the case of the above-mentioned prior art, the deviation (| Ts-T0
Since it is determined only according to |), the following problems occur. For example, an evaporator of the refrigeration cycle is used as an indoor heat exchanger, an air conditioner that cools the room indoors with this evaporator, and a condenser of the refrigeration cycle is used as an indoor heat exchanger,
In the air conditioner for indoor heating with this condenser, when the compressor rotation speed is changed by the increase / decrease amount determined according to the deviation (| Ts-T0 |), the passage through the indoor heat exchanger at this time Since the air volume is the predetermined air volume, the approach of the blown air temperature to the set blown air temperature Ts is as shown in FIG.
It is assumed that it is optimum as shown by the solid line in (a) or FIG.

Incidentally, FIG. 22 (a) shows the behavior of the blown air temperature during the indoor cooling, and FIG. 23 (a) shows the behavior of the blown air temperature during the indoor heating. However, when the indoor heat exchanger passing air volume at this time is larger than the predetermined air volume, as compared with when the indoor heat exchanger passing air volume is the predetermined air volume, the evaporator or the condenser has insufficient cooling capacity or insufficient heating capacity. As a result, the speed at which the blown air temperature approaches the set blown air temperature Ts is
2 (a) and FIG. 23 (a) are delayed as indicated by the alternate long and short dash line.

On the contrary, when the air volume passing through the indoor heat exchanger at this time is smaller than the predetermined air volume, the capacity of the evaporator or the condenser becomes excessive as compared with when the air volume passing through the indoor heat exchanger is the predetermined air volume. Therefore, the speed at which the blown air temperature approaches the set blown air temperature Ts becomes faster, but since the temperature change rate is too large, overshoot occurs as shown by the broken lines in FIGS. 22 (a) and 23 (a). I will end up.

22 (b) and 23 (b) show the behavior of the compressor rotation speed corresponding to the cases of FIG. 22 (a) and FIG. 23 (b). Therefore, in view of the above problems, an object of the present invention is to make the temperature of air blown into a room approach a predetermined target room temperature in an optimum state at all times, regardless of the air volume passing through the indoor heat exchanger. .

[0007]

SUMMARY OF THE INVENTION To achieve the above object, claims 1 to 6 are provided.
In the invention described above, the deviation between the predetermined target indoor temperature and the temperature of the air blown into the room, and the indoor heat exchanger (evaporator in the invention of claim 1, condenser in the invention of claim 3, claim 5 In the invention described, the target rotation speed of the compressor is determined according to the amount of air passing through the hot water heat exchanger, and the drive that drives the compressor so that the actual rotation speed of the compressor is the target rotation speed. Control means. At this time, the target rotation speed is determined to be higher in accordance with an increase in the air volume passing through the indoor heat exchanger.

According to this, both when performing indoor cooling and when performing indoor heating, when the amount of air passing through the indoor heat exchanger is large, the number of revolutions of the compressor becomes high, and conversely, when passing through the indoor heat exchanger. When the air volume is small, the compressor speed is low.
Therefore, the temperature of the air passing through the indoor heat exchanger is almost constant regardless of the amount of air passing through the indoor heat exchanger, so the temperature of the air blown into the room is always the optimum target indoor temperature. Approach.

[0009]

BEST MODE FOR CARRYING OUT THE INVENTION Next, a first embodiment in which the present invention is applied to an air conditioner for an electric vehicle will be described with reference to FIGS. First, the overall configuration of this embodiment will be described with reference to FIG. The indoor unit 1 includes a duct 2 as an air passage that guides air into the vehicle interior. The inside / outside air switching means 3 and the air blowing means 4 are provided in the air upstream side portion of the duct 2.
Is connected.

The inside / outside air switching means 3 includes an inside air inlet 5 and an outside air inlet 6 formed on the air upstream side of the duct 2, and an inside / outside air switching door 7 for selectively opening and closing the inlets 5, 6.
With. The inside / outside air switching door 7 is driven by a servo motor (not shown). The blowing unit 4 includes a fan case 8, a fan 9 and a fan motor 10. The fan motor 10 rotates and drives the fan 9 by being energized by a battery (not shown) which is a DC power source, and blows the inside air or the outside air into the vehicle compartment through the duct 2.

At the air downstream end of the duct 2, a center face outlet 11 for blowing the air passing through the duct 2 from the center of the front part of the passenger compartment toward the upper body of the passenger, and the air from both sides of the front part of the passenger compartment. A side face outlet 12 that blows out toward the upper half of the body or the side glass, a foot outlet 13 that blows out the air toward the feet of the occupant, and a defroster outlet 14 that blows out the air toward the inner surface of the window glass. ing.

At the upstream side portions of the air passages 15 to 17 leading to the center face outlet 11, the foot outlet 13, and the defroster outlet 14, a center face door 18 for adjusting the air flow rate to each outlet is provided. , A foot door 19 and a defroster door 20 are provided. The center face outlet 11 and the side face outlet 12 are provided with an occupant opening / closing door 21 for manually adjusting the amount of air blown according to the occupant's preference.

Inside the duct 2, an indoor heat exchanger 22 for cooling and an indoor heat exchanger 23 for heating, which exchange heat between the refrigerant flowing inside the duct 2 and the air inside the duct 2, are provided on the entire surface of the duct 2. Has been. Each of these heat exchangers 22 and 23 is a heat exchanger forming a part of a refrigeration cycle 24 described later, the heat exchanger 22 functions as an evaporator in a cooling mode described later, and the heat exchanger 23 is It functions as a condenser in the heating mode described later.

The refrigerating cycle 24 is a heat pump type refrigerating cycle for cooling and heating the passenger compartment by the indoor heat exchanger 22 for cooling and the indoor heat exchanger 23 for heating. In addition to these heat exchangers 22 and 23, In addition, the compressor 25 and the outdoor heat exchanger 2
6, a cooling decompression device 27, a heating decompression device 28, an accumulator 29, and a four-way valve 30 that switches the flow direction of the refrigerant, which are connected by a refrigerant pipe 31. In the figure, 32 and 33 are electromagnetic valves, 34 and 35 are one-way valves, and 36 is an outdoor fan.

The compressor 25 sucks, compresses, and discharges the refrigerant when driven by the electric motor 37. The electric motor 37 is arranged in the hermetically sealed case integrally with the compressor 25, and the rotation speed thereof is continuously changed by being controlled by the inverter 38. The inverter 38 is energized and controlled by the control device 39.

As shown in FIG. 2, the control device 39 has an air cooling degree in the indoor heat exchanger 22 for cooling (specifically, an air temperature immediately after passing through the heat exchanger 22).
Each signal from the after-passage air temperature sensor 40 that detects the temperature, the compressor rotation speed sensor 41 that detects the rotation speed of the compressor 25, and the high pressure sensor 42 that detects the high pressure of the refrigeration cycle is input, and the control panel Each signal from each lever and switch of 43 is also input.

As shown in FIG. 3, the control panel 43 sets a blowout mode setting lever 44 for setting each blowout mode, an air volume setting lever 45 for setting the amount of air blown into the passenger compartment, and an inside / outside air switching mode. The inside / outside air switching lever 46, the cooling switch 47a for setting the refrigeration cycle 24 in the cooling mode, and the heating switch 47b for setting the heating mode.
And a temperature setting lever 48 for setting a vehicle interior target temperature.

There are specifically five setting modes by the air volume setting lever 45. In addition to the mode for stopping the fan 9 (OFF), there are four modes for driving the fan 9 (Lo, Me1, Me2, Hi). There is. Needless to say, the rotation speed of the fan 9 in the setting mode of the air volume setting lever 45 is Lo <Me1 <Me2 <Hi.

Further, the cooling switch 47a and the heating switch 47b are configured not to be turned on at the same time. Then, the cooling switch 47a and the heating switch 47b
In order to turn off both of the switches 47 and 47 at the same time, one of the switches 47a and 47b may be turned on, and the other may be lightly pressed. In this case, the blower mode in which the compressor 25 stops is instructed.

A sliding terminal (not shown) is connected to the temperature setting lever 48, and the temperature setting lever 48
3 is moved in the left-right direction in FIG. 3, and in conjunction with this, the sliding terminal slides on the resistance element to which a predetermined voltage is applied to both ends. Then, the control device 39 reads the set position of the temperature setting lever 48 by reading the voltage output from the sliding terminal.

A well-known microcomputer including a CPU, ROM, RAM and the like (not shown) is provided inside the control device 39, and signals from the sensors 40 to 42 and signals from the control panel 43 are It is input to the microcomputer via an input circuit (not shown) in the control device 39. Then, this microcomputer executes the processing described later, and controls each electric driving means such as the inverter 38 based on the processing result.
The control device 39 is supplied with power from a battery (not shown) when a key switch (not shown) of the automobile is turned on.

When the passenger compartment passenger turns on the cooling switch 47a, the microcomputer controls the four-way valve 30 and the solenoid valve 32 to put the refrigeration cycle 24 into the cooling mode. The flow of the refrigerant in this cooling mode is as follows: compressor 25 → four-way valve 30 → outdoor heat exchanger 2
The order is 6 → cooling decompression device 27 → cooling indoor heat exchanger 22 → accumulator 29 → compressor 25.

When the heating switch 47b is turned on by an occupant in the passenger compartment, the microcomputer controls the four-way valve 30 and the solenoid valves 32 and 33 to put the refrigeration cycle 24 into the heating mode. The flow of the refrigerant in the heating mode is as follows: compressor 25 → four-way valve 30 → indoor heating heat exchanger 23 → heating decompression device 28 → outdoor heat exchanger 26 →
The order is accumulator 29 → compressor 25.

Next, the control process of the inverter 38 performed by the microcomputer will be described with reference to the flowchart of FIG. First, in step 110, the internal RAM of the microcomputer is initialized. Then, in the next step 120, the sensors 4
The signals from 0 to 42 and the signals from the levers and switches of the control panel 43 are read.

Then, in the next step 130, it is determined whether or not the cooling switch 47a is turned on. If YES is determined here, in the next step 140, the temperature immediately after passing through the indoor heat exchanger for cooling 22 is determined according to the position of the temperature setting lever 48 based on the characteristic of FIG. 5 stored in the ROM. Determine the target temperature TEO of the air. here,
The target temperature TEO is determined to be 3 (° C.) when the temperature setting lever 48 is at the left end of FIG. 3, and is determined to be 20 (° C.) when the temperature setting lever 48 is at the right end of FIG.

Then, in the next step 150, the deviation En between the target temperature TEO and the actual air temperature TE detected by the post-passage air temperature sensor 40 is calculated based on the following formula 1.

[0027]

## EQU1 ## En = TEO-TE Then, in the next step 160, the deviation change rate Edot is calculated based on the following mathematical formula 2.

[0028]

## EQU00002 ## Edot = En-En-1 Here, since En is updated every 4 seconds, En-1 is En.
Is 4 seconds before. Next, in step 170, based on the membership function of FIG. 6 and the rules of FIG.
Target increase / decrease speed Δ in En and Edot calculated in
Calculate fz (rpm). Here, this target increase / decrease rotation speed Δfz
Is the number of revolutions of the compressor 25 that increases or decreases with respect to the target number of revolutions fn-1 (rpm) 4 seconds before.

Specifically, from the CF1 obtained in FIG. 6 (a) and the CF2 obtained in FIG. 6 (b), the input conformance CF is obtained based on the following equation 3, and the input conformance CF and FIG. Δfz is calculated based on the following equation 4 from the rule value of

[0030]

(3) CF = CF1 × CF2

[0031]

Δfz = Σ (CF × rule value) / ΣCF Then, in the next step 180, as shown in FIG.
The corrected target increase / decrease rotation speed Δf is calculated by multiplying the target increase / decrease rotation speed Δfz by a coefficient that differs depending on the setting position of the air volume setting lever 45. In the present embodiment, the correction target increase / decrease rotation speed Δf is set as the coefficient of FIG. 8 as the rotation speed of the fan 9 becomes higher (as the air volume passing through the indoor heat exchanger 22 for cooling becomes larger). Is set to be large.

Then, in the next step 190, the target rotational speed fn of the compressor 25 is calculated based on the following equation (5).

[0033]

Fn = fn-1 + Δf Then, in the next step 200, the current input to the inverter 38 is set so that the compressor rotation speed detected by the compressor rotation speed sensor 41 becomes the target rotation speed fn. Control.
Then, the process returns to step 120.

On the other hand, if NO at step 130, the heating switch 47b is reached at step 210.
It is determined whether or not is turned on. If YES is determined here, in step 220, the target high pressure PCO is determined according to the position of the temperature setting lever 48 based on the characteristics of FIG. 9 stored in the ROM. Here, the target high pressure PCO is determined to be 8 (kg / cm ² G) when the temperature setting lever 48 is at the left end in FIG. 3, and is 16 when the temperature setting lever 48 is at the right end in FIG.
(Kg / cm ² G).

Then, in the next step 230, the deviation Dn between the target high pressure PCO and the actual high pressure PC detected by the discharge pressure sensor 42 is calculated based on the following equation (6).

[0036]

## EQU6 ## Dn = PCO-PC Then, in the next step 240, the deviation change rate Ddot is calculated based on the following mathematical expression 7.

[0037]

## EQU7 ## Ddot = Dn-Dn-1 Here, since Dn is updated every 4 seconds, Dn-1 becomes a value 4 seconds before Dn. Next, step 250
In accordance with the membership function of FIG. 10 and the rule of FIG. 11 stored in the ROM, the above step 230,
The target increase / decrease rotation speed Δfz (rpm) at Dn and Ddot calculated at 240 is calculated. The calculation method of the target increase / decrease rotation speed Δfz in step 250 is as follows.
Since it is the same as that of No. 1, the description is omitted.

Then, in the next step 260, as in the case of step 180, as shown in FIG. 8, correction is performed by multiplying the target increasing / decreasing rotational speed Δfz by a coefficient which differs depending on the setting position of the air volume setting lever 45. The target increase / decrease rotation speed Δf is calculated. Then, in steps 190 and 200,
After performing the processing in step 120, the processing returns to step 120.

When it is determined in step 210 that the heating switch 47b is not turned on, the operation of the compressor 25 is stopped in step 270 to set the blower mode. Here, a specific calculation example of the target rotation speed fn will be described. For example, if Dn = 6.25 in the heating mode,
From FIG. 6A, CF1 has NB = 0, NS = 0, and ZO =
0, PS = 0.75, PB = 0.25. Also, D
When dot = -0.15, NB = 0, N from Fig. 6 (b)
S = 0.5, ZO = 0.5, PS = 0, PB = 0.

Therefore, ΣCF, which is the denominator of the above equation 4,
Is 0.75 × 0.5 + 0.75 × 0.5 + 0.25 ×
It becomes 0.5 + 0.25 * 0.5 = 1. In addition, Σ (CF × rule value), which is the numerator of the equation 4, is 0.75 ×
0.5 x 0 + 0.75 x 0.5 x 100 + 0.25 x
0.5 × 300 + 0.25 × 0.5 × 600 = 150. As a result, Δfz = 150.

Further, if the setting position of the air volume setting lever 45 at this time is Me2, as can be seen from FIG.
= 125. Therefore, the compressor rotation speed fn is increased by 125 (rpm) from the rotation speed fn-1 4 seconds before. When ΣCF = 0, Δf = 0. By controlling the energization of the inverter 38 as described above, in the cooling mode, the air temperature immediately after passing through the indoor heat exchanger 22 for cooling approaches the target temperature TEO, and thus the temperature of the air blown into the vehicle interior is set to the temperature setting lever. The target temperature set by 48 is approached. Further, in the heating mode, the high pressure approaches the target high pressure PCO, and the temperature of the air blown into the vehicle interior approaches the target temperature set by the temperature setting lever 48.

The above steps constitute means for realizing the respective functions. Next, a specific operation when the cooling mode is set by the cooling switch 47a and the target temperature TEO at the time of starting the air conditioner (time t = 0) is lower than the actual temperature TE will be described with reference to FIG. . In this case, at the initial stage of starting the air conditioner, it is necessary to increase the compressor rotation speed to increase the cooling capacity.
Both Δf and Δf are calculated as positive values, and the compressor rotation speed rises.
As shown in (b), the air volume increases as the air volume set by the air volume setting lever 45 increases.

Therefore, the temperature of the air that has passed through the indoor heat exchanger 22 for cooling is always substantially constant regardless of the size of the air volume. Therefore, how the temperature of the air blown into the vehicle approaches the target temperature set by the temperature setting lever 48 is as shown in FIG.
As shown in (a), the air temperature TE that has passed through the cooling heat exchanger 22 is always optimum, as is the way the air temperature TE approaches the target temperature TEO.

The specific operation when the heating mode is set by the heating switch 47b and the target high pressure PCO is higher than the actual high pressure PC when the air conditioner is started (time t = 0) will be described with reference to FIG. explain. In this case, since the compressor rotation speed must be increased to increase the heating capacity at the initial stage of starting the air conditioner, both Δfz and Δf are calculated as positive values, and the compressor rotation speed increases. As shown in FIG. 13B, this degree of increase increases as the air volume set by the air volume setting lever 45 increases.

Therefore, the temperature of the air passing through the heating indoor heat exchanger 23 is always substantially constant regardless of the air volume. Therefore, how to approach the temperature of the air blown into the vehicle interior to the target temperature set by the temperature setting lever 48 is as shown in FIG.
Target high pressure PCO of actual high voltage PC as shown in (a)
It will always be optimal as well as how to approach. As described above, in the present embodiment, the target increase / decrease rotation speed Δfz is calculated according to the deviation between the predetermined target vehicle interior temperature and the temperature of the air blown into the vehicle interior, and further passes through the indoor heat exchanger. The corrected target increase / decrease rotation speed Δfz is calculated so that the target increase / decrease rotation speed Δfz increases as the air flow rate increases. Therefore, regardless of the air volume passing through the indoor heat exchanger, The blown air temperature always approaches the predetermined target vehicle interior temperature in an optimal state.

Next, a second embodiment of the present invention will be described with reference to FIGS. The same parts as those in the first embodiment are designated by the same reference numerals as those in the first embodiment, and the description thereof will be omitted. In the present embodiment, the refrigerant water heat exchanger 49, the heater core 50, the hot water tank 51,
Also, a hot water circuit 54 is formed by connecting the water pump 52 with a hot water pipe 53.

Of these, the refrigerant water heat exchanger 49 is formed by bending a hollow cylindrical pipe 49a made of an aluminum alloy in a meandering manner. The internal passage 49b of the pipe 49a is connected to the hot water pipe 53, and a plurality of passages 49c are formed in the thick portion of the pipe 49a.
Is connected to the refrigerant pipe 31. Therefore, the passage 4
9b functions as a hot water passage through which hot water in the hot water circuit 54 flows, and the passage 49c functions as a refrigerant passage through which the refrigerant in the refrigeration cycle 24 flows.

Further, the heater core 50 is arranged at the portion where the indoor heating heat exchanger 23 (FIG. 1) is arranged in the first embodiment, and the hot water flowing inside the heater core 50, It is a hot water heat exchanger that exchanges heat with the air in the duct 2. As described above, the hot water flows in the passage 49b and the refrigerant flows in the passage 49c, so that the hot water and the refrigerant are heat-exchanged in the refrigerant water heat exchanger 49.
Then, the refrigerant in the refrigeration cycle 24 is condensed in the passage 49c. That is, the passage 49c functions as a condenser. Then, the hot water in the hot water circuit 54 is heated in the passage 49b.

Although not shown in FIG. 14, like the first embodiment, the compressor 25 is the same as the compressor 25.
Is driven by an electric motor (not shown) which is integrally arranged in the sealed case (the same as the electric motor 37 in FIG. 1) and is controlled by an inverter (not shown) so that the rotation speed continuously changes. Then, the energization of this inverter is controlled by the control device 39 (FIG. 16).

Further, as shown in FIG. 16, the control device 39 includes the after-passage air temperature sensor 40, the compressor rotation speed sensor 41, and each lever of the control panel 43.
In addition to the signals from the switch, an inside air temperature sensor 55 that detects the inside air temperature in the vehicle compartment, an outside air temperature sensor 56 that detects the outside air temperature, a solar radiation sensor 57 that detects the amount of solar radiation applied to the vehicle interior, and a heater core 50. Each signal is input from a water temperature sensor 58 that detects the temperature of the hot water flowing into the inside.

Next, the control process of the inverter performed by the microcomputer in the control device 39 will be described with reference to FIG.
A description will be given based on the flowchart. It should be noted that, here, only the parts different from the first embodiment will be described. Further, the control device 39 changes the flow of the refrigerant in the refrigeration cycle 24 in the heating mode from the compressor 25 → the refrigerant water heat exchanger 49 → the heating decompression device 28 → the outdoor heat exchanger 26 →
The solenoid valves 32 and 33 are controlled so that the accumulator 29 and the compressor 25 are arranged in this order.

When YES is determined in the step 210, the target blow-out temperature TAO blown out into the vehicle compartment is calculated in the following step 215 based on the following equation (8).

[0053]

## EQU8 ## TAO = Kset × Tset−Kr × Tr−Kam ×
Tam−Ks × Ts−C where Tset is a set temperature determined by the setting position of the temperature setting lever 48, Tr is the inside air temperature detected by the inside air temperature sensor 55, Tam is the outside air temperature detected by the outside air temperature sensor 56, And Ts are the amount of solar radiation detected by the solar radiation sensor 57. Kset, Kr, Kam and Ks are gains, respectively, and C is a constant.

Then, in the next step 225, the target warm water temperature TWO is calculated based on the following mathematical expression 9.

[0055]

## EQU9 ## TWO = (TAO-Tin) /. Phi. (V) + Tin Here, Tin is the air temperature on the suction side of the heater core 50, and in the present embodiment, the post-passage air temperature sensor 4 is used.
The detected value of 0 is used instead. Further, φ (V) is a temperature efficiency that varies depending on the air volume V by the fan 9, and the relationship between this temperature efficiency φ (V) and the air volume V is as shown in FIG. 18. The relationship shown in FIG. 18 is stored in the ROM.

Then, in the next step 230, the deviation Dn between the target warm water temperature TWO and the actual warm water temperature TW detected by the water temperature sensor 58 is calculated based on the following formula 10.

[0057]

## EQU10 ## Dn = TWO-TW After that, the processing from step 240 onward is performed. According to the present embodiment as described above, the compressor 2 is controlled by controlling the inverter.
By controlling the number of rotations of 5, the refrigerant water heat exchanger 4
The hot water heating amount in 9 is controlled, by extension, the air heating capacity in the heater core 50 is controlled, and the temperature of the air blown into the vehicle compartment is controlled.

In this embodiment as well, since the processing of steps 180 and 260 is performed, the behavior of the hot water temperature in the heating mode is almost the same as that when the high pressure in FIG. 13 is replaced with the hot water temperature. . Next, a third embodiment of the invention will be described with reference to FIGS. In each of the above embodiments, a predetermined target vehicle interior temperature,
Using fuzzy inference that incorporates parameters according to the deviation from the temperature of the air blown into the passenger compartment, the target increase / decrease speed Δfz
Although the target increase / decrease rotational speed Δfz is corrected according to the setting position of the air volume setting lever 45, the fuzzy inference further includes a parameter regarding the setting position of the air volume setting lever 45. The target increase / decrease rotation speed Δf may be calculated using fuzzy inference. In this case, needless to say, the fuzzy inference is determined so that the target increase / decrease rotation speed Δf increases as the air volume passing through the indoor heat exchanger increases.

Then, as the control processing of the inverter,
In steps 170 and 250, the air volume setting lever 45
After the target rotation speed Δf of the compressor 25 is calculated by using the fuzzy inference that incorporates the parameter related to the setting position of, the processing of step 190 may be directly performed. Here, the processing in step 250 when the system of the first embodiment is used is as follows.

First, CF1 obtained in FIG. 19A and FIG.
CF2 found in 9 (b) and CF3 found in FIG. 19 (c)
Then, the input conformance CF is obtained based on the following formula 11, and Δf is calculated from the input conformance CF and the rule values of FIGS.

[0061]

[Equation 11] CF = CF1 × CF2 × CF3 As described above, also in the present embodiment, not only the deviation between the predetermined target vehicle interior temperature and the temperature of the air blown into the vehicle interior, but also the passage through the indoor heat exchanger. Since the target increase / decrease rotation speed Δf is calculated even in accordance with the air flow rate, the temperature of the air blown into the vehicle interior is irrespective of the air flow rate passing through the indoor heat exchanger.
The target vehicle interior temperature is always approached in an optimum state.

(Other Embodiments) In the first embodiment, the target high pressure PCO is determined according to the set position of the temperature setting lever 48 in the heating mode. Target air temperature TC immediately after passing 23
O (° C.) may be determined. In this case, a temperature sensor for detecting the air temperature immediately after passing through the indoor heating heat exchanger 23 is provided, and the deviation Dn is set to the target temperature TCO.
And the difference between the temperature and the detected value TC of the sensor.

In this embodiment, as shown by the parentheses in FIG. 9, the controller has a temperature setting lever 48 shown in FIG.
When it is at the left end, the target temperature TCO is determined to be 30 (° C.), and when it is at the right end in FIG.
(° C). In each of the above embodiments, the deviation En (Dn) between the target value and the actual value and the deviation change rate Edot
I calculated Δf from (Ddot) using fuzzy inference.
Δf may be obtained by using P control, PI control, PID control, or the like. Also, when fuzzy inference is used, the rule is not limited to the 5 × 5 rule, and a finer rule or a rough rule may be used.

The coefficients shown in FIG. 8 may have other values. The point is that this coefficient may be increased as the amount of air passing through the indoor heat exchanger increases.

[Brief description of drawings]

FIG. 1 is an overall configuration diagram according to a first embodiment of the present invention.

FIG. 2 is a block diagram of a control system in the above embodiment.

FIG. 3 is a front view of the control panel in the above embodiment.

FIG. 4 is a control flowchart for the inverter in the above embodiment.

FIG. 5 is a map showing a relationship between a temperature setting lever position and a target temperature TEO in the above embodiment.

FIG. 6 is a membership function used by the control device in the above embodiment in the cooling mode.

FIG. 7 is a fuzzy rule table used by the control device in a cooling mode.

FIG. 8 is a correspondence table showing the relationship between the air volume setting lever position and the correction target increase / decrease rotation speed Δf in the above embodiment.

FIG. 9 is a map showing the relationship between the temperature setting lever position and the target high pressure PCO (target temperature TCO) in the above embodiment.

FIG. 10 is a membership function used by the control device in the heating mode.

FIG. 11 is a fuzzy rule table used by the control device in a heating mode.

FIG. 12 (a) is a post-passage air temperature TE in the cooling mode.
And (b) is a graph showing the behavior of the compressor rotation speed in the cooling mode.

13A is a graph showing the behavior of the high-pressure PC in the heating mode, and FIG. 13B is a graph showing the behavior of the compressor rotation speed in the heating mode.

FIG. 14 is an overall configuration diagram according to a second embodiment of the present invention.

15 is a cross-sectional view taken along the line AA of FIG.

FIG. 16 is a block diagram of a control system in the second embodiment.

FIG. 17 is a control flowchart for the inverter in the second embodiment.

FIG. 18 is a graph showing the relationship between temperature efficiency φ (V) and air volume V.

FIG. 19 is a membership function used in the heating mode by the control device according to the third embodiment of the present invention.

FIG. 20 is a fuzzy rule table used by the control device in the third embodiment in the heating mode.

FIG. 21 is a fuzzy rule table used by the control device in the third embodiment in the heating mode.

22 (a) and 22 (b) are graphs for the conventional case, where (a) shows the behavior of the blown air temperature in the cooling mode, and (b) shows the behavior of the compressor rotation speed in the cooling mode. Show.

23 (a) and 23 (b) are graphs for the conventional case, in which (a) shows the behavior of the blown air temperature in the heating mode, and (b) shows the behavior of the compressor rotation speed in the heating mode. Show.

[Explanation of symbols]

2 ... Duct (air passage), 4 ... Blower means, 22 ... Cooling indoor heat exchanger (evaporator), 23 ... Heating indoor heat exchanger (condenser), 24 ... Refrigeration cycle, 25 ... Compressor, 26
... outdoor heat exchanger (condenser, evaporator), 27 ... cooling decompression device (decompression means), 28 ... heating decompression device (decompression means), 37 ... electric motor (driving means), 39 ... control device, 40 After passing air temperature sensor (cooling degree detecting means), 42 ... High pressure sensor (high pressure detecting means), 48 ...
Temperature setting lever (temperature setting means), 49 ... Refrigerant water heat exchanger, 49c ... Refrigerant passage (condenser), 50 ... Heater core (hot water heat exchanger), 54 ... Hot water circuit, 58 ... Water temperature sensor (hot water temperature detection) means).

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[Procedure amendment]

[Submission date] January 12, 1996

[Procedure amendment 1]

[Document name to be amended] Statement

[Name of item to be corrected] Figure 7

[Correction method] Change

[Correction contents]

[7] The control device is a fuzzy rule view table used in the cooling mode.

[Procedure amendment 2]

[Document name to be amended] Statement

[Correction target item name] Fig. 8

[Correction method] Change

[Correction contents]

8 is a corresponding view table showing the relationship between the air volume setting lever position in the above embodiment the correction target decreasing rotational speed Delta] f.

[Procedure 3]

[Document name to be amended] Statement

[Correction target item name] FIG.

[Correction method] Change

[Correction contents]

11 is a fuzzy rule diagram table the control device used in the heating mode.

[Procedure amendment 4]

[Document name to be amended] Statement

[Correction target item name] FIG.

[Correction method] Change

[Correction contents]

FIG. 20 is a fuzzy rule view table used in the control apparatus heating mode in the third embodiment.

[Procedure Amendment 5]

[Document name to be amended] Statement

[Correction target item name] FIG.

[Correction method] Change

[Correction contents]

21 is a fuzzy rule view table used in the control apparatus heating mode in the third embodiment.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Akira Isaji 1-1-1, Showa-cho, Kariya city, Aichi Nihon Denso Co., Ltd.

Claims (6)

[Claims] 1. A blower means (4) for generating an air flow, an air passage (2) for guiding the air generated by the blower means (4) into a room, and a refrigerant when driven by a drive means (37). A compressor (25) for inhaling, compressing, and discharging
5) a condenser (26) for condensing the refrigerant, a decompression means (27) for decompressing the refrigerant from the condenser (26), and a refrigerant for evaporating the refrigerant from the decompression means (27) and the air passage ( 2) Evaporator (22) provided inside
And a refrigerating cycle (24) provided with a target rotation speed determining means (step) for determining a target rotation speed of the compressor (25) according to a deviation between a predetermined target indoor temperature and the temperature of air blown into the room. 140-190), and a controller (39) including drive control means (step 200) for controlling the drive means (37) so that the actual compressor rotation speed reaches the target rotation speed. An air conditioner configured to perform indoor cooling by blowing air that has passed through a device (22) into the room, wherein the target rotation speed determination means (steps 140 to 190).
The air conditioner is configured to determine the target rotation speed to be higher when the amount of air passing through the evaporator (22) increases. 2. An air conditioning driver comprises temperature setting means (48) for setting the predetermined target indoor temperature, and cooling degree detecting means (40) for detecting an air cooling degree in the evaporator (22). The control device (39) is configured to determine a target air cooling degree in the evaporator (22) according to a setting position of the temperature setting device (48), and the target rotation speed determination device ( Steps 140-190)
According to a deviation between the target air cooling degree and the air cooling degree detected by the cooling degree detecting means (40),
An air conditioner according to claim 1, characterized in that it is arranged to determine a target speed of the compressor (25). 3. A blower means (4) for generating an air flow, an air passage (2) for guiding the air generated by the blower means (4) into a room, and a refrigerant when driven by a drive means (37). A compressor (25) for inhaling, compressing, and discharging
A condenser (23) provided in the air passage (2) for condensing the refrigerant from the condenser (5), and the condenser (2).
3) depressurizing means (28) for depressurizing the refrigerant, and evaporator (2) for evaporating the refrigerant from this depressurizing means (28).
Refrigeration cycle (24) provided with 6), and target rotation speed determination means for determining the target rotation speed of the compressor (25) in accordance with the deviation between the predetermined target indoor temperature and the temperature of the air blown into the room. (Steps 220 to 260, 19
0), and a controller (39) including drive control means (step 200) for controlling the drive means (37) so that the actual compressor rotation speed becomes the target rotation speed. 23) In the air conditioner configured to perform indoor heating by blowing air that has passed through 23) into the room, the target rotation speed determination means (steps 220 to 260, 1)
The air conditioner 90) is configured to determine the target number of revolutions to be higher when the amount of air passing through the condenser (23) increases. 4. An air conditioning driver comprises temperature setting means (48) for setting the predetermined target indoor temperature, and high pressure detecting means (42) for detecting a high pressure of the refrigeration cycle (24). The control device (39) is configured to determine the target high-pressure pressure according to the set position of the temperature setting means (48), and the target rotation speed determination means (steps 220 to 260, 1).
90) is the compressor (2) according to a deviation between the target high pressure and the high pressure detected by the high pressure detecting means (42).
The air conditioner according to claim 3, wherein the air conditioner is configured to determine the target rotation speed of 5). 5. A blower means (4) for generating an air flow, an air passage (2) for guiding the air generated by the blower means (4) into the room, and a refrigerant when driven by a drive means (37). A compressor (25) for inhaling, compressing, and discharging
A condenser (49c) for condensing the refrigerant from 5) and a decompression means (2) for decompressing the refrigerant from this condenser (49c).
8) and a refrigeration cycle (24) including an evaporator (26) for evaporating the refrigerant from the decompression means (28), the refrigerant in the condenser (49c) and the hot water flowing therein. A refrigerant water heat exchanger (49) to be exchanged, and a hot water heat exchanger (50) provided in the air passage (2) while hot water from the refrigerant water heat exchanger (49) flows inside Target water speed circuit (54), a target rotation speed determination means (steps 215 to 215) for determining a target rotation speed of the compressor (25) according to a deviation between a predetermined target indoor temperature and the temperature of air blown into the room. 260, 19
0), and a controller (39) including drive control means (step 200) for controlling the drive means (37) so that the actual compressor rotation speed becomes the target rotation speed. An air conditioner configured to heat a room by blowing air passing through an exchanger (50) into the room, wherein the target rotation speed determining means (steps 215 to 260, 1).
The air conditioner 90) is configured to determine the target number of revolutions to be higher when the amount of air passing through the hot water heat exchanger (50) increases. 6. A temperature setting means (48) for an air conditioning driver to set the predetermined target indoor temperature, and a hot water temperature detecting means for detecting a hot water temperature flowing into the hot water heat exchanger (50). (58), the control device (39) is configured to determine a target hot water temperature according to the setting position of the temperature setting means (48), and the target rotation speed determination means (steps 215 to 215). 260, 1
90) is a compressor (2) according to the deviation of the target hot water temperature and the hot water temperature which the hot water temperature detection means (58) detects.
The air conditioner according to claim 5, wherein the air conditioner is configured to determine the target rotation speed of 5).