JPH089291B2 - Refrigeration cycle control device - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a refrigeration cycle control device used in an air conditioner, and more particularly to a refrigeration cycle control device having a continuously variable cooling capacity. is there.

[Conventional technology]

Conventionally, for example, in a vehicle air conditioner, a refrigerant compression refrigeration cycle has been used. As the control of this refrigeration cycle, it is general to intermittently transmit the power to the refrigerant compressor according to the cooling load. In such intermittent control of the compressor, power loss is large and air-conditioning feeling is bad. Therefore, many variable capacity refrigerant compressors have been proposed. With this, the capacity of the compressor is adjusted according to the cooling load, power loss is greatly reduced, and air conditioning feeling is also improved.

[Problems to be solved by the invention]

However, even if a refrigeration cycle capacity adjusting device typified by such a variable displacement refrigerant compressor is used, conventional proportional, integral, differential, or a combination thereof control is sufficient for power loss and cooling feeling. It could not be said that the effect was obtained.

Therefore, the present invention applies the modern control theory to the control device of the refrigeration cycle and configures this control device as an additional integral type optimum regulator to further reduce the power loss accompanying the operation of the refrigeration cycle and the air conditioning feeling. It was made for the purpose of further improvement of.

[Means for solving problems]

In order to achieve the above-mentioned object, the present invention employs a refrigeration cycle control device having a structure as shown in FIG.

That is, the downstream side is provided in a ventilation passage that communicates with the vehicle compartment, and a blower that sends out the air in the ventilation passage to the vehicle compartment, and the ventilation device that is disposed in the ventilation passage and evaporates the refrigerant circulating in the refrigeration cycle. A cooler for cooling the air blown by the blower, a cooling capacity adjusting device provided in the refrigeration cycle for adjusting the cooling capacity of the cooler, and a physical quantity detecting means for detecting a physical quantity related to the cooling capacity. A target setting means for setting a target value of the physical quantity, an air flow rate detection means for detecting an air flow rate by the blower, and an air flow rate detected by the air flow rate detection means based on the cooling capacity adjusting device. Model setting means for setting a dynamic model of the refrigeration cycle in which the adjustment amount is a control input and the physical quantity is a control output, and a detection object detected by the physical quantity detection means The deviation between the physical quantity and the target physical quantity set by the target setting means, and outputs the cumulative deviation, based on a dynamic model set by the model setting means, and the detected physical quantity, And a control amount calculation unit that calculates the adjustment amount from the cumulative deviation.

[Action]

The refrigeration cycle control device according to the present invention is configured and operates as an additional integral type optimum regulator.

That is, the deviation accumulating means M8 calculates the cumulative deviation between the control output and the target value in order to eliminate the steady deviation as the servo system in which the target value of the control output changes. Then, based on these control outputs and the accumulated deviation, the control amount calculation means M9
Calculates the target adjustment amount that is the control input.

Further, the dynamic model of the refrigeration cycle is set by the model setting means M7 based on the air flow rate detected by the air flow rate detection means M6. And this model setting means M7
Based on the dynamic model set by
And work.

In this additional integral type optimum regulator, the control system is configured based on the dynamic model of the refrigeration cycle.

It is known that in the construction of such an additional integral type optimum regulator, this dynamic model has a great influence on the controllability.

Since this dynamic model is assumed in the range where the behavior of the control input and the control output of the refrigeration cycle can be regarded as linear, outside the range that can be regarded as linear, it is based on this model. Optimal control cannot be performed with the designed optimum integral regulator.

Therefore, in the present invention, as the amount of changing the linearity of the behavior of the refrigeration cycle, focusing on the passing air volume of the heat exchanger, the range in which the behavior of the refrigerating cycle can be regarded as linear is determined according to this passing air volume, In addition to setting multiple dynamic models for each range, an additional integral optimal regulator is designed according to these dynamic models, and the dynamic models are switched according to the detected air volume detected by the air volume detection means. .

As a result, the control characteristics of the additional integral type optimum regulator are switched, and even if the air volume changes, the optimum control is maintained in response to this change.

〔Example〕

 Examples to which the present invention is applied will be described below.

First, the configuration of this embodiment will be described with reference to the drawings.
In this embodiment, the present invention is applied to a controller for a vapor compression refrigeration cycle used in a vehicle air conditioner.

FIG. 2 shows the configuration of the vehicle air conditioning control device. A vehicle air conditioner (hereinafter referred to as an air conditioner) 2 that performs air conditioning of a vehicle interior 1 has the following configuration.

Reference numeral 3 is a ventilation duct of the vehicle air conditioner 2, 4 is an inside air inlet communicating with the vehicle compartment 1, and 5 is an outside air inlet communicating with the outside of the vehicle compartment. Reference numeral 6 denotes an inside / outside air switching damper for selecting either the inside air intake 4 or the outside air intake 5, which is in the inside air mode at the position shown and in the outside air mode at the position shown by the broken line. Reference numeral 7 denotes a blower that sucks the outside air or the inside air into the duct 3 and blows the air toward the vehicle compartment 1, and includes a blower motor 7a and a blower fan 7b.

8 is a refrigeration cycle, 8a is an evaporator, 8b is a variable capacity compressor, 8c is a condenser, 8d is a receiver,
8e is an expansion valve and 8f is a magnetic clutch. The opening of the expansion valve 8e is detected by a temperature-sensing cylinder (not shown) for the outlet temperature of the evaporator 8a,
It is controlled by the gas pressure inside the temperature sensitive cylinder. The refrigerant circulates in the refrigeration cycle 8 to exchange heat. The high-temperature and high-pressure refrigerant gas compressed by the variable capacity compressor 8b is cooled and liquefied by the condenser 8c, gas-liquid separated by the receiver 8d, atomized by the expansion valve 8e, vaporized by the evaporator 8a, and heat of the evaporator 8a. Take away. Evaporator 8a
The gaseous refrigerant vaporized in is again the variable capacity compressor 8b.
The refrigeration cycle is repeated in which the heat is taken from the air on the surface of the evaporator 8a and the heat is removed to the air on the surface of the condenser 8c.

A heating device 9 is composed of a heater core 9a, a hot water source 9b, and a water valve 9c. The hot water supplied from the hot water source 9b heats the air passing through the heater core 9a. The hot water source 9b is an engine that serves as a power source for the vehicle, and uses its cooling water as hot water. Reference numeral 10 denotes an air mix damper, which controls the temperature of the air blown into the passenger compartment downstream of the heater core 9a by adjusting the amount of air passing through the heater core 9a among the air cooled by the evaporator 8a. .

Reference numeral 11 denotes a control device composed of a microcomputer, which includes a CPU, ROM, RAM, I / O ports, which are generally more conventional than before, and a bus for electrically connecting these. The control device 11 receives signals from various sensors and input devices described below and outputs drive signals to various actuators.

12 is an outside air temperature sensor provided outside the vehicle compartment, 13 is an after-evaporation sensor that detects the air temperature behind the evaporator, 14 is an inside air temperature sensor provided in the vehicle compartment, 15 is a solar radiation sensor provided in the vehicle compartment, and 16 is a hot water source. Is a water temperature sensor. 17 is a temperature setter for setting a target temperature in the vehicle interior, 18
Are various switches for designating modes such as operation and stop of the air conditioner 2, air volume, and inside / outside air.

Reference numeral 19 is an inside / outside air switching servomotor for driving the inside / outside air switching damper 6, and 20 is a speed control circuit for adjusting the rotation speed of the blower motor 7a of the blower 7. Reference numeral 21 is a variable displacement actuator for operating the variable displacement mechanism of the variable displacement compressor 8b, 22 is an air mix servomotor for driving the air mix damper 10, and 23 is a water valve servomotor for operating the water valve 9.

Next, the configurations of the refrigeration cycle 8 and the control device 11 for controlling the same, which are the gist of the present invention, will be described in more detail.

FIG. 3 is a configuration diagram showing the configuration of the refrigeration cycle 8 and the configuration of the control system of the control device 11. In the refrigeration cycle 8 of FIG. 3, a temperature sensitive cylinder 8g for adjusting the opening of the expansion valve 8e is shown.

In this embodiment, the control system is configured as an additional integral type optimum regulator that controls the air temperature T _E immediately after the evaporator 8a of the refrigeration cycle 8.

As shown in FIG. 3, the additional integral type optimum regulator operates by being given a target temperature T _E ^* (P1), but since the nonlinear behavior of the refrigeration cycle 8 is linearly approximated, the operating range of the refrigeration cycle is It is configured to be divided into several ranges that can be considered to be valid for linear approximation, and to handle each control amount as a perturbation component δT _E , δV from the steady point T _E a, V a within this segment (P4, P7).

In addition, the addition integral type optimal regulator Is estimated based on the perturbation components δT _E and δV, and (P
5), Cumulative ZT of deviation ST _E between target temperature T _E ^* and actual temperature T _E
E is obtained (P2, P3), and the state variable quantity is calculated by the cumulative value ZT _E. To a predetermined optimum feedback gain The feedback control amount of the compressor capacity V (here, the perturbation component δV from the steady point) is determined by multiplying by (P6). Therefore, in the refrigeration cycle 8, this perturbation component δV
The control amount V obtained by adding the steady point value Va to is output (P7).

Further, the feedback gain, the observer parameter, and each steady point are switched based on the operating state of the refrigeration cycle 8, in this embodiment, the amount of air passing through the evaporator 8a (P8).

Next, a setting procedure of the above-mentioned addition integral type optimum regulator will be described.

(A) Modeling of control system The behavior of the control system, here, the system that controls the air temperature immediately after the evaporator 8a of the refrigeration cycle 8 is calculated by using the state equation and the output equation. As. In the equations (1) and (2), Is the state variable amount of the refrigeration cycle 8, Is the control input quantities of the refrigeration cycle 8 (compressor capacity V of the refrigeration cycle 8 in this embodiment), Is the post-evaporation temperature T _E as the control output of the refrigeration cycle 8,
The subscript k represents the number of times of sampling. FIG. 4 shows a refrigeration cycle 8 operating as a 1-input 1-output system.
It is a block diagram which expressed the system of with the transfer function G (z). In addition, z represents z conversion of the sample value of the input / output signal, and G (z) is assumed to have an appropriate order.

When it is extremely difficult to determine a physical model like the refrigeration cycle 8 of the present embodiment, the transfer function G is determined by a kind of simulation called system identification.
Although (z) can be obtained, it is identified by the least square method here.

The refrigeration cycle 8 is steadily operated in a predetermined operating state, an appropriate test signal is added as a change amount δV of the compressor capacity, the input δV at that time, and a change amount δT _{E of the} post-evaporator temperature which is the output.
And data are sampled N times. Input data series {u (i)} = {δVi}, output data series {y (i)} = {δT _E i} (where i = 1,2,3, ...
N). At this time, the system can be regarded as one input and one output, and the transfer function G (z) of the system is G (z) = B (z ^-1 ) / A (z ^-1 ) ... (3 ) That is, G (z) = (b ₀ + b ₁ · z ⁻¹ +… + b _n · z ^-n ) / (1 + a ₁ · z ⁻¹ + a ₂ · z ⁻² +… + a _n ·
z ^-n ) ……… It is calculated in (4). Here, z ⁻¹ is a unit transition operator, which means z ⁻¹ · X (k) = X (k−1).

The transfer function G (z) of the system is determined by defining the parameters a _{1 to} a _n and b _{0 to} b _n of the equation (4) from the input / output data series {u (i)}, {y (i)}. To be In system identification by the method of least squares, the parameters a _{1 to} a _n , b _{0 to} b _n are Is set to be the minimum. In this embodiment, n = 2,
Each parameter was calculated. In this case, the signal flow diagram of the system is as shown in Fig. 5, and the state variable quantity [X
₁ (k) X ₂ (k)] ^T , the state / output equation is Can be expressed as Therefore, the system parameters when viewed as a system with one input and one output Are each Becomes

In this way, the dynamic model of the present embodiment was obtained by system identification. When the refrigeration cycle 8 is operating in a predetermined state, this dynamic model has a linear approximation in the vicinity of this state. It is defined in the form. Therefore, the transfer function G (z) is obtained by the above method for a plurality of steady operating states, and the vector in the state equation (1) and the output equation (2) is obtained. Is obtained, and the input / output relationship is established during the perturbation δ.

(B) Design of observer An observer (P5) for estimating the state variable amount is designed by using the above-mentioned degrees of increase δT _E and δV.

As the observer, there are a same-dimensional observer, a minimum-dimensional observer, etc., and various design methods are known. In this embodiment, it is designed as the same-dimensional observer.

The same-dimensional observer has the configuration shown in FIG. 6, and as shown in the figure, the estimated value of the state variable. As the feedback gain, Becomes here To be stable Choose If the absolute values of the eigenvalues of the matrix are all less than 1, It has been proved that Therefore, That way, and Then the observer Becomes

The parameter Is obtained for each model obtained for a steady operating state.

Above, the vector of the state equation (1) etc. obtained by system identification More designed the observer P5.

(C) System expansion Since the control target of this embodiment is a servo system in which the target temperature T _E ^* changes, the system is expanded using cumulative values. That is, the state variable amount estimated by the observer P5 And cumulative value Including this and And That is, Becomes

(D) Optimal feedback gain Calculate the expanded state variable quantity Optimal feedback gain for The method for obtaining is detailed in, for example, Shokodo of Katsuhisa Furuta, "Linear System Control Theory" (1976), and the detailed explanation is omitted here.

The system of the system expanded in (c) above is expressed as follows.

Where the state variable quantity Is a quadratic, Is. As described above, δT _E and δV represent the deviation (perturbation) from the steady point.

At this time, the optimum control input that minimizes the following evaluation function J,
That is, operating conditions Is to solve the control problem as the additional integral type optimum regulator for the refrigeration cycle 8.

Incidentally, here Is the weight parameter matrix, and k is the number of samplings when the control start time is 0. The right side of equation (15) is Is a so-called quadratic form expression in which is a diagonal matrix.

As a result, optimum control input Becomes

And Is a positive definite solution of the following matrix Riccati equation.

Here, the evaluation function J in the equation (15) means the various quantities of operating conditions as control inputs to the refrigeration cycle 8. Of the operating state as a control output while limiting the movement of the Here, various quantities including the perturbation component ΔT _E of post-evaporation temperature It is intended to minimize the deviation from. Various operating conditions The weighting of the constraints for is the weight parameter matrix It can be changed by the value of. Therefore, the dynamic model of the refrigeration cycle 8 that has already been obtained, that is, the matrix Using an arbitrary weight parameter matrix And solve equation (18) And obtain the optimum feedback gain using equation (17). Can be requested. Therefore, this optimal feedback gain Control input variables of the refrigeration cycle 8 (Here, δV) Can be obtained as

In this example Got

This feedback gain Is determined for each model.

Above, the configuration of the optimum integral regulator (Fig. 3)
The modeling of the control system, the design of the observer, the expansion of the system, and the setting of the optimum feedback gain have been explained based on the above.
Inside 11, the actual control is performed using only the result.

Next, the operation of the control device 11 for realizing the control system as described above will be described.

FIG. 7 is a flowchart for realizing the above control system. In the following description, the amount handled in the current process is added with the subscript (k), and the amount handled the previous time is added with the subscript (k).
-1) Append.

The control device 11 of this embodiment starts execution of a predetermined program when the car air conditioner 2 is activated.

Then, together with the control program for the refrigeration cycle 8 shown in FIG. 7, a control program for controlling the passenger compartment 1 to the target temperature set by the temperature setter 17, such as the air mix damper 10 and the water valve 9c, , Executes a control program such as the inside / outside air switching damper 6.

The flow chart of FIG. 7 shows the part related to the refrigeration cycle control of these control programs.

First, in step 110, each variable used in the subsequent arithmetic processing is initialized and initial values are set.

In step 120, the detection value of each sensor including the air temperature T _E (k) detected by the post-evaporation sensor 13 and the temperature setter 17,
Signals from various switches 18 are input.

In step 130, the target post-evaporator temperature T _E ^* (k) immediately after the evaporator is calculated. This target temperature T _E ^* (k)
Is the passenger compartment target temperature, inside air temperature, outside air temperature, cooling water temperature,
It is calculated depending on whether or not the dehumidifying action is necessary. This step
The arithmetic processing of 130 corresponds to the target post-evaporator temperature setting unit P ₁ in FIG.

In step 140, the calculated target post-evaporator temperature T _E ^{* (k)} in step 130, after the evaporator input from the post-evaporation sensor 13 temperature T _E (k) deviation between the ST _E (k) is the following formula Is calculated.

ST _E (k) = T _E ^* (k) −T _E (k) (20) The arithmetic processing of step 140 corresponds to the addition unit P ₂ in FIG.

In step 150, the deviation ST obtained in step 140
_The process of accumulating _E (k) is performed, and the cumulative deviation ZT _E (k) is calculated by the following equation.

ZT _E (k) = ZT _E (k−1) + T · ST _E (k) (21) Note that T in the equation (21) is a sampling period. The calculation process of step 150 corresponds to the accumulating unit P _{3 of} FIG.

In step 160, when the dynamic model of the refrigeration cycle 8 is constructed based on the various signals input in step 120, the closest state is selected from the steady operating states adopted as the range in which the linear approximation holds, and the Steady point T _E a that is the post-evaporation temperature of the state and Va that is the compressor capacity
And the feedback gain And the parameters Select and. This processing is performed by the air flow rate detection unit P _{8 in} FIG. 3 and T _E a, Va, according to the detected air flow rate. It corresponds to each of the configurations P ₄ , P ₅ , P ₆ , P ₇ for switching.

In this embodiment, the air volume is adopted as the operating state, and the processing of step 160 is performed according to the command signal given to the speed control circuit 20 of the blower motor 7a.

In step 170, the process of extracting the perturbation component δT _E (k) from the steady point T _E a of the post-evaporation temperature T _E (k) input from the post-evaporation sensor 13 is performed by the following formula.

δT _E (k) = T _E (k) -T _E a (22) The calculation process of step 170 corresponds to the perturbation component extraction unit P ₄ in FIG.

In step 180, predetermined and selected in step 160 And the perturbation δT _E (k) obtained in step 170 and the state variable amount estimated last time. And the perturbation component δV (k-1) of the compressor capacity obtained last time
From the above, the state variable quantity is calculated by the following equation based on the above equation (11). Is estimated. _{1 (k) = a 0 11} · 1 (k-1) + a 0 12 · 1 (k-
_{1) + b 0 1 · δV} (k-1) + l1δT E (k-1) 2 (k) = a 0 21 · 2 (k-1) + a 0 22 · 2 (k-
1) + b ₀ 2 · δV (k-1) + l2δT _E (k-1) ………… (2
3) The calculation process of step 180 corresponds to the state variable amount estimation unit P ₅ in FIG.

In step 190, the state variable amount obtained in step 180 And the cumulative deviation ZT _E (k) obtained in step 150, the perturbation component δV (k) of the compressor capacity, which is the manipulated variable, is calculated by the following equation based on the above equation (19). That is, the feedback gain Since there is a, δV (k) = - a _{f 1 · 1 (k) -f} 2 · 2 (k) + f 3 · ZT E (k) ......... (24).

The calculation process of step 190 corresponds to the feedback control amount determining unit P ₆ in FIG.

In step 200, the compressor capacity V (k) is calculated from the perturbation component δV (k) of the compressor capacity obtained in step 190 and the steady point value Va selected in step 160 by the following equation. .

V (k) = Va + δV (k) (25) The arithmetic processing of step 200 corresponds to the reference value adding section P ₇ in FIG.

In step 210, a variable displacement actuator is used so as to realize the compressor capacity V (k) obtained in step 200.
21 is controlled.

Then, in step 220, the value of k, which is the number of times of sampling, is incremented, and the process returns to step 120 again.

The control results of the refrigeration cycle by the control system having the configuration described above and the operation of the control device 11 that realizes this control system are shown in FIGS. 8, 9, and 10.

Fig. 8 shows the target post-evaporator temperature T _E from the steady operating state.
^* (Dashed-dotted line) shows the actual change in the post-evaporation temperature when the step function is changed. The solid line shows the example according to the present invention and the broken line shows the conventional control. In the conventional case, the target T _E ^* is controlled while overshooting and undershooting, whereas in this embodiment according to the present invention, the target T _E ^* is controlled quickly without almost overshooting or undershooting.

FIG. 9 shows a change in post-evaporator temperature due to a change in the air volume passing through the evaporator due to a change in the air volume mode.
Even if the air volume mode is switched from " _Lo " to " _Hi " and the steady operating state of the refrigeration cycle is switched, the target T _E ^{* is} promptly provided with almost no overshoot or undershoot even in the case of this embodiment ^. Controlled by.

That is, the steady-state value T _E a, Va, the feedback gain Observer parameters It is because it is switching. FIG. 10 shows changes in post-evaporation temperature with changes in the rotation speed of the engine that drives the compressor 8b. In this case as well, in the case of this embodiment, the target T _E is quickly controlled with almost no overshoot or undershoot.

As described above, in this embodiment, the post-evaporation temperature can be stably controlled to a target even with respect to various disturbances, and the temperature of air blown to the vehicle interior 1 as the vehicle air conditioner 2 is also stabilized. It is possible to provide a comfortable air conditioning environment.

Further, since there is almost no overshoot or undershoot, the post-evaporation temperature is controlled efficiently. For this reason, it is possible to provide the vehicle air conditioner 2 that has both power consumption and fuel efficiency.

Although the embodiments to which the present invention is applied have been described above, other embodiments such as those listed below may be used.

Although the variable capacity compressor is shown as the cooling capacity controller, an expansion valve whose opening degree changes continuously may be used, or these may be combined.

Although the post-evaporator temperature is shown as the physical quantity relating to the cooling capacity of the heat exchanger detected by the detection means, it may be the surface temperature of the evaporator, the refrigerant temperature in the evaporator, the refrigerant pressure in the evaporator, or the like.

The model of the refrigeration cycle is not limited to the one based on the method of system identification, and the thermal characteristics of the configuration of each part of the refrigeration cycle may be analyzed, and a mathematical model obtained from this result may be adopted.

The method of fixing the system is not limited to the least square method, and various theories may be applied. Further, in the above-described embodiment, the system is identified as a second-order system, but the controllability is further improved by further increasing the order and the observer order and the feedback gain order. In this embodiment, the second order is used in consideration of the calculation capability of the control device 11 and the simulation time for constructing the control system.

Further, the target post-evaporator temperature is not limited to being calculated according to various conditions, and may be constant at a predetermined temperature.

The present invention is not limited to those enumerated in this way, and other various embodiments are possible without departing from the scope of the present invention.

〔The invention's effect〕

According to the present invention described above, it is possible to suppress fluctuations (overshoot, undershoot) in the control output during a transition in which the operating state of the refrigeration cycle changes, and it is possible to satisfactorily control the target value.

Further, the fluctuation of the control input during the transition can be suppressed to the necessary minimum.

From these, the cooling capacity, which is the control output of the refrigeration cycle, can be satisfactorily controlled, and since overcontrol is reduced, the power loss for operating the refrigeration cycle can also be reduced.

[Brief description of drawings]

FIG. 1 is a block configuration diagram showing the configuration of the present invention, and FIG. 2 is a configuration diagram of a vehicle air conditioner of an embodiment to which the present invention is applied.
FIG. 3 is a block diagram showing a refrigeration cycle control system according to an embodiment, FIG. 4 is a block diagram showing a refrigeration cycle system with one input and one output, and FIG. 5 is a dynamic model of the refrigeration cycle. Signal flow diagram of FIG. 6, FIG. 6 is a block diagram showing the configuration of the same-dimension observer, FIG. 7 is a flowchart showing the operation of the control device, and FIGS. 8, 9, and 10 are controls of one embodiment. It is a graph explaining the effect by. M1 …… Blower, M2 …… Cooler, M3 …… Cooling capacity controller, M
4 ... Physical quantity detecting means, M5 ... Target setting means, M6 ... Air flow amount detecting means, M7 ... Model setting means, M8 ... Deviation accumulating means, M9 ... Control amount calculating means.

Claims (1)

[Claims] 1. A blower which is provided in a ventilation passage communicating with a passenger compartment on the downstream side, and blows air in the ventilation passage to the passenger compartment; and a refrigerant which is disposed in the ventilation passage and which circulates in a refrigeration cycle. By doing so, a cooler for cooling the air blown by the blower, a cooling capacity adjusting device provided in the refrigeration cycle for adjusting the cooling capacity of the cooler, and a physical quantity related to the cooling capacity are detected. Physical quantity detection means, target setting means for setting the target value of the physical quantity, air flow rate detection means for detecting the air flow rate by the blower, and the cooling capacity based on the air flow rate detected by the air flow rate detection means. Model setting means for setting a dynamic model of the refrigeration cycle in which the adjustment amount of the adjustment device is a control input and the physical quantity is a control output, and detection detected by the physical quantity detection means Based on the dynamic model set by the deviation accumulation means that accumulates the deviation between the physical quantity and the target physical quantity set by the target setting means, and outputs the cumulative deviation, the detected physical quantity and the A refrigeration cycle control device comprising: a control amount calculation means for calculating the adjustment amount from the accumulated deviation.