JPH03260542A - Operation controller for air conditioner - Google Patents

Abstract

PURPOSE:To improve comfortableness of air conditioning by controlling the opening of a pressure reducing valve to converge suction air temperature and moisture to set temperature and set moisture, respectively. CONSTITUTION:The opening of an indoor motor-driven expansion valve 51 is so controlled by opening control means 101A that a suction air temperature Ta to be detected by a suction sensor Thl and suction air humidify RH to be detected by a moisture sensor Hu are respectively converged to a set temperature Ts, a set moisture RHs. That is, in the case of only opening control based on the temperature Ta, if the moisture RH is different, a difference is generated at a diffused air temperature Td to the same temperature Ta. Particularly, since evaporating capacity to be consumed for dehumidifying is larger as compared with a temperature fall, if the moisture is ignored, it is apprehended that the comfortableness of air conditioning might be lost. Since it is controlled by considering the moisture RH, such a difference of the diffusing air temperature is reduced, thereby improving the comfortableness of air conditioning.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to an operation control device for a refrigeration system, and particularly to one that controls the capacity of an evaporator in consideration of humidity.

(Prior Art) Conventionally, as disclosed in, for example, Japanese Unexamined Patent Publication No. 62-218012, a compressor, a heat source side heat exchanger, a pressure reducing valve whose opening degree can be adjusted, and a user side heat exchanger are connected in sequence. For a refrigerant circuit consisting of a refrigerant circuit, a reheater that functions only as a condenser is connected in parallel to the heat exchanger on the heat source side together with a flow control valve, and the reheater is used in the ventilation path of the heat exchanger fan on the user side. It is placed downstream of the side heat exchanger, and during cooling operation, the user side heat exchanger functions as an evaporator to cool the room, while the user side heat exchanger and reheater are used to cool the room. , is a well-known technique that performs dehumidifying operation.

(Problems to be Solved by the Invention) By the way, in the above-mentioned conventional device, during cooling operation, the opening degree of the pressure reducing valve is adjusted according to the temperature deviation between the intake air temperature and the set temperature. That is, the temperature deviation of the intake air temperature with respect to the set temperature is taken as the required capacity, and the opening degree of the pressure reducing valve is controlled by PI control etc. so that this deviation becomes "0".

However, for example, as shown in FIG. 16, two state points (p
Suppose that the blown air at each state point (q+) and (q2) is supplied indoors by passing through the evaporator from 1) and (p2). In that case, the SHF line for the state point with high humidity (p1) is as shown by ■ in the figure, and the state point with low humidity (p1) is
The SHF line for 2) is as shown in the figure, so if the heat exchange amount in the evaporator is the same, the blowing air temperature will be different as shown in S al and S a2 in the figure. That is, there is a problem in that it is not possible to supply an appropriate blowout air temperature commensurate with the state of the intake air.

In view of the above, a first object of the present invention is to improve the air conditioning effect by controlling the capacity of the evaporator in consideration of humidity.

On the other hand, in the case of dehumidification operation using a reheater in the conventional type described above, the capacity of the evaporator is usually controlled by the intake air temperature, and the capacity of the reheater is also controlled according to the humidity. .

However, in that case, the room temperature is first cooled and dehumidified by the evaporator, and then heated by the reheater, so the amount of reheat from the reheater does not directly contribute to dehumidification, and the rise in room temperature causes cooling. The desired dehumidification is achieved only when the amount increases. Therefore, if the capacity during dehumidification operation is controlled only by humidity, the temperature of the blown air cannot be controlled in accordance with the indoor demand, and there is a risk that the comfort of the air conditioning will be impaired.

In view of the above, a second object of the present invention is to improve the comfort of air conditioning by controlling the capacity of the reheater in consideration of the intake air temperature.

(Means for solving the problem) In order to achieve the above object, the first means for solving the problem is as shown in FIG. 1A. A refrigeration system is assumed to be provided with a refrigerant circuit (10) formed by sequentially connecting an evaporator (51) and an evaporator (5).

The operation control device for the refrigeration equipment includes a suction air temperature detection means (Th1) that detects the temperature of the suction air, a humidity detection means (HU) that detects the humidity of the suction air, and the suction air temperature detection means (Th1) that detects the humidity of the suction air. ) and humidity detection means (Hu
), the pressure reducing valve (5) is operated so that the suction air temperature and suction air humidity become the set temperature and set humidity, respectively.
1) is provided with an opening degree control means (101A) for controlling the opening degree.

As shown in FIG. 1B, the second solution is based on a refrigeration system similar to the first solution, and includes a suction air temperature detection means ( T h1), a humidity detection means (Hu) for detecting the humidity of the intake air, and the above-mentioned intake air temperature detection means (
temperature-dependent capacity calculation means (102) for calculating the required capacity based on the temperature difference between the suction air temperature detected by T h1) and the set temperature; and the suction air humidity and setting detected by the humidity detection means (Hu). Humidity dependent capacity calculation means (103) which calculates the required capacity based on the humidity difference from the humidity, and recalculation means (102) which calculates the capacity of the evaporator (5).

The opening control means (101B) is provided to control the opening of the pressure reducing valve (51) so that the required capacity is the larger of the two required capacities calculated in step (103).

As shown in FIG. 1B, the third solution is based on the same refrigeration system as the second solution, and includes similar suction air temperature detection means (T h1) and humidity detection means (Hu).
, temperature dependent ability calculation means (102), and humidity dependent ability calculation means (103).

Then, the opening degree of the pressure reducing valve (51) is controlled so that the capacity of the evaporator (5) becomes the above-mentioned priority required capacity until the predetermined priority required capacity among both required capacities becomes equal to or less than a predetermined value. Opening degree control means (101C) is provided to control the opening degree of the pressure reducing valve (51) so that the capacity of the evaporator (5) becomes the other required capacity when the required capacity becomes less than a predetermined value.

As shown in FIG. 1B, the fourth solution is based on the same refrigeration system as the second solution, and includes similar suction air temperature detection means (Th1) and humidity detection means (Hu). Temperature-dependent ability calculation means (102) and humidity-dependent ability calculation means (103) are provided.

Further, an opening control means (101D) is provided for controlling the opening of the pressure reducing valve (51) so that the capacity of the evaporator (5) becomes the sum of both required capacities.

A fifth solution is that in the fourth solution, the opening control means (101D) is forced to turn off the thermostat when a predetermined priority required capacity of both required capacities becomes less than a set value. It is intended to be controlled.

As shown in FIG. 1C, the sixth solution is based on the same refrigeration system as the first solution, and furthermore, the evaporator fan (57) has a ventilation path downstream of the evaporator (5). A reheater (6) shall be installed to heat the blast air.

A suction air temperature detection means (T h1) for detecting the suction air temperature, a humidity detection means (Hu) for detecting the humidity of the suction air, and a humidity detection means (Hu) for detecting the humidity of the suction air during dehumidification operation.
) an opening control means (101E) for controlling the opening of the pressure reducing valve (51) so that the suction air humidity detected by the
), and during dehumidification operation, the above-mentioned suction air temperature detection means (T h
capacity control means (104) for controlling the capacity of the reheater (6) so that the intake air temperature detected in step 1) reaches the set temperature;
A).

As shown in FIG. 1D (not including the broken line portion), a seventh solution means, in addition to the fourth or fifth solution means, provides a cooling system for the evaporator (5) in the ventilation path of the evaporator fan (57). A reheater (6) is provided on the downstream side to heat the blast air.

Further, a capacity control means (104B) is provided to control the capacity of the reheater (6) according to the required capacity based on the temperature calculated by the temperature dependent capacity calculation means (102).

As shown in FIG. 1D (not including the broken line part), the eighth solution means includes a reheater (6) similar to the seventh solution means, in addition to the fourth or fifth solution means. will be established.

Further, the capacity of the reheater (6) is controlled according to the required capacity difference between the required capacity calculated by the humidity dependent capacity calculation means (103) and the required capacity calculated by the temperature dependent capacity calculation means (102). This configuration is provided with a capacity control means (104C) for controlling.

A ninth solution, as shown in FIG. 1D (including the broken line portion), includes a reheater (6) similar to the seventh solution in addition to the fourth or fifth solution. Install.

Furthermore, target outlet temperature setting means (T h1) receives the output of the suction air temperature detection means (T h1) and sets a target temperature of the outlet air temperature based on the temperature difference between the suction air temperature and its set temperature.
105) and outlet temperature detection means (
T h2) and the output of the outlet temperature detection means (T h2), the outlet air temperature is determined by the target outlet temperature setting means (105).
) A capacity control means (104D) is provided for controlling the capacity of the reheater (6) so that the temperature reaches the target blowing air temperature set in (104D).

(Function) With the above configuration, in the invention of claim (1), the opening control means (101A) controls the suction air temperature detection means (T
suction air temperature and humidity detection means (H
The suction air humidity detected at u ) is the set temperature,
The opening degree of the pressure reducing valve (51) is controlled so that the humidity converges to the set humidity.

Therefore, control is performed that also takes humidity into consideration, and problems such as supplying conditioned air with a different blowout air temperature relative to the same intake air temperature are suppressed, and the comfort of air conditioning is improved.

In the invention of claim (2), the opening degree control means (101B) calculates the required capacity based on the temperature calculated by the temperature dependent capacity calculation means (102) and the humidity dependent capacity calculation means (103).
) The pressure reducing valve (5) is adjusted so that the capacity of the evaporator (5) converges to the larger capacity of the required capacity based on the humidity calculated in
]) is controlled.

Therefore, especially when the humidity is high, most of the capacity of the evaporator (5) is used for dehumidification, and the lack of cooling amount that would prevent the temperature of the blown air from lowering sufficiently will be eliminated.

In the invention of claim (3), the opening control means (101C) controls the capacity of the evaporator (5) according to the required capacity until the preset priority required capacity becomes equal to or less than a predetermined value. When the priority required capacity decreases, the capacity of the evaporator (5) is adjusted by controlling the opening of the pressure reducing valve (51) according to other required capacities, so that the state quantity of the conditioned air sequentially converges to the target point. This improves the comfort of air conditioning.

In the invention of claim (4), the opening control means (101D) controls the pressure reducing valve (51) so that the evaporation capacity of the evaporator (5) becomes the sum of the required capacity based on temperature and the required capacity based on humidity.
), the cooling capacity is controlled according to the capacity truly required indoors, and even when humidity and temperature are high, for example, the room can be rapidly cooled with a large amount of cooling. , the comfort of air conditioning improves more significantly.

In the invention of claim (5), in the invention of claim (4), when the state quantity on the priority side (for example, the intake air temperature) reaches the set value, the thermostat is forcibly turned off, so that the indoor temperature is immediately turned off. While approaching the target state, the thermostat is immediately turned off when the state quantity on the priority side approaches the set value, so overshoot due to excessive cooling amount is suppressed as much as possible.

In the invention of claim (6), during dehumidification operation, the opening control means (
101E), the opening degree of the pressure reducing valve (51) is controlled based on the humidity deviation between the suction air humidity and the set humidity, and first, the humidity approaches the set humidity. After that, the ability control means (10
4A), the capacity of the reheater (6) is adjusted based on the temperature deviation between the intake air temperature and the set temperature, and finally the outlet air temperature approaches the set temperature.

Therefore, during dehumidification operation that is normally performed when the temperature is close to the set value, the cooling capacity and dehumidification capacity of the evaporator (5) are controlled based on the humidity, while the capacity of the reheater (6) is controlled depending on the temperature deviation. Since the humidity and temperature are controlled based on the temperature, both humidity and temperature quickly converge to the target values.

In the invention of claim (7), the above claim (4) or (5)
In addition to the above invention, the capacity control means (104B) controls the capacity of the reheater (6) according to the required capacity based on the intake air temperature.

Therefore, even if the amount of cooling in the evaporator (5) becomes excessive, the temperature of the blown air is guaranteed to be lowered by heating in the reheater (6). Since the capacity of the reheater (6) is controlled in this way, continuous control is possible without discontinuously switching between normal cooling operation, dehumidification operation, and heating operation.

In the invention of claim (8), the capacity control means (104C) controls the capacity of the reheater (6) according to the capacity difference between the required capacity based on humidity and the required capacity based on temperature. During the process, even if the amount of cooling increases under the current control compared to the previous control, the amount of heating in the reheater (6) will be increased by that increase, and the suction air temperature will remain the same. If there is, the temperature of the blown air becomes approximately equal to the previous blown air temperature. That is, more stable control becomes possible, and the comfort of air conditioning is significantly improved.

In the invention of claim (9), the target blowing temperature setting means (105
), the target blowout temperature is calculated based on the value of the suction air temperature, and the capacity of the reheater (6) is controlled so that the blowout air temperature becomes the target blowout temperature.

In other words, the temperature of the blown air is controlled to directly converge to the target value without passing through the room, so compared to controlling the intake air temperature, there is no feedback delay after the air passes through the room. Quick and stable control is possible.

(Example) Hereinafter, an example of the present invention will be described based on the drawings from FIG. 2 onwards.

Fig. 2 shows a refrigerant piping system of an air conditioner according to an embodiment of the present invention, in which two indoor units (A) and (B) are connected to two outdoor units (X). This is a multi-type air conditioner.

In the outdoor unit (X), one end of a high pressure side gas line (31) is connected to the discharge side of the compressor (1), while a low pressure side gas line (32) is connected to the suction side. On the other hand, the liquid line (
33) is connected to the high pressure side gas line (31), low pressure side gas line (32) and liquid line (3).
3) from the outdoor unit (X) to each indoor unit (A).

A refrigerant circuit (10
) is configured.

Here, the tip of the gas pipe (22) of the outdoor heat exchanger (2) is connected to the - port of the four-way switching valve (21),
The four-way switching valve (21) allows the warm-up pipes (24a), (2
4b) through the gas pipe (22) of the outdoor heat exchanger (2)
are alternately communicated with the high-pressure side gas line (31) or the low-pressure side gas line (32).

In addition, (41) is an accumulator interposed between the connection part of the low-pressure side gas line (32) with the branch pipe (24b) and the compressor (1), and (26) is the four-way switching valve ( 21
) - port to the gas pipe (22) of the outdoor heat exchanger (2)
This is a capillary tube installed in a relief path (27) for letting the refrigerant escape. In addition, the above liquid line (33
), an outdoor electric expansion valve (25) and a receiver (43) are interposed in order from the outdoor heat exchanger (2) side.

And each of the above lines (31) and (32).

(33) has a flow divider (31a) at each end.

(32a) and (33a) are provided, and the gas pipe (5) of the indoor heat exchanger (5) of each indoor unit (A) is provided.
a) is a flow divider for the high pressure side gas line (31) and the low pressure side gas line (32) by the branch pipe (31b), C32b) via the first on-off valve (52) and the second on-off valve (53). (31a) and (32a) for communication. Furthermore, the liquid pipe (33) of each indoor heat exchanger (5)
b) is equipped with an indoor electric expansion valve (51), and each liquid pipe (33b) is connected to a flow divider (33a) of the liquid line (33).
It is connected to the.

Here, in one indoor unit (A), a reheater (6) is disposed downstream of the indoor heat exchanger (5) in the ventilation path of the indoor fan (57), and the reheater ( 6) is interposed in a bypass path (62) that connects the liquid pipe (33b) and the flow divider (31a) of the high-pressure side gas line (31). In the bypass passage (62), a reheat electric expansion valve (6]) is provided on the flow side of the reheater (6) to adjust the flow rate of refrigerant in the bypass passage (62). That is, the gas pipe side of the reheater (6) communicates only with the high-pressure side gas line (31), so that it always functions as a condenser.

In addition, sensors are arranged in each of the indoor units (A) and (B), and (T h1) is a suction sensor that is arranged at the air suction port and serves as a suction air temperature detection means for detecting the suction air temperature Ta. , (T h2) is a blow-off sensor arranged at the air outlet and detects the blow-out air temperature SA;
) is placed at the air suction port and serves as a humidity detection means for detecting the intake air humidity R1 (); (Pc) is placed in the high-pressure gas line (31) and is a high-pressure pressure sensor that detects the high-pressure side pressure; Pe) is the low pressure side gas line (
32) is a low-pressure pressure sensor that detects the pressure on the low-pressure side. Further, (Th3) is a liquid pipe sensor that is arranged on the liquid pipe side of the reheater (6) of the indoor unit (A) and detects the temperature of the liquid pipe.

Each of the above sensors is connected to the air conditioner controller (
(not shown) by a signal line, and the controller controls the operation of the air conditioner according to the detected values of each sensor.

Next, to explain the operation of the air conditioner having the above configuration, when each indoor unit (A) is in cooling operation, the first on-off valve (52) closes, the second on-off valve (53) opens, and By communicating the gas pipe (5a) side of the heat exchanger (5) with the low pressure side gas line (32), the indoor heat exchanger (5) functions as an evaporator, and cool air from each indoor fan (57) is While supplying indoor air, during heating operation, the first on-off valve (
52) opens and the second on-off valve (53) closes, causing either the gas pipe (5a) side of the indoor heat exchanger (5) or the high pressure side gas line (31
), the indoor heat exchanger (5) functions as a condenser and supplies warm air indoors by the indoor fan (57). When both indoor units (A) and (B) are in cooling operation, the outdoor unit (
At X), the four-way switching valve (21) switches as shown by the solid line in the figure and communicates with the gas pipe (22) of the outdoor heat exchanger (2) or the high-pressure side gas line (31), thereby allowing outdoor heat exchange. While the container (2) functions as a condenser, when the indoor units (A) and (B) are both in heating operation, the four-way selector valve (21) switches as shown by the broken line in the figure, By communicating the gas pipe (22) of the heat exchanger (2) with the low pressure side gas line (32), the outdoor heat exchanger (2)
) acts as a condenser. In addition, each indoor unit (A
) and (B) are performing cooling/heating operation individually, the four-way switching valve (21) or the solid line or broken line will be activated depending on whether the total load of both units (A) and (B) is cooling load or heating load. The outdoor heat exchanger (2) functions as an evaporator or a condenser to meet the demands on the indoor side.

Here, a first embodiment regarding capacity control of the indoor heat exchanger (5) during cooling operation of each indoor unit (A) will be described based on the flowchart of FIG. 3.
In step S1, the indoor set temperature Ts and set temperature RHs are set.
When inputting , the suction air temperature Ta and the suction air humidity RH are inputted in step S, and in step S3, the required capacity e1 based on temperature and the required capacity e based on humidity are calculated by the following formula. That is, -(RH-RH3) is set in el -Kl (Ta -Ts) e2- (where Kl is a constant), and in step S4, the magnitudes of each ability elder obtained above are compared, and step S5. In S6, the larger one is set as the control function e (t).

Then, in step S7, the amount of change ΔShs in the target degree of superheating 5) Is for P1 control of the capacity of the indoor heat exchanger (5) based on the control function e (t) is calculated using the following formula 3%( ]] (where e(t)' is the control function at the previous sampling time, Tip is the integration time, and Δt is the sampling time), and then the new target value of the superheat degree SH, 5lls, is calculated using the following formula 3. Further, the target superheat degree 5l (s and control function e
(t) is updated.

Next, in step S8, the indoor electric expansion valve (5
1) Increment ΔEV of opening degree EV for PI control of opening degree
is calculated based on the following formula (% formula %).

Then, in step S9, a new indoor electric expansion valve (51
) and update it, and step S
A drive signal for the indoor electric expansion valve (51) is output at IO, and when the sampling time has elapsed at step S++, the process returns to each step S and repeats the above control.

In the above flow, the control in steps S4 to SIO constitutes the opening control means (101A) and (101B) in the invention of claims (11, [2)].

Further, by the control in step S3, the suction sensor (T h
Temperature-dependent capacity calculation means (102) is configured to calculate the required capacity e1 based on the temperature difference between the suction air temperature Ta detected in step 1) and the set temperature Ts. Humidity-dependent capacity calculation means (103) is configured to calculate the required capacity e2 based on the humidity difference between the suction air humidity RH detected at RH and the set humidity RHs.

Therefore, in the invention of claim (1), the opening control means (
101A), the indoor electric expansion valve ( pressure reducing valve) (5
1) The opening degree is controlled. In other words, in the case where only the opening control is performed based on the suction air temperature Ta as in the past, the first
As shown in FIG. 6, when the humidity RH is different, a difference occurs in the outlet air temperature Td for the same intake air temperature Ta. In particular, since the evaporation capacity used for dehumidification is large compared to the decrease in temperature, there is a risk that the comfort of air conditioning will be impaired if humidity is ignored. , such a difference in the temperature of the blown air is reduced, and the comfort of air conditioning can be improved.

In the invention of claim (2), the temperature dependent ability calculation means (10
The capacity e1 or e2 of the indoor heat exchanger (5) is set to the larger capacity e1 or e2 of the required capacity e1 based on the temperature calculated in step 2) and the required capacity e2 based on the humidity calculated by the humidity dependent capacity calculation means (103). Indoor electric expansion valve (5
1) The opening degree is controlled.

That is, as shown in FIG. 4, in the psychrometric diagram, for the difference in state quantities between the current state point P and the target point S (Ts, RHs), the humidity difference ΔR) on the enthalpy line 11) e line The enthalpy difference ΔiR+(=to+Δ
RH) or the enthalpy difference Δ17(-
or 2∆ton), whichever is greater, compared to conventional methods, especially when the humidity is high,
This has the advantage of solving the problem of insufficient cooling amount. In addition, in the above constant, ,K.

is set with a weight such as 5:1, for example, and is set to be the most reasonable value depending on the state of the device.

Next, the control contents of the second embodiment according to the invention of claim (3) will be explained based on the flowchart of FIG.

Here, in this embodiment, only the parts corresponding to steps S and %S6 in FIG. 3 in the first embodiment are shown, and the following control is made to follow the control in steps 87 to S11 in FIG. 3 above. There is.

That is, in steps S21 to S23, similar to steps S1 to S3 in FIG.
H is input, and the required capacity e1 based on temperature and the required capacity e2 based on humidity are calculated from them, and in step S24
Then, it is determined whether or not the required capacity e1 based on the temperature, which is set in advance as the priority required capacity, is larger than the predetermined value C1. If el > cl is YES, the control function e(t)-el is set in step S25. While setting, N of e1≦01.

If so, the control function e (t) 5=e2 at step Ss
The opening degree of the indoor electric expansion valve (51) is then PI-controlled based on this control function e (t).

In the above flow, the opening degree control means (101C) is constituted by the control in steps 824 to 326 and subsequent steps.

Therefore, in the invention of claim (3), as shown in the psychrometric diagram of FIG. Until e1 becomes less than a predetermined value, the required ability e1
While the capacity of the indoor heat exchanger (5) is controlled according to the above, even if the priority required capacity e1 decreases, the other required capacity e2
Even when the humidity is large (for example, when the humidity RH is high), the air conditioning state can be quickly converged to the set state (target point S in FIG. 4), and the comfort of the air conditioning can be improved.

Next, the control contents of the third embodiment according to the invention of claim (4) will be explained based on the flowchart of FIG. 6.
1 to S3, the required capacity e1 based on the temperature,
After calculating the required capacity e2 based on humidity, step S
34, the control function e(t)-e1+e2, that is, the sum of both required capacities el and e2, is set, and the control from steps 87 to Sl+ in FIG. 3 is thereafter performed.

In the above flow, the opening degree control means (101D) is configured by the control from step 834 onwards.

Therefore, in the invention of claim (4), as shown in FIG. 7, the opening control means (101D) controls the enthalpy difference Δiτ (= Kt ΔT) and humidity difference ΔX (ΔRH)
The capacity of the indoor heat exchanger (5) is controlled to converge with respect to the sum Δi of the enthalpy differences Δ1RT (−: ΔRH) corresponding to .

In other words, according to the cooling capacity that the room truly requires,
Since the evaporation capacity is controlled, the interior of the room can be rapidly brought to a target state, and the comfort of air conditioning can be significantly improved.

In the invention of claim (5), although the embodiment is omitted, in the invention of claim (4), when the parameter on the priority side (for example, the suction air temperature Ta) reaches the set value Ts, the thermostat is forcibly turned off. Therefore, the capacity of the indoor heat exchanger (5) is determined by the suction air temperature Ta and the suction air humidity Hu.
The advantage is that overshoot due to excess capacity can be suppressed by controlling the temperature based on both of these factors to quickly bring the temperature close to the target point S, and by immediately turning off the thermostat when the target point S is approached.

Next, the control contents of the fourth embodiment according to the invention of claim (6) will be explained based on the flowcharts of FIGS. 8A to 8C. In step R1, the set temperature Ts and the set humidity Rhs are manually set. , step R・, the suction sensor (T
In step R3, it is determined whether or not the suction air temperature Ta is higher than the set temperature Ts by manually inputting the detected values of the suction air temperature Ta and the suction air humidity R)l by the humidity sensor (Hu) and the humidity sensor (Hu). , if Ta > Ts is YES, proceed to cooling operation in step R5, while if Ta≦Ts is No.
If so, further in step R4, the suction air humidity RH and the set humidity RHs are compared, and if RH>RHs, the process proceeds to step R6 to perform dehumidification operation, and RHsR1 (
If it is s, the process moves to step R7 and the thermostat is turned off.

Then, in step R8, the process waits for the sampling time to elapse and returns to step R.

Here, FIG. 8B shows a subflow of control in cooling operation, in which the control function e (t) -TBTs is set in RIG, and the opening degree EV of the indoor electric expansion valve (51) is set in step SI+.
The amount of change ΔEV of is calculated based on the following formula % formula %( :1 (However, KS is a constant)
2"t knee new opening degree EV-EV'-+4EV, and in step RI3, a drive signal is output to bring the indoor electric expansion valve (51) to the new opening degree EV. Note that the reheat electric expansion valve (61)
) is closed.

Moreover, FIG. 8C shows the control contents in the dehumidification operation, and in step RI5, the control function e of the indoor electric expansion valve (51) is
(t)Ev is e(t)sv″−RHRHs, and the control function e(t)co of the reheat electric expansion valve (61) is defined as e(
t) c o =Ta−Ts, and in step RI6, each control function e (t)EV, e (t
6 valves (51) from the value obtained by substituting ) co in place of the control function e (t) in step R1+ (however, 4 + KS changes to a constant).

The opening changes ΔEV and ΔCO of (61) are calculated, and in step RI7, the new opening EVEV of 6 valves (51) and (61),
After calculating EVC○, a drive signal is output in step R111.

In the above flow, the control in steps RI5 to R18 causes the suction air humidity RH to change to the set humidity RHs during dehumidification operation.
an opening control means (101E) that controls the opening of the indoor electric expansion valve (pressure reducing valve) (51) so that The reheater (6) is controlled by controlling the opening of the flow control valve (61).
) is configured.

Therefore, in the invention of claim (6), as shown in FIG. 9, during dehumidification operation, the suction air at the state point PH (Tal, RHI) is brought into the state at the target point S (Ts, 'RHs). controlled. In other words, the capacity of the indoor heat exchanger (evaporator) (5) is controlled based on the humidity deviation ΔRH between the suction air humidity Rold and the set humidity RHs.
), the air blown from the indoor heat exchanger (5) changes to the state of state point P2 (T a2. RR2) in the figure, and the humidity RH2 first approaches the set humidity RHs.

Thereafter, the capacity of the reheater (6) is adjusted based on the temperature deviation ΔT between the suction air temperature Tal and the set temperature Ts, and finally the blowing air temperature approaches the set temperature Ts, and a predetermined dehumidification effect is obtained. It will be done.

Therefore, during dehumidification operation that is normally performed when the temperature is close to the set value, the cooling capacity and dehumidification capacity of the indoor heat exchanger (5) are controlled based on the humidity, while the capacity of the reheater (6) is controlled based on the humidity. Since it is controlled based on the air temperature Ta, each state quantity quickly converges to the target value.

Next, regarding the fifth embodiment according to the invention of claim (7),
To explain based on the flowcharts of FIGS. 10A to 10C, in step R2+, the set temperature Ts and the set humidity R
Hs manually, input the detected values of suction air temperature Ta and suction air humidity RH in step R22, and step R23.
The temperature deviation ΔT(-Ta-Ts) and the humidity deviation ΔRH(
-RH-RHs), with R24 and R25,
The capacity of the indoor heat exchanger (5) and reheater (6) is controlled respectively. When the sampling time elapses in step R26, the process returns to step R22 and repeats the above control.

Here, FIG. 103 shows the evaporation control of the indoor heat exchanger (5) in step R24, that is, the indoor electric expansion valve (
51) is a subflow showing the contents of the opening degree control, and in step RE, the control function e(1) is changed to e (t)- by 6
ΔRH+7ΔT (Ka.

R7 is a constant), and step RE2
Then, the opening degree change amount ΔEv of the indoor electric expansion valve (51) is calculated using the following formula, ΔEV-e (t) −e (t) ' + (Δt/2
Tip (e (t)+e (t)' 1) In step RE3, the new opening EV (-EV'
After calculating ΔEV), a drive signal for the indoor electric expansion valve (51) is output in step RE4.

On the other hand, FIG. 10C shows the details of the capacity control of the reheater (6), in which the control function e(1) is changed to e (t
) = 3ΔT (Ks is a constant), and in step RR2, the opening change amount ΔC of the reheat electric expansion valve (61) is calculated.
O is expressed as below, ΔCO=9[e (t) −e (t)
' +(Δt/2Ti p)(e (t)+e (t
)' ] ] (where R9 is a constant), and after calculating the new opening EVcO in step RR3, a drive signal is output in step RR4.

In the above flow, step RRI constitutes a temperature-dependent capacity calculation means (102) that calculates the required capacity e (t) based on temperature, and steps RR, to RR4 configure the temperature-dependent capacity calculation means (102) to calculate the required capacity e (t) based on temperature. A capacity control means (104B) is configured to control the capacity of the reheater (6) according to the required capacity e (t).

Therefore, in the invention of claim (7), as shown in FIG. 11, in the invention of claim (4) or (5),
The capacity of the indoor heat exchanger (5) is the temperature deviation ΔT and the humidity deviation Δ
R1 (required ability (enthalpy difference) calculated based on
The state point Q+ (Tal
, RHI) Q: After transitioning to the state of (Ta2°RH2), the opening degree of the reheat electric expansion valve (61) is changed according to 8ΔT to the required capacity based on the suction air temperature Ta, that is, The capacity of the reheater (6) is controlled, and the air at state point Q3 in the figure is supplied indoors.

In other words, even when the indoor heat exchanger (5) cools an excessive amount due to a large temperature deviation ΔRH, it is possible to ensure that the temperature of the blown air is lowered by heating in the reheater (6). can. By controlling the capacity of the reheater (6) in this way, it is possible to control the normal cooling operation, dehumidification operation, and heating operation continuously without discontinuously switching between them. This will result in a more noticeable improvement in comfort.

Next, the control contents of the sixth embodiment according to the invention of claim (8) will be explained based on the flowchart of FIG. 12. FIG. 12 shows only the subflow of the capacity control of the reheater (6) in the fifth embodiment, and the main flow and the capacity control of the indoor heat exchanger (5) are the same as in the fifth embodiment. The explanation will be omitted. Here, step RR
I+ calculates the control function e(t)co for controlling the opening degree EVcO of the reheat electric expansion valve (61) based on the following formula % formula % (however, KIO and Kl+ are both constants), and step In RR12, this control function e (t)CO
Based on this, the opening change amount ΔEVcO of the reheat electric expansion valve (61) is calculated by PI calculation similar to step RR in the fifth embodiment, and the new opening degree EVc is calculated in step RRI3.
After calculating O, a drive signal is output in step RR14.

In the above flow, steps RRII to RR.

From the required capacity KIOΔRH calculated by the humidity dependent capacity calculation means (103), the temperature dependent capacity calculation means (10
A capacity control means (104C) is configured to control the capacity of the reheater (6) in accordance with the required capacity difference obtained by subtracting the required capacity KllΔT calculated in step 2).

Therefore, in the invention of claim (8), as shown in FIG.
Therefore, even if the current control reaches state point T2 and the cooling amount increases, the heating amount in the reheater (6) will be increased by the increased amount, and the blowing air temperature SA will be the same as the previous one. It becomes approximately equal to the blown air temperature SA'. That is,
More stable control becomes possible, and therefore the comfort of air conditioning can be improved more significantly.

Next, the control contents of the seventh embodiment according to the invention of claim (9) will be explained based on the flowchart of FIG. 14. FIG. 14 shows only the sub-flow related to the control of the reheater (6) in the fifth embodiment, and the main flow and the sub-flow related to the capacity control of the indoor heat exchanger (5) are the same, so their explanation will be omitted. In Fig. 14, step RR2+, RR iron, set temperature Ts and suction air temperature T
A is performed manually, and in step RR23, the temperature difference ΔT between the two is calculated. Then, in step RR24, a target value SAs of the outlet temperature SA (target outlet temperature) is calculated based on this temperature deviation ΔT. In other words, based on the following formula (% formula %) )) (where Kn is a constant), the change amount ΔSAs in the target outlet temperature is calculated from the current temperature deviation ΔT with respect to the temperature deviation ΔT' at the previous sampling time, and then ,
A new target outlet temperature SAs is calculated based on the following formula % formula %.

Next, in step RR25, the liquid temperature sensor (Th3)
The degree of supercooling Sc of the refrigerant detected at is its minimum value 5cIl
Whether it is smaller than lin or the above step RR2
The target outlet temperature SAs calculated in , 1 is the maximum value SAs...
Determine whether Sc<Scn+i is larger than aX.
If either ns or S As > S Asmax is established, it is determined that the capacity of the reheater (6) cannot be increased any further, and in step RR26, SAs
-S Asaax, but if none of the above relationships hold true, the process directly proceeds to step RR27, and further determines whether SA<S As++in, and if SAs<S Asm1n holds true, step RRn Assume that S As −S As'. Then, in step RR4, when the sampling time has elapsed,
Return to step RR.

In the meantime, in step RR3: after calculating the change amount ΔEV of the opening degree EV of the reheat electric expansion valve (61) based on the following formula (% formula %), the new opening degree is further calculated based on the following formula EV-EV+ΔEV. The EV is calculated, a drive signal is output in step RR3, and after waiting for the sampling time to elapse in step RR32, the process returns to step RR30 and the above control is repeated.

In the above flow, step RR24 sets the target outlet temperature SAs based on the temperature deviation ΔT between the intake air temperature Ta and its set temperature Ts.
105) is configured, and in steps RRo and RR31, the blowing air temperature S^ is set to the target blowing air temperature setting means (105).
) to reach the target outlet temperature SAs set in the reheater (
A capacity control means (104D) is configured to control the capacity of 6).

Therefore, in the invention of claim (9), as shown in FIG. 15, after the intake air at the state point U1 is cooled by the indoor heat exchanger (5) and moves to the state point U2, (105), the target blowout temperature SAs is set based on the value of the suction air temperature Ta, and the capacity control means (104D
), the outlet air temperature SA becomes the target outlet temperature SAs.
The capacity of the reheater (6) is controlled so that In other words, the outlet air temperature SA indicated by state point U3 in the figure is controlled so as to directly converge to the target value, and the feedback is lower than when the control is performed only based on the intake air temperature Ta, which has changed due to mixing with indoor air. The state of the blown air can be controlled without causing control instability due to delays.
Therefore, the comfort of air conditioning can be significantly improved.

In the above embodiment, the reheater (6) is connected to the refrigerant circuit (10).
), but the present invention is not limited to such an embodiment, and for example, an electric heater or the like may be used to heat the air. , similar effects can be obtained by controlling the ability as in the above embodiment.

(Effects of the Invention) As explained above, according to the invention of claim (1), the opening degree of the pressure reducing valve that adjusts the capacity of the evaporator of the refrigeration system is adjusted to the target values of the suction air temperature and the suction air humidity. Therefore, even when the humidity is different, it is possible to maintain approximately the same outlet air temperature for the same intake air temperature, thereby improving the comfort of air conditioning.

According to the invention of claim (2), since the opening degree of the pressure reducing valve is controlled according to the larger required capacity between the required capacity based on the suction air temperature and the required capacity based on the suction air humidity, Even when the temperature is high, the capacity of the evaporator can be controlled without causing a shortage of cooling amount.

According to the invention of claim (3), the opening degree of the pressure reducing valve is adjusted according to a preset priority required capacity among the required capacity based on the suction air temperature and the required capacity based on the suction air humidity. When the required capacity reaches a predetermined value, the opening degree of the pressure reducing valve is controlled according to the required capacity on the non-priority side.
While controlling the capacity of the evaporator through simple control at the beginning, it is possible to ultimately adjust the capacity accurately, and therefore,
The comfort of air conditioning can be significantly improved.

According to the invention of claim (4), the capacity of the evaporator is controlled according to the sum of the required capacity based on the suction air temperature and the required capacity based on the suction air humidity. The capacity of the evaporator can be controlled to match the high evaporation capacity required by the system, and the comfort of air conditioning can be significantly improved by rapidly converging to the target state.

According to the invention of claim (5), in the invention of claim (4), when the preset state quantity on the priority side reaches the set value, the thermostat is forcibly turned off. There is an advantage in that it is possible to greatly control the capacity of the evaporator to quickly converge to the target state, while suppressing overshoot due to an excessive amount of cooling.

According to the invention of claim (6), a reheater is disposed on the downstream side of the fan ventilation path with respect to the evaporator and heats the air, and during dehumidification operation, the opening degree of the pressure reducing valve of the evaporator is adjusted. The reheater capacity is controlled according to the required capacity based on the suction air temperature, and the reheater capacity is controlled according to the required capacity based on the suction air temperature. During operation, the reheater allows fine adjustment of the temperature while appropriately controlling the amount of cooling in the evaporator based on humidity.
Comfortable dehumidification operation can be performed.

Claim (According to the invention of the sword, the above claim (4) or (5)
) In addition to the above invention, the reheater is placed downstream of the evaporator in the fan ventilation path, and the refrigerant flow rate to the reheater is controlled according to the required capacity based on the suction air temperature. To be able to continuously control indoor air conditioning conditions without discontinuously switching operation modes such as cooling operation, dehumidification operation, heating operation, etc., and thereby to more significantly improve the comfort of air conditioning. I can do it.

According to the invention of claim (8), the above claim (4) or (
In addition to the invention of 5), a reheater is placed downstream of the evaporator in the fan ventilation path, and reheating is performed according to the required capacity difference between the required capacity based on the suction air humidity and the required capacity based on the suction air temperature. Since the capacity of the reheater is controlled, even if the temperature of the blown air tends to drop due to an increase in the amount of cooling in the evaporator, this reduction is guaranteed by increasing the amount of heating in the reheater. Therefore, more stable control can be performed.

According to the invention of claim (9), the above claim (4) or (
In addition to the invention of 5), a reheater is arranged downstream of the evaporator in the fan ventilation path, a target value of the blowout air temperature is set based on the intake air temperature, and the blowout temperature matches the target blowout temperature. Since the capacity of the reheater is controlled in this way, the temperature of the outlet air can be controlled without the delay of controlling the state quantity that has passed through the room, resulting in more pronounced air conditioning. The comfort of the vehicle can be improved.

[Brief explanation of drawings]

1A to 1D show the structure of the invention, FIG. 1A is the invention according to claim (1), FIG. 1B is the invention according to claims (2) to (5), and FIG. 1C is the invention according to claim (6). FIG. 1D is a block diagram showing the configuration of the invention according to claims (7) to (9). 2 to 15 show embodiments of the present invention, FIG. 2 is a refrigerant piping system diagram of an air conditioner, and FIGS.
3 is a flowchart showing the control contents, FIG. 4 is an psychrometric diagram showing changes in the state quantity of air blowing, FIG. 5 is a flowchart showing the control contents in the second embodiment, and FIG. 6 is a flowchart showing the control contents. and Fig. 7 show the third embodiment, Fig. 6 is a flowchart showing the control contents, Fig. 7 is an psychrometric diagram showing changes in the state quantity of air blowing, and Figs. 8 and 9 show the fourth embodiment. 8A to 8C are flowcharts showing a main flow, a subflow for controlling the opening of the indoor electric expansion valve, and a subflow for controlling the opening of the reheat electric expansion valve, respectively, and FIG. The psychrometric diagrams, FIGS. 10 and 11, which show changes in the state quantities of
Figures A to 10C are flowcharts showing the main flow, the sub-flow for the opening control of the indoor electric expansion valve, and the sub-flow for the opening control of the reheat electric expansion valve, respectively, and Figure 11 shows the state quantity change of the air blower. An psychrometric diagram showing
12 and 13 show the sixth embodiment, FIG. 12 is a flowchart showing a sub-flow for controlling the opening of the electric reheating expansion valve, and FIG. 13 is an psychrometric diagram showing changes in the state quantity of air blowing. , FIG. 14 and FIG. 15 show the seventh embodiment,
FIG. 14 is a flowchart showing a subflow regarding the opening degree control of the electric reheating expansion valve, and FIG. 15 is an psychrometric diagram showing changes in the state quantity of air blowing. FIG. 16 is an psychrometric diagram showing changes in the state of conditioned air in conventional control. 1 Compressor 2 Outdoor heat exchanger (condenser) 5 Indoor heat exchanger (evaporator) 10 1 01 02 03 04 05 hl h2 u Reheater refrigerant circuit indoor electric expansion valve (pressure reducing valve) Opening control means temperature dependent Capacity calculation means Humidity dependence Capacity calculation means Capacity control means Target outlet temperature setting means Suction sensor (Suction air temperature detection means) Outlet sensor (Outlet temperature detection means) Humidity sensor (Humidity detection means) 4th decoy 6th figure / 21gi R8, Figure 8B Figure 8C Figure 108m1 Figure 10C Figure 8A Fu Figure 9 Figure 10A Figure 11 Adventure 15 Horse 16 Akane 246-

Claims (9)

[Claims] (1) In a refrigeration system equipped with a refrigerant circuit (10) in which a compressor (1), a condenser (2), a pressure reducing valve (51) whose opening degree can be adjusted, and an evaporator (5) are connected in sequence, Suction air temperature detection means (Th1
), and a humidity detection means (Hu) for detecting the humidity of the intake air.
In response to the outputs of the suction air temperature detection means (Th1) and humidity detection means (Hu), the opening degree of the pressure reducing valve (51) is adjusted so that the suction air temperature and suction air humidity become the set temperature and humidity, respectively. Control opening control means (101A
). An operation control device for a refrigeration system. (2) In a refrigeration system equipped with a refrigerant circuit (10) in which a compressor (1), a condenser (2), a pressure reducing valve (51) whose opening degree can be adjusted, and an evaporator (5) are successively connected, Suction air temperature detection means (Th1
), and a humidity detection means (Hu) for detecting the humidity of the intake air.
and a temperature-dependent capacity calculation means (102) for calculating the required capacity based on the temperature difference between the suction air temperature detected by the suction air temperature detection means (Th1) and the set temperature, and the humidity detection means (Hu). Humidity-dependent capacity calculation means (103) calculates the required capacity based on the humidity difference between the detected suction air humidity and the set humidity, and the capacity of the evaporator (5) is calculated by both calculation means (102) and (103). The pressure reducing valve (51) is adjusted so that the required capacity is the larger of the two calculated required capacities.
1. An operation control device for a refrigeration system, comprising an opening control means (101B) for controlling the opening of the refrigeration system. (3) In a refrigeration system equipped with a refrigerant circuit (10) formed by sequentially connecting a compressor (1), a condenser (2), a pressure reducing valve (51) whose opening degree can be adjusted, and an evaporator (5), Suction air temperature detection means (Th1
), and a humidity detection means (Hu) for detecting the humidity of the intake air.
and a temperature-dependent capacity calculation means (102) for calculating the required capacity based on the temperature difference between the suction air temperature detected by the suction air temperature detection means (Th1) and the set temperature, and the humidity detection means (Hu). Humidity-dependent capacity calculation means (103) that calculates the required capacity based on the humidity difference between the detected suction air humidity and the set humidity; The opening degree of the pressure reducing valve (51) is controlled so that the capacity of the evaporator (5) reaches the above-mentioned priority required capacity, while when the prioritized required capacity becomes less than a predetermined value, the capacity of the evaporator (5) changes to the other required capacity. Opening degree control means (101C) for controlling the opening degree of the pressure reducing valve (51) so that
An operation control device for a refrigeration system, characterized by comprising: (4) In a refrigeration system equipped with a refrigerant circuit (10) in which a compressor (1), a condenser (2), a pressure reducing valve (51) whose opening degree can be adjusted, and an evaporator (5) are connected in sequence, Suction air temperature detection means (Th1
), and a humidity detection means (Hu) for detecting the humidity of the intake air.
and a temperature-dependent capacity calculation means (102) for calculating the required capacity based on the temperature difference between the suction air temperature detected by the suction air temperature detection means (Th1) and the set temperature, and the humidity detection means (Hu). Humidity-dependent capacity calculation means (103) that calculates the required capacity based on the humidity difference between the detected suction air humidity and the set humidity; and the pressure reducing valve so that the capacity of the evaporator (5) becomes the sum of both required capacities. (51) An operation control device for a refrigeration system, comprising an opening degree control means (101D) for controlling the opening degree of the refrigeration system. (5) The opening degree control means (101D) controls the thermostat to be forcibly turned off when a predetermined priority required capacity among both required capacities becomes less than a set value. Operation control device for refrigeration equipment. (6) In a refrigeration system equipped with a refrigerant circuit (10) formed by sequentially connecting a compressor (1), a condenser (2), a pressure reducing valve (51) whose opening degree can be adjusted, and an evaporator (5), It is installed on the downstream side of the evaporator (5) in the ventilation path of the evaporator fan (57), and is equipped with a reheater (6) that heats the air, as well as a suction air temperature detection means (Th1) that detects the suction air temperature.
), and a humidity detection means (Hu) for detecting the humidity of the intake air.
and an opening degree control means (101E) for controlling the opening degree of the pressure reducing valve (51) so that the suction air humidity detected by the humidity detecting means (Hu) becomes a set humidity during the dehumidifying operation; Refrigeration characterized by comprising: capacity control means (104A) for controlling the capacity of the reheater (6) so that the suction air temperature detected by the suction air temperature detection means (Th1) becomes a set temperature. Equipment operation control device. (7) It is installed on the downstream side of the evaporator (5) in the ventilation path of the evaporator fan (57), and includes a reheater (6) that heats the air, and is calculated by the temperature dependent capacity calculation means (102). Claim (4) or (5) comprising a capacity control means (104B) for controlling the capacity of the reheater (6) according to the required capacity based on the temperature.
) The operation control device for the refrigeration equipment described in . (8) It is installed downstream of the evaporator (5) in the ventilation path of the evaporator fan (57) and includes a reheater (6) that heats the air, and is calculated by the humidity dependent capacity calculation means (103). Claim (4) further comprising a capacity control means (104C) for controlling the capacity of the reheater (6) in accordance with a required capacity difference between the required capacity and the required capacity calculated by the temperature-dependent capacity calculation means (102). )
Or the operation control device for an air conditioner according to (5). (9) Installed on the downstream side of the evaporator (5) in the ventilation path of the evaporator fan (57), equipped with a reheater (6) that heats the air, and receives the output of the suction air temperature detection means (Th1). , a target outlet temperature setting means (105) for setting a target temperature of the outlet air temperature based on the temperature difference between the intake air temperature and its set temperature; an outlet temperature detecting means (Th2) for detecting the outlet air temperature; Capacity control means receives the output of the temperature detection means (Th2) and controls the capacity of the reheater (6) so that the temperature of the discharged air reaches the target discharge air temperature set by the target discharge temperature setting means (105). (104D)
4) or the operation control device for a refrigeration device according to (5).