JPH07158998A - Heat pump type cooling and heating device provided with hot water supply or addional boiling unit - Google Patents

Abstract

PURPOSE:To provide a high reliability heat pump type heating device which is capable of both heating and supplying hot water simultaneously without discomforting the user. CONSTITUTION:Letting the difference between a detected high pressure P by a high pressure detector 25 and a target high pressure Pdm be DELTAPd and the difference between a detected low pressure Ps by a low pressure detector 26 and a target low pressure Psm be DELTAPs for every operation mode, a capacity changing variable DELTAQcomp of a compressor 1 and an air capacity changing variable DELTAVout are computed from the following equation: DELTAQcomp=(d DELTAPd-b DELTAPs)/(a.d-b.c). DELTAVout=(-c.DELTAPd+a.DELTAPs/(a.d-b.c). This device controls a compressor 1 based on the computed capacity changing variable DELTAQcomp and an outdoor fan 12 based on the air capacity changing variable DELTAVout respectively. This construction makes it possible to control the compressor 1 highly efficiently and elaborately to comply with changes in operation mode.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a main refrigerant circuit in which a compressor, an accumulator, an indoor heat exchanger, an outdoor heat exchanger and a pressure reducing device are connected by a refrigerant pipe, and a refrigerant and circulating water in the main refrigerant circuit. The present invention relates to a heat pump type cooling / heating device provided with a hot water supply or a reheating unit having a hot water supply or a reheating heat exchanger for exchanging heat.

[0002]

2. Description of the Related Art FIG. 18 is a block diagram showing an example of a conventional heat pump type cooling and heating apparatus equipped with this kind of hot water supply unit. In the figure, (1) is a compressor, (2) is a four-way switching valve, (3)
Is an indoor heat exchanger, (4a) and (4b) are expansion valves, (5a) and (5b) are check valves for bypass, (6) is a receiver, (7) is an outdoor heat exchanger, and (8) is Accumulator, (9) refrigerant pipe, (10) compressor (1),
Four-way switching valve (2), indoor heat exchanger (3), liquid receiver (6), outdoor heat exchanger (7), accumulator (8), and expansion valve (4a) (4b) A main refrigerant circuit connecting a pressure reducing device to the refrigerant pipe (9), (11) an indoor fan for cooling the indoor heat exchanger (3), (12) an outdoor fan for cooling the outdoor heat exchanger (7), (1
3) is a hot water storage tank, (14) is the refrigerant and hot water storage tank (13) of the main refrigerant circuit (10)
Hot water supply heat exchanger for exchanging heat with circulating water to the water, (15) hot water supply pump, (21) hot water supply unit, (22) refrigerant pipe to hot water supply unit (21), (23) electromagnetic control valve, (24) is a control device, (25)
Is a high-pressure pressure detector that detects the pressure of the refrigerant on the discharge side of the compressor (1).

Next, the operation at the time of simultaneous heating and hot water supply operation will be described. The high-temperature high-pressure refrigerant gas discharged from the compressor (1) flows through the refrigerant pipe (9) through the four-way switching valve (2) in the indoor heat exchanger (3) and the refrigerant pipe (22) as indicated by the solid arrow. The solenoid control valve (2
Pass through the hot water heat exchanger (14) via 3). Indoor heat exchanger (3)
In, the refrigerant exchanges heat with the air to heat the air, and becomes a high-pressure liquid refrigerant to flow out from the indoor heat exchanger (3). Further, in the hot water supply heat exchanger (14), the water in the hot water storage tank (13) is sucked from the lower part by the hot water supply pump (15) and flows into the hot water supply heat exchanger (14) having a double pipe structure. Then, it is heated by the refrigerant from the main refrigerant circuit (10) and returns to the upper part of the hot water storage tank (13).

The high-pressure liquid refrigerant flowing out of the indoor heat exchanger (3) flows through the check valve (5a) into the liquid receiver (6) and merges with the refrigerant flowing out of the hot water supply heat exchanger (14). Then, the expansion valve (4b) becomes a low-pressure two-phase refrigerant and flows into the outdoor heat exchanger (7). Here, the low-pressure two-phase refrigerant is heat-exchanged with the outside air to become a low-pressure refrigerant gas, which flows out from the outdoor heat exchanger (7), and then the four-way switching valve
(2) Return to the suction side of the compressor (1) via the accumulator (8).

The controller (24) controls the opening degree of the electromagnetic control valve (23) so that the high pressure detected by the high pressure detector (25) is within a predetermined range, and the hot water heat exchanger (14) ), The amount of heat exchange by is controlled.

[0006]

Since the conventional heat pump type cooling / heating apparatus having the hot water supply unit is constructed as described above, it is possible to temporarily stop the operation when the temperature of the water in the hot water storage tank is low during the simultaneous heating and hot water supply operation. As a result, the heating capacity is significantly reduced, which makes the heating user uncomfortable, and the control of the high pressure is performed by controlling the opening of the electromagnetic control valve.
Since it is carried out by changing the amount of the refrigerant to (14), there is a problem in that the control cannot obtain high reliability.

The present invention has been made to solve the above problems, and it is possible to obtain high reliability in controlling high pressure during heating / hot water supply or simultaneous operation of additional heating, and An object of the present invention is to obtain a heat pump type cooling and heating device provided with a hot water supply or reheating unit that does not cause a heating user to feel uncomfortable due to a temporary decrease in heating capacity due to simultaneous operation.

[0008]

According to a first aspect of the present invention, there is provided a heat pump type cooling and heating apparatus, which comprises a high pressure detector for detecting a refrigerant pressure on a discharge side of a compressor and a low pressure detector for detecting a refrigerant pressure on a suction side. From the deviation between the high pressure detected by the high pressure detector and the target high pressure and the deviation between the low pressure detected by the low pressure detector and the target low pressure, the capacity change amount of the compressor and the above by a predetermined relational expression. A calculation means for calculating the air flow rate change amount of the outdoor fan that cools the outdoor heat exchanger,
Compressor control means for controlling the compressor according to the capacity change amount of the compressor calculated by the calculating means, and the outdoor fan according to the air flow rate change amount of the outdoor fan calculated by the calculating means. And a controller having an outdoor fan control means.

According to a second aspect of the present invention, in the heat pump type heating and cooling apparatus according to the first aspect of the invention, the predetermined relational expression of the calculating means is: detected high pressure _Pd , target high pressure _Pdm , detected low pressure _Is P _s , the target low pressure is P _sm , and their deviations are ΔP _d = P _dm −P _d , ΔP _s = P _sm −P _s , the compressor capacity change amount ΔQ _comp and the outdoor fan air flow rate change. The quantity ΔV _out is defined by the following determinant

[Equation 2] By solving the following equation ΔQ _comp = (d · ΔP _d −b · ΔP _s ) / (a · d−b ·
c) ΔV _out = (− c · ΔP _d + a · ΔP _s ) / (a · d−b
・ This is the formula obtained in c).

A heat pump type cooling and heating apparatus according to a third aspect of the present invention includes a high pressure detector for detecting the refrigerant pressure on the inlet side of the hot water heat exchanger and an outlet side for detecting the refrigerant temperature on the outlet side of the hot water heat exchanger. Refrigerant temperature detector, hot water temperature detector for hot water tank, and set supercooling degree determining means for determining the set subcooling degree at the outlet of the hot water heat exchanger according to the detected temperature of the hot water temperature detector, the high pressure detection Current supercooling degree calculating means for calculating the current supercooling degree at the outlet of the hot water supply heat exchanger from the detected high pressure of the air conditioner and the temperature detected by the outlet side refrigerant temperature detector, and hot water supply calculated by the current supercooling degree calculating means Hot water supply heat exchanger refrigerant that controls the refrigerant amount control valve from the main refrigerant circuit to the hot water heat exchanger so that the current supercooling degree at the outlet of the heat exchanger becomes the set supercooling degree determined by the set supercooling degree determining means. With a controller having a quantity control means It is intended.

A heat pump type cooling and heating apparatus according to a fourth aspect of the present invention detects a hot water supply flow rate control valve for controlling the circulating water flow rate of the hot water supply heat exchanger and a hot water supply water pipe temperature at the outlet side of the hot water supply heat exchanger. A hot water supply water pipe outlet temperature detector, and a controller having a hot water supply water flow rate control valve control means for controlling the hot water supply water flow rate control valve so that the temperature detected by the hot water supply water pipe outlet temperature detector becomes a predetermined constant value. It is provided.

According to a fifth aspect of the present invention, there is provided a heat pump type cooling and heating apparatus according to the first or second aspect,
A hot water temperature detector is installed in the hot water storage tank, the operating frequency of the compressor is made variable, and the capacity of the compressor is controlled by changing this operating frequency.The controller is used to supply hot water during heating operation of the main refrigerant circuit. A difference frequency calculation means for calculating the difference between the maximum operation frequency and the actual operation frequency of the compressor according to the operation request of the unit, and the difference frequency calculated by this means is predetermined according to the temperature detected by the hot water temperature detector. A hot water supply unit operation start control means for starting the operation of the hot water supply unit only when the value is equal to or more than the value is provided.

According to a sixth aspect of the present invention, there is provided the heat pump type cooling and heating apparatus according to the first or second aspect,
A hot water temperature detector is installed in the hot water storage tank, the operating frequency of the compressor is made variable, and the capacity of the compressor is controlled by changing this operating frequency.The controller is equipped with a main refrigerant circuit during operation of the hot water supply unit. In response to the heating operation request, the hot water supply / heating switching means that suspends the operation of the hot water supply unit and starts the heating operation, and the difference between the maximum operating frequency and the actual operating frequency of the compressor during the heating operation after switching by this means A difference frequency calculating means for calculating, and a restart control means of the hot water supply unit for restarting the operation of the hot water supply unit only when the difference frequency calculated by this means is equal to or higher than a predetermined value according to the detected temperature of the hot water temperature detector. Be prepared.

A heat pump type cooling and heating apparatus according to the invention of claim 7 is the same as the invention of claim 1 or 2,
A hot water temperature detector is provided in the hot water storage tank, the operating frequency of the compressor is made variable, and the capacity of the compressor is controlled by changing this operating frequency.The controller is equipped with a heating operation for the main refrigerant circuit and a hot water supply unit. Hot water supply unit suspension control means for suspending the operation of the hot water supply unit in response to the fact that the discharge side refrigerant pressure cannot be controlled to the target high pressure even with the maximum capacity of the compressor due to an increase in heating load during simultaneous operation with A difference frequency calculating means for calculating the difference between the maximum operating frequency and the actual operating frequency of the compressor during the heating operation after the operation of the hot water supply unit is stopped by this means, and the difference frequency calculated by this means is the hot water temperature detector. The hot water supply unit operation restart control means for restarting the operation of the hot water supply unit only when the temperature is equal to or higher than a predetermined value according to the detected temperature.

The heat pump type cooling and heating apparatus according to the invention of claim 8 is the same as the invention of claim 1 or 2,
If the discharge side refrigerant pressure cannot be controlled to the target high pressure even with the maximum capacity of the compressor during the simultaneous operation of the main refrigerant circuit heating operation and the hot water supply unit operation, the controller lowers this target high pressure to a specified value. The target high pressure reducing means is provided, and the hot water supply unit operation suspension control means for suspending the operation of the hot water supply unit when the discharge side refrigerant pressure cannot be controlled even by the target high pressure reduced by this means.

A heat pump type air conditioner according to a ninth aspect of the present invention is the heat pump type air conditioner according to any one of the first to eighth aspects, further comprising a reheating unit instead of or in addition to the hot water supply unit. Is a reheating heat exchanger and a hot water storage tank as a bath.

[0017]

According to the first aspect of the present invention, a predetermined relational expression is used for each operation mode from the deviation between the detected high pressure and the target high pressure and the deviation between the detected low pressure and the target low pressure.
The capacity change amount of the compressor and the air flow rate change amount of the outdoor fan are calculated, and the compressor is controlled by the calculated capacity change amount, and the outdoor fan is controlled by the air volume change amount, respectively, to operate with high efficiency.

According to the second aspect of the present invention, the deviation ΔP _d between the detected high pressure P _d and the target high pressure P _dm and the deviation ΔP between the detected low pressure P _s and the target low pressure P _sm for each operation mode. from _s to the determinant

[Equation 3] By solving the following equation ΔQ _comp = (d · ΔP _d −b · ΔP _s ) / (a · d−b ·
c) ΔV _out = (− c · ΔP _d + a · ΔP _s ) / (a · d−b
From · c), the air volume change amount [Delta] V _out of capacity change amount Delta] Q _comp an outdoor fan of the compressor is calculated, these calculated capacity change amount Delta] Q _comp the compressor, outdoor fan by airflow change amount [Delta] V _{ou t} Are controlled respectively and operated with high efficiency.

According to the third aspect of the invention, the current degree of subcooling at the outlet of the hot water heat exchanger calculated from the high pressure which is the refrigerant pressure at the inlet of the hot water heat exchanger and the refrigerant temperature at the outlet of the hot water heat exchanger. However, the amount of refrigerant from the main refrigerant circuit to the hot water supply heat exchanger is controlled so that the set subcooling degree at the hot water supply heat exchanger outlet is set according to the hot water temperature of the hot water storage tank.

According to the fourth aspect of the present invention, the circulating water flow rate of the hot water supply heat exchanger is controlled so that the temperature of the hot water supply water piping on the outlet side of the hot water supply heat exchanger has a predetermined constant value.

In the fifth aspect of the invention, when there is an operation request for the hot water supply unit during the heating operation, the difference between the maximum operating frequency of the compressor and the actual operating frequency is calculated, and the difference frequency is the hot water temperature of the hot water storage tank. Accordingly, operation of the hot water supply unit is started only when the frequency is equal to or higher than a predetermined frequency.

According to the sixth aspect of the present invention, when a heating operation request is issued during operation of the hot water supply unit, the operation of the hot water supply unit is once suspended and the heating operation is started. then,
The difference between the maximum operating frequency of the compressor and the actual operating frequency is calculated, and the operation of the hot water supply unit is restarted only when the difference frequency is equal to or higher than a frequency predetermined according to the hot water in the hot water storage tank.

According to the seventh aspect of the present invention, when the heating load increases during the simultaneous heating and hot water supply operation and the discharge side refrigerant pressure cannot be controlled to the target high pressure, the hot water supply unit is temporarily stopped and the heating operation is started. Then, the difference between the maximum operating frequency and the actual operating frequency of the compressor is calculated, and the operation of the hot water supply unit is restarted only when the difference frequency is equal to or higher than the frequency predetermined according to the hot water temperature of the hot water storage tank.

In the eighth aspect of the invention, the heating operation is switched from the heating operation to the heating hot water supply simultaneous operation, or the heating load suddenly increases during the heating hot water supply simultaneous operation, and the discharge side refrigerant pressure is controlled to the target high pressure. If it becomes impossible, the target high pressure is once lowered to a predetermined value, and when the target high pressure cannot be controlled even still, the operation of the hot water supply unit is suspended.

In the invention described in claim 9, in the invention described in each of the above claims, a reheating unit is provided instead of the hot water supply unit or in addition to the hot water supply unit, and the same control as the hot water supply unit is added. Performed on units.

[0026]

【Example】

Example 1. Examples of the present invention will be described below. 1 to 4 show Embodiment 1 of the present invention, FIG. 1 is a configuration diagram, FIG. 2 is a configuration diagram illustrating a cooling operation, FIG. 3 is a configuration diagram illustrating a heating and hot water supply simultaneous operation, and FIG. 4 is a control block. It is a diagram.

In the figure, (1) is a compressor, (3) is an indoor heat exchanger, (7) is an outdoor heat exchanger, (8) is an accumulator, and (9a).
Is a refrigerant pipe for high-pressure gas, (9b) is a refrigerant pipe for low-pressure gas,
c) is a refrigerant pipe for liquid refrigerant, (10) is a main refrigerant circuit, (11) is an indoor fan for cooling the indoor heat exchanger (3), and (12) is an outdoor fan for cooling the outdoor heat exchanger (7). , (13) is a hot water storage tank, (14) is a hot water supply heat exchanger, (15) is a hot water supply pump, (16) is a heater for heating,
(17) is the outlet side hot water supply water pipe of the hot water heat exchanger (14), (18) is the hot water supply pipe, (19) is the water supply pipe, (20) is the hot water supply flow control valve, (2)
1) is a hot water supply unit, (25) is a high pressure pressure detector that detects the discharge side refrigerant pressure of the compressor (1), (26) is a low pressure pressure detector that detects the suction side refrigerant pressure of the compressor (1), (27) is a reheating unit, (28) is a reheating heat exchanger, (29) is a reheating pump, (3)
0) is a bathtub.

(31a) (31b) (31c) (31d) (31e) (31f) (31g) (31
h) is a two-way valve, and (32a) is a cooling / heating refrigerant amount control valve, which constitutes the pressure reducing device of the main refrigerant circuit (10). (32b) is a refrigerant amount control valve for the hot water supply unit, (32c) is a refrigerant amount control valve for the reheating unit, (40) is a controller including a microcomputer, (41) is this controller (40) The compressor (1) is calculated from the deviation between the high pressure detected by the high pressure detector (25) and the target high pressure and the deviation between the low pressure detected by the low pressure detector (26) and the target low pressure. Compression function force change amount calculation means (42) for calculating the capacity change amount and the outdoor fan air flow change amount calculation means (43) for calculating the air flow change amount of the outdoor fan (12)
Consists of. (44) is a compressor control means for controlling the compressor (1) according to the calculated capacity change amount, and (45) is an outdoor fan control for controlling the outdoor fan (12) according to the calculated air flow change amount. It is a means.

Next, referring to FIG. 2, the operation of the cooling operation in which the outdoor heat exchanger (7) becomes a condenser will be described. During cooling operation, the two-way valve (31a) (31d) (31e) (31f) (31g) (31h) and the refrigerant amount control valve (32b) (32c) is closed, the two-way valve (31b) (31c) and the refrigerant The quantity control valve (32a) is opened.

The high-temperature high-pressure refrigerant gas discharged from the compressor (1) passes through the outdoor heat exchanger (7) from the refrigerant pipe (9a) via the two-way valve (31c). In the outdoor exchanger (7), the refrigerant becomes a high-pressure liquid refrigerant by exchanging heat with the outside air, and flows out from the outdoor heat exchanger (7). The liquid refrigerant flowing out is
After passing through c), the refrigerant amount control valve (32a) reduces the pressure to a low-pressure two-phase refrigerant, which flows into the indoor heat exchanger (3). Here, the low-pressure two-phase refrigerant cools the air by exchanging heat with the air, and the refrigerant evaporates into a low-pressure refrigerant gas, which flows out from the indoor heat exchanger (3). The low-pressure refrigerant gas that has flowed out returns to the suction side of the compressor (1) via the two-way valve (31b), the refrigerant pipe (9b), and the accumulator (8).

In the above main refrigerant circuit (10), the compressor
High pressure detector (25) provided in the high pressure gas section from the discharge port of (1) to the refrigerant pipe (9a), and the accumulator (8)
From the low pressure detector (26) installed in the low pressure gas section from the compressor to the suction port of the compressor (1), the controller (4
In (0), the capacity of the compressor (1) and the air volume of the outdoor fan (12) are controlled.

That is, the high pressure P _d detected by the high pressure detector (25) and the low pressure P _s detected by the low pressure detector (26)
Are taken into the calculation means (41) of the controller (40), and the compression function force change amount calculation means (42) and the outdoor fan air flow change amount calculation means
In (43), the target high pressure P _dm and the target low pressure P _sm
And the deviations ΔP _d = P _dm −P _d and ΔP _s = P _sm −P _s are obtained. From these deviations ΔP _d and ΔP _s , the following determinant is obtained.

[0033]

[Equation 4]

The following equation ΔQ _comp = (d · ΔP _d −b · ΔP _s ) / (a · d−b · c) (1) ΔV _out = (− c · ΔP _d + a · ΔP _s ) The compression function force change amount ΔQ _comp and the outdoor fan air flow change amount ΔV _out are calculated from / (a · d−b · c) (2). These compression function force change amount ΔQ
_The compressor is controlled by the compressor control means (44) and the outdoor fan control means (45) according to _comp and the amount of change ΔV _out of the outdoor fan air volume.
(1) and the outdoor fan (12) are controlled.

The coefficients a, b, c and d in the above equations (1) and (2) are obtained by experiments. In the cooling operation in which the outdoor heat exchanger (7) is a condenser, a ₁ , b ₁ , When c ₁ and d ₁ > 0, a = a
₁ , b = −b ₁ , c = −c ₁ , d = −d ₁ . Rewriting equations (1) and (2) with this coefficient, ΔQ _comp = (d ₁ · ΔP _d −b ₁ · ΔP _s ) / (a ₁ · d ₁ + b ₁ · c ₁ ) (3) ΔV _out = − (C ₁ · ΔP _d + a ₁ · ΔP _s ) / (a ₁ · d ₁ + b ₁ · c ₁ ) (4)

For example, here, the pressure P _d detected by the high pressure detector (25) is lower than the target high pressure P _dm , and the pressure P _s detected by the low pressure detector (26) is lower than the target low pressure P _sm . When it is high, that is, when ΔP _d > 0 and ΔP _s <0, the capacity change amount ΔQ _comp of the compressor (1) in the above equation is the capacity of the compressor (1) from high pressure and low pressure. Both of the factors of the amount of change become positive, and the amount of change in capacity of the compressor (1) ΔQ
_comp > 0.

Further, the amount of air flow change of the outdoor fan (12) ΔV _out
For factors from high pressure, see High Pressure Detectors (25)
In order that the pressure P _d detected in step up to the target high pressure P _dm rises, the air flow rate of the outdoor fan (12) is reduced to reduce the heat exchange amount on the condenser side to raise the high pressure, but for the low pressure, In order to lower the low pressure by lowering the high pressure, the air volume of the outdoor fan (12) is increased to increase the heat exchange amount on the condenser side and to lower the high pressure. The air flow rate change amount ΔV _out is determined by the coefficient a ₁ ,
Depending on the weighting of c ₁ , it becomes positive or negative.

However, basically, when the outdoor heat exchanger (7) is a condenser, it is considered that the main body of control on the high pressure side is the air flow rate change amount ΔV _out of the outdoor fan (12), and Deviation ΔP _d
The coefficient c ₁ is weighted more than a ₁ for the deviation ΔP _s on the low pressure side, and the main component of the control on the low pressure side is the compressor.
_Assuming that the capacity change amount ΔQ _{comp in} (1) is used, the weighting of the coefficient b ₁ to the deviation ΔP _s on the low voltage side is applied to the deviation ΔP on the high voltage side.
It should be larger than d ₁ for P _d .

Next, referring to FIG. 3, the operation of the heating and hot water supply simultaneous operation in which the outdoor heat exchanger (7) becomes an evaporator will be described. Two-way valve (31b) (31c) (31f) when heating and hot water are operating simultaneously
(31g) (31h) and refrigerant amount control valve (32c) are closed, two-way valve (31a)
(31d) (31e) and the refrigerant amount control valves (32a) (32b) are opened.

The high-temperature and high-pressure refrigerant gas discharged from the compressor (1) is introduced from the refrigerant pipe (9a) through the two-way valve (31a), the indoor heat exchanger (3) and the two-way valve (31e). And flows into the hot water heat exchanger (14). In the indoor heat exchanger (3), the refrigerant heat-exchanges with air to heat the air to become a high-pressure liquid refrigerant, and flows out from the indoor heat exchanger (3). Also, hot water heat exchanger (14)
In, the water in the hot water storage tank (13) is sucked from the lower part of the hot water storage tank (13) by the hot water supply pump (15), flows into the hot water heat exchanger (14) having a double pipe structure, and the refrigerant circulates. While circulating water is heated by exchanging heat with water, it becomes a high-pressure liquid refrigerant and flows out from the hot water supply heat exchanger (14), while the heated circulating water exits the hot water supply heat exchanger (14). Hot water storage tank from the water pipe (17)
Return to the upper part of (13).

The liquid refrigerant flowing out of the indoor heat exchanger (3) passes through the refrigerant amount control valve (32a) to become a low-pressure two-phase refrigerant, and the high-temperature liquid refrigerant flowing out of the hot water heat exchanger (14) is The low-pressure two-phase refrigerant passes through the refrigerant amount control valve (32b), and the refrigerant pipe (9
In c), it merges with the refrigerant having passed through the indoor heat exchanger (3) and flows into the outdoor heat exchanger (7). Here, the low-pressure two-phase refrigerant exchanges heat with the outside air to become a low-pressure refrigerant gas, which flows out from the outdoor heat exchanger (7). The low-pressure refrigerant gas that has flowed out returns to the suction side of the compressor (1) via the two-way valve (31d), the refrigerant pipe (9b), and the accumulator (8).

Even in the heating and hot water supply simultaneous operation, the controller (40) receives the signals from the high pressure pressure detector (25) and the low pressure pressure detector (26), and the capacity of the compressor (1) and the outdoor fan.
Although the air volume in (12) is controlled, the coefficients a, b, c and d in the above equations (1) and (2) are a ₂ , b ₂ when the outdoor heat exchanger (7) is an evaporator. , C ₂ , d ₂ > 0, a =
_{a 2, b = b 2,} c = -c 2, the d = d _2. Rewriting equations (1) and (2) with this coefficient, ΔQ _comp = (d ₂ · ΔP _d −b ₂ · ΔP _s ) / (a ₂ · d ₂ + b ₂ · c ₂ ) (5) ΔV _out = ( c ₂ · ΔP _d + a ₂ · ΔP _s ) / (a ₂ · d ₂ + b ₂ · c ₂ ) (6)

For example, here, the pressure P _d detected by the high pressure detector (25) is lower than the target high pressure P _dm , and the pressure P _s detected by the low pressure detector (26) is lower than the target low pressure P _sm . When it is high, that is, when ΔP _d > 0 and ΔP _s <0, in the equation (5), the capacity change amount ΔQ _comp of the compressor (1) is calculated from the high pressure and low pressure of the compressor (1). Both factors of the capacity change amount become positive, and the capacity change amount of the compressor (1) ΔQ
_comp > 0.

Further, the amount of air flow change of the outdoor fan (12) ΔV _out
For the factors from low pressure, the low pressure detector (2
As the pressure P _d detected in 6) falls to the target low pressure P _dm, it works to reduce the heat exchange amount on the evaporator side by lowering the air volume of the outdoor fan (12), but lower the low pressure. In order to increase the high pressure by increasing the low pressure, the outdoor fan (12) works by increasing the air volume of the outdoor fan (12) to increase the heat exchange amount on the evaporator side and increase the low pressure. The air flow rate change amount ΔV _{out of)} is positive or negative depending on the weighting of the coefficients a ₂ and c ₂ .

However, basically, when the outdoor heat exchanger (7) is an evaporator, it is considered that the main body of control on the low pressure side is due to the air flow rate change amount ΔV _out of the outdoor fan (12) and the low pressure side. Deviation of
Weighting coefficient a ₂ for P _s was greater than things c ₂ for the deviation △ P _d of the high-pressure side, the subject of control of the high pressure side as on the ability change amount △ Q _comp compressor (1), the high-pressure side the weighting coefficient d ₂ for the deviation △ P _d to be greater than the ones b ₂ for the low-pressure side of the deviation △ P _s.

Although only the heating and hot water supply simultaneous operation has been described above, heating alone operation, hot water supply independent operation, heating heating simultaneous operation, heating hot water heating and heating simultaneous operation, hot water heating and simultaneous heating operation, additional heating alone operation are also possible. However, in any of these cases, since the outdoor heat exchanger (7) operates the evaporator, the capacity change amount ΔQ _{comp of} the compressor (1) and the air flow change amount ΔV of the outdoor fan (12) are increased. The calculation of _out is the same as that for the simultaneous heating and hot water supply operation, and thus its description is omitted.

Control of the capacity control of the compressor (1) and the air volume control of the outdoor fan (12) by the detection pressures P _d and P _s of the high pressure pressure detector (25) and the low pressure pressure detector (26). The system can be shown in a control block diagram as in FIG.

Example 2. Next, a second embodiment of the present invention will be described. 5 to 7 show Embodiment 2 of the present invention,
5 is a configuration diagram, FIG. 6 is a flow chart for explaining the operation, and FIG. 7 is a time chart for explaining the operation.

In the figure, (25) is a high pressure detector for detecting the inlet side refrigerant pressure of the hot water supply heat exchanger (14), and (32b) is supplied from the main refrigerant circuit (10) to the hot water supply heat exchanger (14). Refrigerant amount control valve for controlling the amount of refrigerant to be stored, (33) is a hot water temperature detector for the hot water storage tank (13), (34) is an outlet side refrigerant temperature for detecting the outlet side refrigerant temperature of the hot water heat exchanger (14) A detector, (50) a controller for controlling the amount of refrigerant in the hot water heat exchanger, (51) a setting that determines the degree of supercooling at the outlet of the hot water heat exchanger according to the temperature detected by the hot water temperature detector (33) The subcooling degree determining means, (52), calculates the current subcooling degree at the outlet of the hot water heat exchanger from the high pressure detected by the high pressure detector (25) and the temperature detected by the outlet side refrigerant temperature detector (34). The current supercooling degree calculating means, (53), the current supercooling degree of the hot water supply heat exchanger outlet calculated by the current supercooling degree calculating means (52) is determined by the set supercooling degree determining means (51). It becomes the set supercooling degree Hot water supply heat exchanger refrigerant amount control means for controlling the refrigerant amount control valve (32b). The same parts as those in FIG. 1 are denoted by the same reference numerals.

Next, the operation of this embodiment during the simultaneous heating and hot water supply operation will be described. The heat pump operation by the refrigerant of the main refrigerant circuit (10) and the hot water supply unit (21) is the same as that of the first embodiment, so the description thereof is omitted and the hot water heat exchanger of the hot water supply unit (21) is omitted.
The refrigerant amount control of (14) will be described with reference to the flowchart of FIG.

During the heating and hot water supply simultaneous operation, the hot water temperature of the hot water storage tank (13) is detected by the hot water temperature detector (33) in step (S1), and the hot water temperature is detected in step (S2). The set subcooling degree at the outlet of the hot water supply heat exchanger (14) is determined to a predetermined value (the higher the hot water temperature, the higher the value) (the set subcooling degree determining means (5
1)), in step (S3), the refrigerant amount control valve (32b) is controlled so as to achieve the set supercooling degree (hot water supply heat exchanger refrigerant amount control means (53)). That is, when the set degree of supercooling is large, the refrigerant amount control valve (32b) is controlled to be narrowed.

Next, in step (S4), the high pressure detector (25)
The refrigerant pressure on the inlet side of the hot water heat exchanger (14) detected by the hot water heat exchanger (14) is detected by the refrigerant temperature detector (34) on the outlet side.
At the outlet side refrigerant temperature of each is detected, step (S5)
Then, the current supercooling degree at the outlet of the hot water heat exchanger (14) is calculated from the detected pressure and temperature (current supercooling degree calculating means (5
2)). That is, the set degree of supercooling at the outlet of the hot water supply heat exchanger (14) is the difference between the saturated refrigerant temperature of the inlet side refrigerant temperature and the outlet side refrigerant temperature.

Next, in step (S6), the current supercooling degree at the outlet side of the hot water heat exchanger (14) is compared with the set subcooling degree. If the current subcooling degree does not reach the set subcooling degree, step ( Returning to S3), the control of the refrigerant amount control valve (32b) is continued until the set supercooling degree is reached, and when the set supercooling degree is reached, the process proceeds to step (S7).
Next, in step (S7), it is determined whether the heating capacity has decreased due to the difference between the room temperature and the set room temperature.
In (S8), the set subcooling degree is further increased and the process returns to step (S3). If it does not decrease, the process returns to step (S1), the set subcooling degree is changed according to the change in the hot water temperature, and the refrigerant amount control valve It is controlled to change the opening of 32b).

For example, when the hot water temperature in the hot water storage tank (13) is considerably lower than the indoor air temperature, the refrigerant flows more easily into the hot water supply heat exchanger (14) than the indoor heat exchanger (3). If so, the heating capacity is temporarily and sharply reduced, resulting in discomfort to the heating user. Therefore, when the hot water temperature in the hot water storage tank (13) is considerably lower than the indoor air temperature, the set subcooling degree at the outlet of the hot water heat exchanger (14) is set to a large value, and the refrigerant amount control valve (32b) is set. The hot water supply heat exchanger
Limit the amount of refrigerant flowing to (14). This makes it possible to prevent a rapid decrease in heating capacity and reduce discomfort to the heating user.

When the hot water supply operation is continued, the hot water storage tank hot water temperature detector (3
When the temperature in 3) gradually rises, the set subcooling degree determining means (51) determines the set subcooling degree at the outlet of the hot water heat exchanger (14) to be a small value stepwise. As a result, the opening of the refrigerant amount control valve (32b) moves stepwise in the opening direction, the refrigerant easily flows into the hot water supply heat exchanger (14), and the boiling of the hot water is accelerated. However, since the temperature of the hot water has risen to some extent at this time, there is no such thing that the hot water supply heat exchanger (14) flows more easily than the indoor heat exchanger (3), and the heating capacity is not reduced. Absent. FIG. 7 shows the situation at this time.

In this way, the set subcooling degree at the outlet of the hot water supply heat exchanger (14) is determined according to the detected temperature of the hot water tank hot water temperature detector (33), and the hot water supply heat is set to the set subcooling degree. Exchanger (14)
By controlling the amount of refrigerant flowing through, it is possible to perform simultaneous heating and hot water supply operation without lowering the heating capacity, without causing discomfort to the heating user, and without significantly delaying the boiling time of hot water supply. .

Example 3. Next, a third embodiment of the present invention will be described. 8 and 9 show Embodiment 3 of the present invention,
FIG. 8 is a block diagram and FIG. 9 is a flow chart for explaining the operation. In the figure, (20) is a hot water supply flow rate control valve for controlling the circulating water flow rate of the hot water supply heat exchanger (14), and (35) is hot water supply for detecting the pipe temperature of the hot water supply heat exchanger outlet side hot water supply water pipe (17). Water pipe outlet temperature detector, (60) is a controller for hot water supply flow rate control,
(61) is a hot water supply flow rate control valve control means for controlling the hot water supply flow rate control valve (20) so that the temperature detected by the hot water supply water outlet temperature detector (35) becomes a predetermined constant value. The same parts as those in FIG. 1 are denoted by the same reference numerals.

Next, the operation of this embodiment at the time of simultaneous heating and hot water supply operation will be described. The heat pump operation by the refrigerant of the main refrigerant circuit (10) and the hot water supply unit (21) is the same as that of the first embodiment, so the description thereof is omitted and the hot water heat exchanger of the hot water supply unit (21) is omitted.
The hot water supply flow rate control of (14) will be described with reference to the flowchart of FIG.

During the heating and hot water supply simultaneous operation, the outlet temperature of the hot water supply water pipe (17) is detected by the hot water supply water pipe outlet temperature detector (35) in step (S9), and this detected temperature and a predetermined temperature are detected in step (S10). A set temperature (for example, 45 ° C) that is a constant value is compared, and if the detected temperature does not reach the set temperature, step (S
11), the hot water supply flow rate control valve (20) is controlled so that the detected temperature becomes the set temperature (the hot water supply flow rate control valve control means (6
1)). That is, if the temperature in the hot water supply pipe (17) is lower than the set temperature, the hot water supply flow rate control valve (20) is controlled to be narrowed.

When the detected temperature reaches the set temperature, step (S
From (10) to step (S9), while the detected temperature is maintained at the set temperature, the loop of step (S9) → step (S10) (YES) → step (S9) is repeated and the hot water tank (13) Wait for the hot water temperature to rise. When the hot water temperature rises, the hot water supply pipe outlet temperature detected by the temperature detector (35) in step (S9) also rises above the set temperature, which is detected in step (S10) and proceeds to step (S11). The hot water supply flow rate control valve (20) is controlled to open until the detected temperature falls to the set temperature.

For example, when the hot water temperature in the hot water storage tank (13) is considerably lower than the indoor air temperature, the refrigerant flows more easily into the hot water supply heat exchanger (14) than the indoor heat exchanger (3). If so, the heating capacity is temporarily and sharply reduced, resulting in discomfort to the heating user. Therefore, when the hot water temperature in the hot water storage tank (13) is considerably lower than the room air temperature and the temperature of the water flowing into the hot water supply heat exchanger (14) is considerably lower than the indoor air temperature, the hot water supply pipe outlet temperature detector (35 ) Is kept at a constant temperature of, for example, 45 ° C., the opening of the hot water supply water flow control valve (20) is narrowed and the flow rate of water flowing into the hot water supply heat exchanger (14) is reduced. The heat exchange amount due to) will decrease as a whole. As a result, the capacity thereof is moved to the heating side, the rapid decrease of the heating capacity is prevented, and the discomfort to the heating user can be reduced.

When the hot water temperature in the hot water storage tank (13) gradually rises as the hot water supply operation continues, the temperature of the water flowing into the hot water supply heat exchanger (14) also rises. When the temperature of (35) is controlled to be constant at 45 ° C, the opening degree of the hot water supply water flow control valve (20) gradually moves in the opening direction, and the flow rate of water flowing into the hot water supply heat exchanger (14) also gradually increases. I will do it. As a result, the boiling speed of the hot water supply is faster than when the opening of the hot water supply water flow control valve (20) is narrowed, but the temperature of the water flowing into the hot water supply heat exchanger (14) is rising. ,
The heat exchange amount of the hot water supply heat exchanger (14) does not suddenly increase and the heating capacity is not reduced.

In this way, the hot water supply pipe outlet temperature detector (3
By controlling the hot water supply flow rate control valve (20) so that the detection temperature of 5) becomes a certain set temperature, the heating capacity is not reduced and the heating water is heated without causing discomfort to the heating user. The heating and hot water supply simultaneous operation can be performed without delaying the raising time so much.

Example 4. Next, a fourth embodiment of the present invention will be described. 10 and 11 show Embodiment 4 of the present invention, FIG. 10 is a configuration diagram, and FIG. 11 is a flow chart for explaining the operation. In the figure, (25) is a high-pressure pressure detector that detects the discharge side refrigerant pressure of the compressor (1), and (26) is the compressor.
Low pressure detector to detect the suction side refrigerant pressure of (1), (33)
Is a hot water temperature detector of the hot water storage tank (13), and (36) is hot water supply unit opening / closing means including two-way valves (31e) (31f) and a refrigerant amount control valve (32b).

(70) is a controller for compressor capacity control and hot water supply operation start control, (42) is a compression function force change amount calculation means for calculating the capacity change amount of the compressor (1), and (71) is Compressor operating frequency control means for controlling the capacity of the compressor by changing the operating frequency of the compressor, (72), in response to the operation request of the hot water supply unit (21) during the heating operation of the main refrigerant circuit (10), the compression is performed. Machine
The difference frequency calculation means for calculating the difference between the maximum operation frequency and the actual operation frequency in (1), (73), the difference frequency calculated by this means (72) depends on the temperature detected by the hot water temperature detector (33). The hot water supply unit operation start control means starts the operation of the hot water supply unit (21) only when the value is equal to or more than a predetermined value. The same parts as those in FIG. 1 are denoted by the same reference numerals.

Next, the operation when shifting from the heating operation to the heating and hot water supply simultaneous operation in this embodiment will be described. Since the heat pump operation by the refrigerant of the main refrigerant circuit (10) and the hot water supply unit (21) and the capacity control operation of the compressor from the high pressure and the low pressure are the same as those in the first embodiment, the description thereof is omitted, and the operation of the hot water supply unit (21) is omitted. The operation switching control will be described with reference to the flowchart of FIG.

During the heating operation in step (S12), step
When there is an operation request from the hot water supply unit (21) in (S13), the actual operation frequency F detected from the compressor (1) in step (S14).
A difference ΔF between e and the maximum operating frequency Fm of the compressor (1) stored in advance in the controller (70) is calculated (difference frequency calculating means (72)). Next, in step (S15), the hot water temperature detector (33) detects the hot water temperature θ of the hot water storage tank (13), and in step (S16), it is determined whether ΔF is 10 Hz or more. If ΔF is not 10 Hz or more, the operating frequency Fe of the compressor (1), which is controlled by the compressor operating frequency control means (71) so that the high pressure becomes the target pressure, reaches the maximum operating frequency Fm and 10 Hz. Since it is operated at a frequency close to this, there is no difference, and there is no surplus capacity for hot water supply operation, the process proceeds to step (S17), and an operation standby signal is sent to the hot water supply unit (21).

If the difference ΔF between the maximum operating frequency Fm and the actual operating frequency Fe of the compressor (1) is 10 Hz or more and lower than 15 Hz, steps (S16) to (S18), (S19)
Then, in step (S19), the hot water temperature θ is 10 Hz
It is determined whether the value is 20 ° C. or higher, which is a predetermined value for 15 Hz. If the temperature is lower than 20 ° C., it is determined that there is no surplus capacity for hot water supply operation at this hot water temperature, the process proceeds to step (S17), and an operation standby signal is sent to the hot water supply unit (21). If the temperature is 20 ° C. or higher, it is determined that there is an excess capacity for hot water supply operation, and the process proceeds to step (S20) to open the two-way valve (31e) and the refrigerant amount control valve (32b) of the hot water supply unit on / off means (36). Then, the operation of the hot water supply unit (21) is started (operation start control means (73)).

Similarly, the difference frequency ΔF is 15 Hz to 20 Hz.
If so, step (S18) to step (S21), step
Proceed to (S22), and it is judged whether the hot water temperature θ is 15 ° C or higher, 1
If it is lower than 5 ° C, proceed to step (S17), and the hot water supply unit
An operation standby signal is sent to (21), and if it is 15 ° C. or higher, the operation proceeds to step (S20) to start the operation of the hot water supply unit (21). If ΔF is 20 to 25 Hz, step
From (S21) to step (S23) and step (S24), it is determined whether the hot water temperature θ is 10 ° C or higher, and if it is lower than 10 ° C, the process proceeds to step (S17) and the operation standby signal to the hot water supply unit (21). Is sent out, and if it is 15 ° C or higher, step (S20)
Then, the operation of the hot water supply unit (21) is started. ΔF is 2
If it is 5 Hz or more, the process proceeds to step (S20), the operation of the hot water supply unit (21) is unconditionally started, and the heating and hot water supply simultaneous operation is started at step (S25).

As described above, when the compressor (1) is operated at a frequency close to the maximum operating frequency, the hot water supply operation is temporarily suspended unconditionally and is operated at a frequency lower than the maximum operating frequency by a predetermined value or more. While operating, the heating and hot water supply operation is unconditionally started, and when operating at the frequency between them,
Depending on whether the hot water temperature of the hot water storage tank (13) is higher or lower than the value corresponding to the difference frequency from the maximum operation frequency, it is determined whether the hot water supply operation is suspended or the simultaneous heating and hot water supply operation is started.

That is, with respect to the surplus capacity estimated from the difference between the maximum operating frequency of the compressor (1) and the actual operating frequency of the hot water in the hot water storage tank (13), the heating capacity is lowered even when hot water supply operation is performed. Only when it is judged not to do so, the heating and hot water supply simultaneous operation is started. For example, if a compressor equivalent to 3 hp is used and the difference frequency from the maximum operating frequency is 10 to 15 Hz, it is considered that there is a hot water supply capacity of about 1000 kcal / h and the hot water temperature is 20 ° C or higher, 15 to 20 Hz. About 2000kca
It is considered that there is a l / h capacity for hot water supply, and when the hot water temperature is 15 ° C or higher and 20 to 25 Hz, it is considered that there is a hot water supply capacity of approximately 3000 kcal / h. The operation of the hot water supply unit (21) is started as it is possible to raise the hot water temperature by -10 ° C / h.

Example 5. Next, a fifth embodiment of the present invention will be described. 12 and 13 show Embodiment 5 of the present invention, FIG. 12 is a configuration diagram, and FIG. 13 is a flow chart for explaining the operation. In the figure, (25) is a high pressure detector, (26) is a low pressure detector, (33) is a hot water temperature detector for the hot water tank (13), (36) is a hot water supply unit opening / closing means, and (37) is Two-way valve (3
The heating on / off means includes 1a) and (31b) and a refrigerant amount control valve (32a).

Reference numeral (70) is a controller, (42) is a compression function force change amount calculation means, (71) is a compressor operating frequency control means, and (72) is a maximum operation of the compressor (1) during heating operation. The difference frequency calculation means for calculating the difference between the frequency and the actual operating frequency, (74), in response to the heating operation request during the hot water supply operation, suspends the operation of the hot water supply unit (21) and starts the heating operation. In the hot water supply / heating switching means for controlling the cutting means (36) and the heating on / off means (37), the difference frequency calculated by the difference frequency calculation means (72) is the hot water temperature of the hot water storage tank (13). The hot water supply unit operation restart control means controls the hot water supply unit on / off means (36) so as to restart the operation of the hot water supply unit (21) only when the value is equal to or more than a predetermined value. The same parts as those in FIG. 1 are denoted by the same reference numerals.

Next, the operation of shifting from the hot water supply single operation to the heating hot water supply simultaneous operation in this embodiment will be described. Since the heat pump operation by the refrigerant of the main refrigerant circuit (10) and the hot water supply unit (21) and the capacity control operation of the compressor from the high pressure and the low pressure are the same as those in the first embodiment, the description thereof will be omitted and the operation switching between heating and hot water supply will be omitted. The control will be described with reference to the flowchart of FIG.

During the hot water supply operation of step (S26), the two-way valves (31a) (31b) and the refrigerant amount control valve (32a) of the heating on / off means (37).
Are closed together, the two-way valve of the hot water supply unit opening / closing means (36)
(31e) and the refrigerant amount control valve (32b) are open. This time,
When there is a heating operation request from the indoor unit in step (S27), the two-way valve (31e) and the refrigerant amount control valve (32b) of the hot water supply unit on / off means (36) are closed in step (S28) to supply hot water. The operation of the unit (21) is stopped, an operation standby signal is sent, and in step (S29), the two-way valve (31) of the heating on / off means (37) is
a) and the refrigerant amount control valve (32b) are opened to start the heating operation, and the heating independent operation is started in step (S30) (hot water supply / heating switching means (74)).

Next, in step (S31), the difference ΔF between the actual operating frequency Fe of the compressor (1) and the maximum operating frequency Fm is calculated (difference frequency calculating means (72)), and in step (S32) the hot water temperature is calculated. The detector (33) detects the hot water temperature θ of the hot water storage tank (13),
At (S33), it is determined whether ΔF is 10 Hz or more. ΔF is 10
If it is not higher than Hz, return to step (S30), hot water supply unit
The resumption of (21) is abandoned and heating independent operation is continued.

If ΔF is 10 Hz or higher and lower than 15 Hz, steps (S33) to (S34) and (S35)
Then, in step (S35), it is determined whether the hot water temperature θ is 20 ° C. or higher. If the temperature is lower than 20 ° C, the operation returns to step (S30) and the heating independent operation is continued.
(31e) and refrigerant quantity control valve (32b) are reopened and hot water supply unit
The operation of (21) is restarted (operation restart control means (75)).

Similarly, the difference frequency ΔF is 15 Hz to 20 Hz.
If so, step (S34) to step (S37), step
Proceed to (S38), it is judged whether the hot water temperature θ is 15 ° C or higher, and 1
If it is lower than 5 ° C, the operation returns to step (S17) and the heating independent operation is continued, and if it is 15 ° C or more, the operation proceeds to step (S36) and the operation of the hot water supply unit (21) is restarted. ΔF is 20Hz
If it is 25 Hz, step (S37) to step (S39),
It proceeds to step (S40), and it is determined whether the hot water temperature θ is 10 ° C or higher. If it is lower than 10 ° C, the process returns to step (S17) to continue the heating independent operation, and if it is 15 ° C or higher, step (S36).
Then, the operation of the hot water supply unit (21) is restarted. ΔF is 2
If it is 5 Hz or more, the process proceeds to step (S36), the operation of the hot water supply unit (21) is unconditionally restarted, and the heating and hot water supply simultaneous operation is started at step (S41).

Example 6. Next, a sixth embodiment of the present invention will be described. 14 and 15 show Embodiment 6 of the present invention, FIG. 14 is a configuration diagram, and FIG. 15 is a flow chart for explaining the operation thereof. In the figure, (25) is a high pressure pressure detector, (26) is a low pressure pressure detector, (33) is a hot water temperature detector for the hot water tank (13), (36) is a hot water supply unit opening / closing means, and (70) is Controller,
(42) is a compression function force change amount calculation means, (71) is a compressor operation frequency control means, (72) is a difference frequency calculation means, (75) is a hot water supply unit operation restart control means, and (76) is a heating Due to an increase in heating load during simultaneous hot water supply operation, even if the compressor's maximum capacity cannot control the discharge side refrigerant pressure to the target high pressure, the hot water supply unit on / off means (stops the operation of the hot water supply unit (21). It is a hot water supply unit operation suspension control means for controlling 36). The same parts as those in FIG. 1 are denoted by the same reference numerals.

Next, the operation of the present embodiment during the simultaneous operation of heating and hot water supply will be described. Main refrigerant circuit (10) and hot water supply unit
The heat pump operation by the refrigerant of (21) and the capacity control operation of the compressor from the high pressure and the low pressure are described in Example 1.
Since it is the same as the above, the description will be omitted, and the operation switching control for heating and hot water supply will be described with reference to the flowchart in FIG.

During the heating / hot water supply simultaneous operation in step (S42),
In step (S43), the high-pressure pressure detector (25) detects the discharge-side high-pressure pressure of the compressor (1), and in step (S44) it is determined whether it is controlled to the target high-pressure pressure. If it is controlled, the process returns to step (S42) and the simultaneous heating and hot water supply operation is continued. At this time, the heating load increases, and even if the compressor (1) is operated at the maximum operating frequency to reach the target high pressure, if the detected high pressure falls below the target high pressure, steps (S44) to (S45) Then, the two-way valve (31e) and the refrigerant amount control valve (32b) of the hot water supply unit opening / closing means (36) are closed, the operation of the hot water supply unit (21) is stopped, and an operation standby signal is sent (hot water supply). Unit operation suspension control means), and heating independent operation starts in step (S46).

Next, in step (S47), the difference ΔF between the actual operating frequency Fe of the compressor (1) and the maximum operating frequency Fm is calculated (difference frequency calculating means (72)), and the hot water temperature is calculated in step (S48). The detector (33) detects the hot water temperature θ of the hot water storage tank (13),
At (S49), it is determined whether ΔF is 10 Hz or more. ΔF is 10
If it is not higher than Hz, return to step (S46), hot water supply unit
The resumption of (21) is abandoned and heating independent operation is continued.

If ΔF is 10 Hz or more and lower than 15 Hz, steps (S49) to (S50) and (S51)
Then, in step (S51), it is determined whether the hot water temperature θ is 20 ° C. or higher. If the temperature is lower than 20 ° C, the operation returns to step (S46) to continue the independent heating operation, and if the temperature is 20 ° C or more, the operation proceeds to step (S52) and the two-way valve of the hot water supply unit on / off means (36).
(31e) and refrigerant quantity control valve (32b) are restarted
The operation of (21) is restarted (operation restart control means (75)).

Similarly, the difference frequency ΔF is 15 Hz to 20 Hz.
If so, step (S50) to step (S53), step
Proceed to (S54), it is judged whether the hot water temperature θ is 15 ° C or higher, and 1
If it is lower than 5 ° C, the operation returns to step (S46) and the heating independent operation is continued, and if it is 15 ° C or more, the operation proceeds to step (S52) and the operation of the hot water supply unit (21) is restarted. ΔF is 20Hz
If it is 25 Hz, from step (S53) to step (S55),
It proceeds to step (S56), it is determined whether the hot water temperature θ is 10 ° C or higher, and if it is lower than 10 ° C, the process returns to step (S46) to continue the independent heating operation, and if it is 15 ° C or higher, step (S52)
Then, the operation of the hot water supply unit (21) is restarted. ΔF is 2
If it is 5 Hz or more, the process proceeds to step (S52), the operation of the hot water supply unit (21) is unconditionally restarted, and the heating and hot water supply simultaneous operation is started at step (S42).

Example 7. Next, a seventh embodiment of the present invention will be described. 16 and 17 show Embodiment 7 of the present invention, FIG. 16 is a configuration diagram, and FIG. 17 is a flow chart for explaining the operation. In the figure, (25) is a high pressure pressure detector, (26) is a low pressure pressure detector, (36) is a hot water supply unit opening / closing means, (80) is a controller, (42) is a compression functional force change amount calculation means, (44) is a compressor control means, (81) reduces the target high pressure to a predetermined value when the discharge side refrigerant pressure cannot be controlled to the target high pressure even if the compressor (1) is operated at the maximum capacity. The target high pressure reducing means for outputting a signal to the compression force change amount calculating means (42) so that the discharge side refrigerant pressure cannot be controlled even with the target high pressure reduced by this means (81). The hot water supply unit operation suspension control means controls the hot water supply unit on / off means (36) so as to suspend the operation of the hot water supply unit (21). The same parts as those in FIG. 1 are denoted by the same reference numerals.

Next, the operation at the time of shifting from the heating operation to the heating and hot water supply simultaneous operation in this embodiment will be described. Since the heat pump operation by the refrigerant of the main refrigerant circuit (10) and the hot water supply unit (21) and the capacity control operation of the compressor from the high pressure and the low pressure are the same as those in the first embodiment, the description thereof is omitted, and the operation of the hot water supply unit (21) is omitted. The operation switching control will be described with reference to the flowchart of FIG.

During the heating operation of step (S57), step
When there is an operation request from the hot water supply unit (21) in (S58), the two-way valve (31e) of the hot water supply unit on / off means (36) is step (S59).
Further, the refrigerant amount control valve (32b) is opened to start the operation of the hot water supply unit (21), and the heating and hot water supply simultaneous operation is started in step (S60). During the heating and hot water supply simultaneous operation, the high-pressure pressure detector (25) detects the high-pressure on the discharge side of the compressor (1) at step (S61), and at step (S62) it is the target high-pressure pressure, for example, 2
It is determined whether the temperature is controlled to 0 kgf / cm ² , and if the target high pressure is controlled, the process returns to step (S60), and the heating and hot water supply simultaneous operation is continued.

If the detected high pressure is not controlled to the target high pressure and the detected high pressure is lower than the target high pressure, the process proceeds to step (S63), and the target high pressure used for the calculation of the compression function force change amount calculating means (42), for example, 20 kgf / cm ² is a predetermined value, for example 18 kgf / c
Reduce to m ² (target high pressure reduction means) and step again
The high pressure is detected in (S64), and it is determined whether the detected high pressure is controlled to the changed target high pressure, for example, 18 kgf / cm ² , and if the target high pressure is reached, the process returns to step (S60). , The heating and hot water simultaneous operation can be continued. When the target low high pressure, for example, 18 kgf / cm ² is not controlled, the process proceeds to step (S66), and the two-way valve (31e) and the refrigerant amount control valve (32b) of the hot water supply unit on / off means (36) are closed. Then, the operation of the hot water supply unit (21) is stopped, an operation standby signal is sent (hot water supply unit operation suspension control means), and the process returns to step (S57) to start the independent heating operation.

In this embodiment, as described in the first embodiment, the capacity of the compressor (1) is controlled so that the high pressure becomes the target high pressure. Therefore, when the heating load increases due to the start of the hot water supply operation or during the heating and hot water supply simultaneous operation, the discharge refrigerant pressure moves in the direction of decreasing and the capacity of the compressor (1) increases. However, even if the compressor (1) is operated at the maximum capacity, the high pressure may not reach the target high pressure. At that time, the target high pressure is, for example, 20 kg.
Switchable from f / cm ² to 18 kgf / cm ² . Therefore, when the high temperature pressure was 20 kgf / cm ² and the blowing temperature of the indoor unit was around 45 ° C, it became 4 kg when it became 18 kgf / cm ^2.
It goes down to around 0 ° C. However, if the blowing temperature of 40 ° C. can be secured, the heating user is not so discomforted.

In this way, when the heating operation is switched to the simultaneous heating and hot water supply operation, or when the heating load suddenly increases during the simultaneous heating and hot water supply operation, it becomes impossible to operate at the target high pressure during heating operation. Since the target high pressure during heating operation is changed to the minimum high pressure at which the heating capacity can be ensured without causing a large discomfort to the heating user in the simultaneous heating and hot water supply operation, the operation is performed. By effectively utilizing the surplus capacity of the heating capacity, the simultaneous heating operation and hot water supply operation can be performed as much as possible.

Example 8. In each of the above embodiments, the heat pump type cooling and heating apparatus including the main refrigerant circuit and the hot water supply unit having the hot water supply heat exchanger for exchanging heat between the refrigerant of the main refrigerant circuit and the circulating water to the hot water tank has been described. As shown in FIG. 1, a reheating unit having a reheating heat exchanger for exchanging heat between the refrigerant of the main refrigerant circuit and the circulating water to the bath is provided outside the hot water supply unit, and the reheating unit is the above-mentioned heating unit. The same effect can be obtained by controlling in exactly the same way as the hot water supply unit. As a result, it is possible to perform a simultaneous heating and hot-water heating simultaneous operation.

Example 9. Further, instead of the hot water supply unit, a reheating unit, that is, even in a heat pump type cooling and heating device provided only with a main refrigerant circuit and a reheating unit, by controlling the reheating unit in exactly the same manner as the hot water supply unit described above. The same effect can be obtained.

[0093]

As described above, according to the first aspect of the present invention, the predetermined relationship is obtained from the deviation between the detected high pressure and the target high pressure and the deviation between the detected low pressure and the target low pressure for each operation mode. The formula is used to calculate the capacity change amount of the compressor and the air flow change amount of the outdoor fan, and the compressor is controlled by the calculated capacity change amount, and the outdoor fan is controlled by the air flow change amount. A refrigeration cycle is realized, and there is an effect that a heat pump type cooling and heating device can be obtained that can constantly operate the compressor with high efficiency according to changes in load and operation mode.

According to the second aspect of the invention, the deviation between the detected high pressure P _d and the target high pressure P _dm is ΔP _d , and the detected low pressure P _s and the target low pressure P _sm are different for each operation mode. Assuming that the deviation is ΔP _s , the following equation ΔQ _comp = (d · ΔP _d −b · ΔP _s ) / (a · d−b ·
c) ΔV _out = (− c · ΔP _d + a · ΔP _s ) / (a · d−b
From · c), to calculate the air volume change amount [Delta] V _out of capacity change amount Delta] Q _comp an outdoor fan of the compressor, the compressor These calculated capacity change amount Delta] Q _comp, an outdoor fan by airflow change amount [Delta] V _out Since the heat pumps are configured to control each other, the optimum values of the coefficients a, b, c, and d are obtained in advance by experiments, etc., so that the heat pump can operate the compressor more finely and highly efficiently according to changes in load and operation mode. There is an effect that the type air conditioner is obtained.

According to the third aspect of the invention, the current subcooling at the outlet of the hot water heat exchanger calculated from the high pressure which is the refrigerant pressure at the inlet of the hot water heat exchanger and the refrigerant temperature at the outlet of the hot water heat exchanger. The refrigerant amount from the main refrigerant circuit to the hot water supply heat exchanger is controlled so that the degree becomes a set degree of supercooling at the outlet of the hot water supply heat exchanger according to the hot water temperature of the hot water storage tank. According to this configuration, the circulating water flow rate of the hot water supply heat exchanger is controlled so that the temperature of the hot water supply water piping on the outlet side of the hot water supply heat exchanger is maintained at a predetermined constant value, so the heating capacity is independent of the hot water temperature in the hot water storage tank. Therefore, there is an effect that a heat pump type cooling and heating device capable of simultaneously performing heating and hot water supply can be obtained without giving discomfort to a heating user.

According to the fifth aspect of the present invention, when there is an operation request for the hot water supply unit during the heating operation, the difference between the maximum operating frequency of the compressor and the actual operating frequency is calculated, and the difference frequency is the hot water temperature of the hot water storage tank. Since the hot water supply unit is configured to start operation only when the frequency is higher than a predetermined frequency, the hot water supply operation is performed by the surplus capacity during the heating operation, and the heating and hot water supply does not cause discomfort to the heating user. There is an effect that a heat pump type air conditioner capable of simultaneous operation can be obtained.

According to the sixth aspect of the present invention, when a heating operation request is issued during operation of the hot water supply unit, the operation of the hot water supply unit is temporarily stopped to start the heating operation, and then the maximum operating frequency of the compressor and the actual operation are performed. The difference in frequency is calculated and the operation of the hot water supply unit is restarted only when the difference frequency is equal to or higher than the predetermined frequency according to the hot water temperature of the hot water storage tank. Therefore, there is an effect that the heat pump type cooling and heating device that can perform the optimum hot water supply operation without causing discomfort to the heating user can be obtained.

According to the seventh aspect of the present invention, when the heating load increases during the simultaneous heating and hot water supply operation and the discharge side refrigerant pressure cannot be controlled to the target high pressure, the hot water supply unit is temporarily stopped and then the compression is performed. The difference between the maximum operating frequency of the machine and the actual operating frequency is calculated, and the operation of the hot water supply unit is restarted only when the difference frequency is equal to or higher than the predetermined frequency according to the hot water temperature of the hot water storage tank. There is an effect that a heat pump type cooling and heating device can be obtained which gives priority to the operation and can perform the optimum hot water supply operation according to the hot water temperature without causing a discomfort to the heating user.

According to the eighth aspect of the present invention, the heating operation is switched to the simultaneous heating and hot water supply simultaneous operation, or the heating load suddenly increases during the simultaneous heating and hot water supply simultaneous operation, and the discharge side refrigerant pressure becomes the target high pressure. When it becomes impossible to control, the target high pressure is once lowered to a predetermined value, and when it cannot be controlled to the target high pressure, the operation of the hot water supply unit is stopped so that the heating user does not feel a big discomfort. There is an effect that a surplus capacity of the heating capacity is effectively used while ensuring the heating capacity, and a heat pump type cooling / heating device capable of performing simultaneous heating and hot water supply operation as much as possible is obtained.

According to the invention described in claim 9, in the invention described in each of the above claims, a reheating unit is provided instead of the hot water supply unit or in addition to the hot water supply unit, and the same control as the hot water supply unit is added. Since it is performed for the heating unit, the same effect as the above-mentioned simultaneous heating and hot water supply operation can be obtained.
There is an effect that can be obtained by simultaneous heating and hot water heating or hot water supply and hot water heating.

[Brief description of drawings]

FIG. 1 is a configuration diagram showing a first embodiment of the present invention.

FIG. 2 is a configuration diagram illustrating a cooling operation according to the first embodiment.

FIG. 3 is a configuration diagram illustrating simultaneous heating and hot water supply operation according to the first embodiment.

FIG. 4 is a control block diagram according to the first embodiment.

FIG. 5 is a configuration diagram showing a second embodiment of the present invention.

FIG. 6 is a flowchart illustrating the operation of the second embodiment.

FIG. 7 is a time chart for explaining the operation of the second embodiment.

FIG. 8 is a configuration diagram showing a third embodiment of the present invention.

FIG. 9 is a flowchart illustrating the operation of the third embodiment of the present invention.

FIG. 10 is a configuration diagram showing a fourth embodiment of the present invention.

FIG. 11 is a flowchart illustrating the operation of the fourth embodiment of the present invention.

FIG. 12 is a configuration diagram showing a fifth embodiment of the present invention.

FIG. 13 is a flowchart illustrating the operation of the fifth embodiment of the present invention.

FIG. 14 is a configuration diagram showing a sixth embodiment of the present invention.

FIG. 15 is a flowchart illustrating the operation of the sixth embodiment of the present invention.

FIG. 16 is a configuration diagram showing a seventh embodiment of the present invention.

FIG. 17 is a flowchart illustrating the operation of the seventh embodiment of the present invention.

FIG. 18 is a configuration diagram of a heat pump type cooling and heating apparatus including a conventional hot water supply unit.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Compressor 3 Indoor heat exchanger 7 Outdoor heat exchanger 8 Accumulator 9a Refrigerant piping 9b Refrigerant piping 9c Refrigerant piping 10 Main refrigerant circuit 12 Outdoor fan 13 Hot water tank 14 Hot water heat exchanger 20 Hot water Water flow control valve 21 Hot water supply unit 25 High pressure Pressure detector 26 Low pressure pressure detector 27 Reheating unit 28 Reheating heat exchanger 30 Bathtub 32a Refrigerant amount control valve (pressure reducing device) 33 Hot water temperature detector 34 Outlet side refrigerant temperature detector 35 Hot water supply pipe outlet temperature detector 36 Hot water supply unit on / off means 37 Heating on / off means 40 Controller 41 Calculation means 42 Compressive function force change amount calculation means 44 Compressor control means 45 Outdoor fan control means 50 Controller 51 Set supercooling degree determining means 52 Current supercooling degree calculation Means 53 Hot water supply heat exchanger Refrigerant amount control means 60 Controller 61 Hot water supply water flow rate control valve control means 70 Control Unit 71 Compressor operation frequency control means 72 Difference frequency calculation means 73 Hot water supply unit operation start control means 74 Hot water supply / heating switching means 75 Hot water supply unit operation restart control means 76 Hot water supply unit operation suspension control means 80 Controller 81 Target high pressure reduction means 82 Hot water supply unit operation suspension control means

 ─────────────────────────────────────────────────── ─── Continuation of front page (72) Inventor Yoshiaki Tanimura 3-18-1, Ogashi, Shizuoka City Mitsubishi Electric Co., Ltd. Living Environment Engineering Center (72) Inventor Tetsuji Okada 3-18-1, Oka, Shizuoka Mitsubishi Electric Environment Co., Ltd. Living Environment Engineering Control Center

Claims (9)

[Claims] 1. A main refrigerant circuit in which a compressor, an accumulator, an indoor heat exchanger, an outdoor heat exchanger, and a pressure reducing device are connected by a refrigerant pipe, and a refrigerant in the main refrigerant circuit and circulating water to a hot water tank are heat-exchanged. In a heat pump type cooling and heating apparatus having a hot water supply unit having a hot water supply heat exchanger, a high pressure pressure detector for detecting the discharge side refrigerant pressure of the compressor, a low pressure pressure detector for detecting the suction side refrigerant pressure, and Based on the deviation between the high pressure detected by the high pressure detector and the target high pressure and the deviation between the low pressure detected by the low pressure detector and the target low pressure, the capacity change amount of the compressor and the outdoor heat exchange are determined by a predetermined relational expression. Calculating means for calculating the air flow rate change amount of the outdoor fan for cooling the device, compressor control means for controlling the compressor according to the capacity change amount of the compressor calculated by the calculating means, and the computing hand And a controller having an outdoor fan control means for controlling the outdoor fan according to the amount of change in the air flow of the outdoor fan calculated by the step. 2. The predetermined relational expression of the calculating means is as follows: the detected high pressure is P _d , the target high pressure is P _dm , the detected low pressure is P _s , the target low pressure is P _sm , and their deviation is ΔP _d = P _dm. -P _d , Δ
When P _s = P _sm −P _s , the compressor capacity change amount ΔQ _comp
And the amount of air flow change ΔV _out of the outdoor fan can be expressed by the following determinant By solving the following equation ΔQ _comp = (d · ΔP _d −b · ΔP _s ) / (a · d−b ·
c) ΔV _out = (− c · ΔP _d + a · ΔP _s ) / (a · d−b
The heat pump type cooling and heating apparatus according to claim 1, wherein the expression is obtained in (c). 3. A main refrigerant circuit in which a compressor, an accumulator, an indoor heat exchanger, an outdoor heat exchanger, and a pressure reducing device are connected by a refrigerant pipe, a refrigerant amount control valve, and an amount corresponding to the opening / closing degree of the refrigerant amount control valve. The refrigerant is supplied from the main refrigerant circuit, and a heat pump type heating and cooling device comprising a hot water supply unit having a hot water supply heat exchanger for exchanging heat between the refrigerant and the circulating water to the hot water storage tank, the inlet of the hot water supply heat exchanger High-pressure pressure detector for detecting the side refrigerant pressure, outlet-side refrigerant temperature detector for detecting the outlet-side refrigerant temperature of the hot water heat exchanger, hot-water temperature detector for the hot water tank, and detection of the hot-water temperature detector Set subcooling degree determining means for determining the set subcooling degree at the outlet of the hot water heat exchanger according to the temperature, from the detected high pressure of the high pressure detector and the detected temperature of the outlet side refrigerant temperature detector, the outlet of the hot water heat exchanger Calculate the current degree of supercooling of The current subcooling degree calculating means, and the refrigerant so that the current subcooling degree at the outlet of the hot water heat exchanger calculated by the current subcooling degree calculating means becomes the set subcooling degree determined by the set subcooling degree determining means. A heat pump type cooling and heating apparatus, comprising: a hot water supply heat exchanger for controlling a quantity control valve; and a controller having a refrigerant quantity control means. 4. A main refrigerant circuit in which a compressor, an accumulator, an indoor heat exchanger, an outdoor heat exchanger, and a pressure reducing device are connected by a refrigerant pipe, and a refrigerant in the main refrigerant circuit and circulating water to a hot water tank are heat-exchanged. In a heat pump type cooling and heating device having a hot water supply unit having a hot water supply heat exchanger, a hot water supply water flow control valve for controlling the circulating water flow rate of the hot water supply heat exchanger and a hot water supply pipe temperature at the outlet side of the hot water heat exchanger Control having hot water supply water outlet temperature detector for detecting the temperature, and hot water supply water flow rate control valve control means for controlling the hot water supply water flow rate control valve so that the detected temperature of the hot water supply water outlet temperature detector becomes a predetermined constant value. A heat pump type cooling and heating device characterized by being provided with. 5. A hot water temperature detector is provided in the hot water storage tank, the operating frequency of the compressor is made variable, and the capacity of the compressor is controlled by changing this operating frequency. A difference frequency calculation means for calculating the difference between the maximum operation frequency and the actual operation frequency of the compressor according to the operation request of the hot water supply unit during heating operation, and the difference frequency calculated by this means is detected by the hot water temperature detector. The heat pump type cooling and heating apparatus according to claim 1 or 2, further comprising: an operation start control means for the hot water supply unit that starts the operation of the hot water supply unit only when the temperature is equal to or higher than a predetermined value according to the temperature. 6. A hot water temperature detector is provided in the hot water storage tank, the operating frequency of the compressor is made variable, and the capacity of the compressor is controlled by changing this operating frequency, and the controller operates the hot water supply unit. Hot water supply / heating switching means that suspends the operation of the hot water supply unit and starts the heating operation in response to the heating operation request of the main refrigerant circuit at the time, and the maximum operating frequency of the compressor and the actual operation during the heating operation after switching by this means. A difference frequency calculation means for calculating a difference in operating frequency, and a hot water supply unit for restarting the operation of the hot water supply unit only when the difference frequency calculated by this means is equal to or higher than a predetermined value according to the detected temperature of the hot water temperature detector. The heat pump type cooling and heating apparatus according to claim 1 or 2, further comprising an operation restart control means. 7. A hot water temperature detector is provided in the hot water storage tank, the operating frequency of the compressor is made variable, and the capacity of the compressor is controlled by changing this operating frequency. Hot water supply that suspends the operation of the hot water supply unit when the discharge side refrigerant pressure cannot be controlled to the target high pressure even with the maximum capacity of the compressor due to an increase in the heating load during the simultaneous operation of the heating operation and the hot water supply unit operation. The unit operation suspension control means, the difference frequency calculation means for calculating the difference between the maximum operation frequency and the actual operation frequency of the compressor during the heating operation after the operation of the hot water supply unit is stopped by this means, and the difference frequency calculated by this means A hot water supply unit restart control means for restarting the operation of the hot water supply unit only when the temperature is equal to or higher than a predetermined value according to the detected temperature of the hot water temperature detector is provided. The heat pump type cooling and heating device according to claim 1 or 2. 8. The target high pressure when the controller cannot control the discharge side refrigerant pressure to the target high pressure even at the maximum capacity of the compressor during the simultaneous operation of the heating operation of the main refrigerant circuit and the operation of the hot water supply unit. Is provided with a target high pressure reducing means for reducing the discharge pressure to a predetermined value, and a hot water supply unit suspension control means for suspending the operation of the hot water supply unit when the discharge side refrigerant pressure cannot be controlled even by the target high pressure reduced by this means. The heat pump type cooling and heating apparatus according to claim 1 or 2, characterized in that. 9. A hot water heating unit is provided in place of or in addition to the hot water supply unit, the hot water supply heat exchanger is a hot water heat exchanger, and the hot water storage tank is a bathtub. The heat pump type air conditioner described in.