JP3430639B2 - Heat pump system - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat pump system.

[0002]

2. Description of the Related Art Conventionally, as this type of heat pump system, for example, there is one described in Japanese Patent Application Laid-Open No. 1-234763. FIG. 32 is a configuration diagram of a conventional heat pump system described in the above publication. As shown in the figure, the compressor 1, the four-way valve 33, the outdoor heat exchanger 16, the indoor heat exchanger 6, and the reheating heat exchanger 13 for heating the bath water.
A reheating unit 12 having a pump 14 and a reheating unit 12 having a pump 14 are connected in parallel to each other, and a hot water supply unit 7 having a hot water supply heat exchanger 8 for heating hot water in the hot water storage tank 10 is provided. Next, the operating state of the heat pump system having the above configuration will be described. Here, the description will be given only to the additional heating operation. The high-temperature and high-pressure refrigerant gas discharged from the compressor 1 is reheated through the four-way valve 33 and the gas pipe 3
Pass 3 Here, heat is exchanged between the water circulated by the pump 14 from the bathtub 15 and the refrigerant, and the heated water returns to the bathtub 15 again. The refrigerant after the heat exchange becomes a high-pressure liquid and becomes a low-pressure two-phase refrigerant by passing through the expansion valve 32c, and then exchanges heat with the outside air while passing through the outdoor heat exchanger 16 to become a low-pressure gas refrigerant. And four-way valve 3 again
3. Return to the suction side of the compressor 1 via the accumulator 2.

[0003]

As described above, in the conventional heat pump system, when performing the reheating operation, there is no method other than collecting heat from the outside air by using the outdoor heat exchanger as the evaporator. Above, when the outside air becomes low,
There was a problem that the efficiency was lowered and the boiling speed was slowed down.

The present invention has been made in order to solve the above problems, and in the reheating operation, not only the heat is taken from the outside air but also the high temperature water in the hot water storage tank is used.
It is an object of the present invention to provide a heat pump system capable of collecting heat without abnormal pressure rise and enabling high-speed boiling at high efficiency. Another object of the present invention is to provide a heat pump system capable of preventing an abnormal pressure rise even when performing heat-up operation, hot water supply operation, or bathroom drying operation by collecting heat from high-temperature outside air such as in summer. Further, another object of the present invention is to provide a heat pump system that enables the additional heating operation by utilizing the exhaust heat of the cooling according to the situation and enables comfortable air conditioning without giving the cooling user an unpleasant feeling. In addition, various operations such as heating operation, cooling operation, hot water supply operation, additional heating operation, cooling exhaust heat utilization operation, hot water heat utilization additional heating operation, bathtub exhaust heat utilization operation, etc. can be easily switched by opening and closing the on-off valve to achieve high efficiency. It is possible to boil at high speed,
It is an object of the present invention to provide a heat pump system that enables effective use of energy. Another object of the present invention is to provide a heat pump system that is not affected by the outside temperature or prevents the outside temperature from being adversely affected.

[0005]

In a heat pump system according to the present invention, a compressor and an indoor heat exchanger are connected by a gas pipe, and the indoor heat exchanger and the outdoor heat exchanger are connected via a flow control valve to a liquid pipe. In the heat pump system in which at least one of cooling and heating can be operated, the compressor is discharged from the compressor by connecting the outdoor heat exchanger and the compressor with a low pressure gas pipe to form a refrigeration cycle. A heat-up heat exchanger having one end connected to the gas pipe and the other end connected to the liquid pipe, which heats the circulating water to the bath by exchanging heat with the refrigerant, and the additional heat It is connected to a heat exchanger via the liquid pipe and the other end is connected to the low-pressure gas pipe, and exchanges heat between the refrigerant and high temperature water stored in a hot water storage tank and circulated by a hot water supply pump. Hot water heat And a refrigerant discharged from the compressor is condensed in the reheating heat exchanger to become a liquid refrigerant, and then evaporated in the hot water heat exchanger to become a gas refrigerant and circulates to the compressor. As a result, the reheating operation is performed using the heat of the high-temperature water stored in the hot water storage tank.

In the heat pump system according to the present invention, the pressure detecting means for detecting the pressure of the refrigerant in the refrigerant system for circulating the refrigerant and the heat exchange amount of the hot water supply heat exchanger are adjusted to adjust the refrigerant during the reheating operation. And a heat exchange amount adjusting means for reducing the pressure.

Further, in the heat pump system according to the present invention, the hot water supply pump in the hot water supply unit is provided with the rotation speed control means for detecting the pressure of the refrigerant and controlling the rotation speed, thereby changing the circulating amount of water. Controls the amount of heat exchange in the hot water supply heat exchanger.

Further, in the heat pump system according to the present invention, a bypass passage via an on-off valve is provided between the inlet side water pipe and the outlet side water pipe of the hot water supply heat exchanger in the hot water supply unit so that the pressure of the refrigerant is When the amount of heat exchange in the hot water supply heat exchanger is detected and detected, the amount of heat exchange is controlled by bypassing water.

Further, in the heat pump system according to the present invention, a bypass passage via a water flow control valve is provided between the inlet side water pipe and the outlet side water pipe of the hot water supply heat exchanger in the hot water supply unit, and When the pressure is detected and the heat exchange amount in the hot water supply heat exchanger is too large, an appropriate amount of water is bypassed to control the heat exchange amount.

Further, the heat pump system according to the present invention is provided with the outside air temperature detecting means and the starting pressure adjusting means, and performs at least one of hot water supply operation and reheating operation, in which case the outdoor heat exchanger is evaporated. In addition, the starting pressure adjusting means adjusts the starting pressure according to the temperature detected by the outside air temperature detecting means.

Further, in the heat pump system according to the present invention, the frequency of the compressor at the start of operation is changed according to the outside air temperature to adjust the pressure at the start.

Further, the heat pump system according to the present invention adjusts the pressure at startup by changing the number of rotations of the outdoor fan of the outdoor heat exchanger at the start of operation according to the outside air temperature.

Further, in the heat pump system according to the present invention, the compressor and the indoor heat exchanger are connected by a gas pipe, and the indoor heat exchanger and the outdoor heat exchanger are connected by a liquid pipe through a flow control valve, The outdoor heat exchanger and the compressor are connected by a low-pressure gas pipe to form a refrigeration cycle in which a refrigerant is circulated, and in at least a heat pump system capable of operating either heating or cooling, the refrigerant and heat discharged from the compressor To replace and heat the circulating water to the bath, a reheating heat exchanger having one end connected to the gas pipe and the other end connected to the liquid pipe provided in the reheating unit, and the reheating heat exchanger. Heat exchange for hot water supply, which is connected through the liquid pipe and has the other end connected to the low-pressure gas pipe, and exchanges heat between the refrigerant and high temperature water stored in a hot water storage tank and circulated by a hot water supply pump. A vessel, Pressure detecting means for detecting the pressure of the refrigerant in the refrigerant system for circulating the refrigerant, and dividing the hot water supply heat exchanger, the length of the shorter hot water supply heat exchanger, the longer hot water supply heat exchange 1/5 or less of the water heater, the shorter hot water supply heat exchanger is placed on the liquid pipe side, the longer hot water supply heat exchanger is connected to the gas pipe side, and the outlet side refrigerant of the shorter hot water supply heat exchanger Connect the piping to the inlet side refrigerant piping and the outlet side refrigerant piping of the longer hot water supply heat exchanger via the two-way valve,
The pressure detecting means detects the pressure of the refrigerant to control the amount of heat exchange in the hot water supply heat exchanger.

In the heat pump system according to the present invention, the compressor and the indoor heat exchanger are connected by a gas pipe, and the indoor heat exchanger and the outdoor heat exchanger are connected by a liquid pipe via a flow control valve. The outdoor heat exchanger and the compressor are connected by a low-pressure gas pipe to form a refrigeration cycle in which a refrigerant is circulated, and in at least a heat pump system capable of operating either heating or cooling, the refrigerant and heat discharged from the compressor Exchanging and heating the circulating water to the bath, a reheating heat exchanger having one end connected to the gas pipe and the other end connected to the liquid pipe provided in the reheating unit, and the gas in the reheating unit. A bathroom drying heat exchanger of a bathroom drying unit connected via a pipe is provided, and a part of high pressure refrigerant gas from the compressor is bypassed to the indoor heat exchanger or the outdoor heat exchanger to perform bathroom drying operation. .

Further, the heat pump system according to the present invention comprises the outside air temperature detecting means, and the opening degree of the refrigerant flow rate control valve on the indoor heat exchanger side is changed according to the outside air temperature detected by the outside air temperature detecting means to change the indoor heat exchange. High-pressure refrigerant gas from the compressor is bypassed to the heater to perform the bathroom drying operation.

[0016]

[0017]

[0018]

In the heat pump system according to the present invention, the compressor and the indoor heat exchanger are connected by a gas pipe, and the indoor heat exchanger and the outdoor heat exchanger are connected by a liquid pipe via a flow control valve, The outdoor heat exchanger and the compressor are connected by a low-pressure gas pipe to form a refrigeration cycle in which a refrigerant is circulated, and in at least a heat pump system capable of operating either heating or cooling, the refrigerant and heat discharged from the compressor It is equipped with a reheating heat exchanger having one end connected to the gas pipe and the other end connected to the liquid pipe, which is exchanged and heats the circulating water to the bathtub, and performs cooling operation. When a reheating operation command is received, if the compressor is operating at a frequency above the sufficient reheating capacity, cooling exhaust heat reheating operation is performed, and the compressor can ensure sufficient reheating capacity. Below frequency In case of being operated is preferentially the reheating operation, performing reheating isolated operation stop cooling operation.

[0020]

The heat pump system according to the present invention is capable of collecting heat from the high temperature water in the hot water storage tank during the reheating operation, and realizes high efficiency and high speed boiling.

Further, the heat pump system according to the present invention detects the pressure of the refrigerant and adjusts the amount of heat exchange in the hot water supply heat exchanger when collecting heat from the hot water storage tank and performing the reheating operation,
Prevents abnormal pressure rise.

Further, the heat pump system according to the present invention detects the pressure of the refrigerant when the heat is collected from the hot water storage tank to perform the reheating operation, and the rotation control means controls the rotation speed of the oil supply pump to circulate the water. By varying the amount, the amount of heat exchange in the hot water supply heat exchanger is adjusted to prevent abnormal pressure rise.

Further, the heat pump system according to the present invention detects the pressure of the refrigerant and opens the on-off valve in the bypass passage of the hot water circulating water to reduce the amount of circulating water and reduce the amount of heat exchange in the hot water heat exchanger. Adjust to prevent abnormal pressure rise.

Further, the heat pump system according to the present invention detects the pressure of the refrigerant and controls the opening degree of the water flow control valve in the bypass passage of the hot water supply circulating water to adjust the circulating water amount,
Adjust the amount of heat exchange in the hot water heat exchanger to prevent abnormal pressure rise.

Further, in the heat pump system according to the present invention, the starting pressure is adjusted by the starting pressure adjusting means in accordance with the outside temperature in the operation mode in which the outdoor unit is the evaporator such as the hot water supply operation, the additional heating operation, and the drying operation. As a result, it is possible to prevent an abnormal stop due to a high voltage rise at startup.

In the heat pump system according to the present invention, in the operation mode in which the outdoor unit is the evaporator, such as hot water supply operation, reheating operation, and drying operation, the initial compressor frequency at the start of operation is changed depending on the outside temperature, and the startup is performed. It is possible to prevent an abnormal stop due to an increase in high pressure.

In the heat pump system according to the present invention, in the operation mode in which the outdoor unit is the evaporator such as hot water supply operation, reheating operation, and drying operation, the initial outdoor fan rotation speed at the start of operation is changed depending on the outside air temperature to stand up. It is possible to prevent an abnormal stop due to a high pressure rise at the time of raising.

In the heat pump system according to the present invention, the length of the hot water heat exchanger is shortened by detecting the pressure of the refrigerant and opening / closing the bypass opening / closing valve of the hot water heat exchanger. Adjust the amount of heat exchange at to prevent abnormal pressure rise.

Further, in the heat pump system according to the present invention, during the bathroom drying operation, a part of the high pressure refrigerant gas from the compressor is bypassed to the indoor heat exchanger or the outdoor heat exchanger to release a part of the condensation heat, Prevent an abnormal rise in.

Further, in the heat pump system according to the present invention, in the bathroom drying operation, the opening degree of the refrigerant flow control valve on the indoor heat exchanger side is changed according to the outside air temperature so that the indoor heat exchanger bypasses an appropriate amount of high pressure refrigerant. Part of the condensation heat is released to the indoor heat exchanger to prevent abnormal high pressure rise.

[0031]

[0032]

[0033]

In addition, in the heat pump system according to the present invention, when the reheating operation command is received during the cooling operation, when the compressor is operated at a frequency higher than the sufficient reheating capacity, When performing the cooling exhaust heat reheating operation, if the compressor is operating at a frequency lower than the frequency that can sufficiently secure the reheating capacity, priority is given to the reheating operation,
By stopping the cooling operation and performing additional heating alone,
It is possible to secure sufficient reheating ability.

[0035]

【Example】

Example 1. FIG. 1 shows the configuration of the first embodiment. In the figure,
1 is a compressor, 2 is an accumulator, 3 is a high pressure gas pipe,
4 is a low pressure gas pipe, 5 is a liquid pipe, 6 is an indoor heat exchanger, 7 is a hot water supply unit, 8 is a hot water heat exchanger, 9 is a hot water pump, 10
Is a hot water tank, 11 is a heater for heating, 12 is a reheating unit, 13 is a reheating heat exchanger, 14 is a reheating pump, 15
Is a bathtub, 16 is an outdoor heat exchanger, 17 is an outlet side water pipe of the hot water heat exchanger, 18 is an inlet side water pipe of the hot water heat exchanger, 1
9 is a hot water supply pipe, 20 is a water supply pipe, 21 is an outdoor fan, 3
1a, 31b, 31c, 31d, 31e, 31f, 31
g and 31h are two-way valves, and 32a, 32b and 32c are refrigerant flow control valves. Next, the operation of the heat pump system of the present invention will be described.

(1) Heating operation A description will be given with reference to FIG. The high-temperature and high-pressure refrigerant gas discharged from the compressor 1 passes through the gas pipe 3 and the indoor heat exchanger 6 via the two-way valve 31a. In the indoor heat exchanger 6, the refrigerant becomes a high-pressure liquid refrigerant while heating the air by exchanging heat with the air, and flows out from the indoor heat exchanger 6. The liquid refrigerant that has flowed out becomes a low-pressure two-phase refrigerant through the refrigerant flow control valve 32a, and after flowing through the liquid pipe 5, flows into the outdoor heat exchanger 16. Here, the low-pressure two-phase refrigerant evaporates by exchanging heat with the outside air, becomes a low-pressure refrigerant gas, and flows out from the outdoor heat exchanger 16. The low-pressure refrigerant gas that has flowed out returns to the suction side of the compressor 1 via the two-way valve 31h, the low-pressure gas pipe 4, and the accumulator 2.

(2) Cooling operation The operation will be described with reference to FIG. The high-temperature and high-pressure refrigerant gas discharged from the compressor 1 passes through the gas pipe 3 and the outdoor heat exchanger 16 via the two-way valve 31g. In the outdoor heat exchanger 6, the refrigerant becomes a high-pressure liquid refrigerant by exchanging heat with the outside air, and flows out from the outdoor heat exchanger 16. The liquid refrigerant that has flowed out passes through the liquid pipe 5, passes through the refrigerant flow control valve 32a, becomes a low-pressure two-phase refrigerant, and flows into the indoor heat exchanger 6. Here, the low-pressure two-phase refrigerant exchanges heat with air to cool the air, and the refrigerant evaporates into a low-pressure refrigerant gas, which flows out from the indoor heat exchanger 6. 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 low-pressure gas pipe 4, and the accumulator 2.

(3) Hot water supply operation The operation will be described with reference to FIG. The high-temperature high-pressure refrigerant gas discharged from the compressor 1 passes through the gas pipe 3 and the hot water heat exchanger 8 via the two-way valve 31c. On the other hand, the water in the hot water storage tank 10 is sucked from the lower part of the hot water storage tank 10 by the hot water supply pump 9, and flows from the inlet side water pipe 18 of the hot water supply heat exchanger into the hot water supply heat exchanger 8 having a double pipe structure. Here, the refrigerant becomes a high-pressure liquid refrigerant while heating the circulating water by exchanging heat with the circulating water, and flows out from the hot water supply heat exchanger 8. On the other hand, the heated circulating water returns from the outlet side water pipe 17 of the hot water supply heat exchanger 8 to the upper part of the hot water storage tank 10. The high-pressure liquid refrigerant flowing out of the hot water supply heat exchanger 8 passes through the refrigerant flow control valve 32b. As a result, it becomes a low-pressure two-phase refrigerant and flows into the outdoor heat exchanger 16 through the liquid pipe 5. Here, the low-pressure two-phase refrigerant becomes a low-pressure gas refrigerant by exchanging heat with the outside air, and returns to the suction side of the compressor 1 via the two-way valve 31h, the low-pressure gas pipe 4, and the accumulator 2. Further, if necessary, the heater 11 is used to further raise the temperature.

(4) Reheating operation will be described with reference to FIG. The high-temperature and high-pressure refrigerant gas discharged from the compressor 1 passes from the gas pipe 3 through the reheating heat exchanger 13 via the two-way valve 31e. On the other hand, the water in the bathtub 15 is sucked from the lower part of the bathtub 15 by the reheating pump 14 and flows into the reheating heat exchanger 13 having a double pipe structure. Here, the refrigerant becomes a high-pressure liquid refrigerant while heating the circulating water by exchanging heat with the circulating water, and the reheating heat exchanger 13
More outflow. On the other hand, the heated circulating water returns to the bathtub 15. The high-pressure liquid refrigerant that has flowed out of the reheating heat exchanger 13 becomes a low-pressure two-phase refrigerant by passing through the refrigerant flow control valve 32c, and flows into the outdoor heat exchanger 16 through the liquid pipe 5.
Here, the low-pressure two-phase refrigerant becomes a low-pressure gas refrigerant by exchanging heat with the outside air, and returns to the suction side of the compressor 1 via the two-way valve 31h, the low-pressure gas pipe 4, and the accumulator 2.

(5) Hot-water supply operation using cooling waste heat will be described with reference to FIG. The high-temperature high-pressure refrigerant gas discharged from the compressor 1 passes through the gas pipe 3 and the hot water heat exchanger 8 via the two-way valve 31c. On the other hand, the water in the hot water storage tank 10 is sucked from the lower part of the hot water storage tank 10 by the hot water supply pump 9, and flows from the inlet side water pipe 18 of the hot water supply heat exchanger into the hot water supply heat exchanger 8 having a double pipe structure. Here, the refrigerant becomes a high-pressure liquid refrigerant while heating the circulating water by exchanging heat with the circulating water, and flows out from the hot water supply heat exchanger 8. On the other hand, the heated circulating water returns to the upper part of the hot water storage tank 10 through the outlet side water pipe 17 of the hot water supply heat exchanger 8. The high-pressure liquid refrigerant flowing out of the hot water supply heat exchanger 8 becomes a low-pressure two-phase refrigerant by passing through the refrigerant flow control valve 32b, and then flows into the indoor heat exchanger 6 through the liquid pipe 5 and the refrigerant flow control valve 32a. To do. here,
The low-pressure two-phase refrigerant cools the air by exchanging heat with the air. The refrigerant becomes a low-pressure gas refrigerant and returns to the suction side of the compressor 1 via the two-way valve 31b, the low-pressure gas pipe 4, and the accumulator 2.

(6) Reheating operation using hot water supply heat will be described with reference to FIG. The high-temperature and high-pressure refrigerant gas discharged from the compressor 1 passes from the gas pipe 3 through the reheating heat exchanger 13 via the two-way valve 31e. On the other hand, the water in the bathtub 15 is sucked from the lower part of the bathtub 15 by the reheating pump 14 and flows into the reheating heat exchanger 13 having a double pipe structure. Here, the refrigerant becomes a high-pressure liquid refrigerant while heating the circulating water by exchanging heat with the circulating water, and the reheating heat exchanger 13
More outflow. On the other hand, the heated circulating water returns to the bathtub 15. The high-pressure liquid refrigerant flowing out of the reheating heat exchanger 13 becomes a low-pressure two-phase refrigerant by passing through the refrigerant flow control valve 32c, and has a double pipe structure via the liquid pipe 5 and the refrigerant flow control valve 32b. It flows into the hot water supply heat exchanger 8. On the other hand, the high temperature water in the hot water storage tank 10 is supplied from the lower portion of the hot water storage tank 10 to the hot water supply pump 9
Is sucked by and flows into the hot water supply heat exchanger 8 through the inlet water pipe 18 of the hot water supply heat exchanger. Here, the low-pressure two-phase refrigerant becomes a low-pressure gas refrigerant by exchanging heat with the circulating high-temperature water, and returns to the suction side of the compressor 1 via the two-way valve 31d, the low-pressure gas pipe 4, and the accumulator 2. The circulating high-temperature water returns to the upper part of the hot water storage tank 10 through the outlet side water pipe 17 of the hot water supply heat exchanger.

(7) Hot water supply operation using waste heat from bathtub The operation will be described with reference to FIG. The high-temperature high-pressure refrigerant gas discharged from the compressor 1 passes through the gas pipe 3 and the hot water heat exchanger 8 via the two-way valve 31c. On the other hand, the water in the hot water storage tank 10 is sucked from the lower part of the hot water storage tank 10 by the hot water supply pump 9, and flows from the inlet side water pipe 18 of the hot water supply heat exchanger into the hot water supply heat exchanger 8 having a double pipe structure. Here, the refrigerant becomes a high-pressure liquid refrigerant while heating the circulating water by exchanging heat with the circulating water, and flows out from the hot water supply heat exchanger 8. On the other hand, the heated circulating water returns to the upper part of the hot water storage tank 10 through the outlet side water pipe 17 of the hot water supply heat exchanger 8. The high-pressure liquid refrigerant flowing out of the hot water supply heat exchanger 8 becomes a low-pressure two-phase refrigerant by passing through the refrigerant flow control valve 32b, passes through the liquid pipe 5 and the refrigerant flow control valve 32c, and becomes a double pipe structure. It flows into the additional heating heat exchanger 13. On the other hand, the hot water in the bathtub 15 is sucked from the lower part of the bathtub 15 by the reheating pump 14 and flows into the reheating heat exchanger 13 having a double pipe structure. Here, the refrigerant becomes a low-pressure gas refrigerant by exchanging heat with the circulating hot water, and flows out from the reheating heat exchanger 13. On the other hand, the warm water returns to the bathtub 15. The low-pressure gas refrigerant flowing out of the reheating heat exchanger 13 returns to the suction side of the compressor 1 via the two-way valve 31f, the low-pressure gas pipe 4, and the accumulator 2.

As described above, in the present embodiment, since the hot-water supply heat can be used for the additional heating operation, high-speed and high-speed boiling can be realized without being affected by the outside temperature. Also, because the exhaust heat in the bathtub can be recovered and the hot water supply operation can be performed,
Effective use of energy is possible. Moreover, since the hot water supply operation can be performed by utilizing the exhaust heat at the time of cooling, the energy can be effectively used.

It is to be noted that FIG. 9 shows that high-speed boiling can be performed with higher efficiency when the additional heating operation is performed by using the hot water supply heat than when the heat is taken from the outdoor air. FIG. 9 shows the reheating performance by comparing the heating capacity by water temperature. As setting conditions, it is assumed that the hot water supply heat source is 85 ° C., the air heat source is 7 ° C., and the temperature is raised from 10 ° C. to 40 ° C. in FIG. An example of the boiling time is shown. The lower the water temperature, the greater the heating capacity in the case of the hot water supply heat source.

Example 2. 11 to 18 showing the second embodiment
11 corresponds to FIGS. 1 to 8 of the first embodiment, respectively.
Is a configuration diagram of the present heat pump system, FIG. 12 is a diagram showing a heating operation, FIG. 13 is a diagram showing a cooling operation, FIG. 14 is a diagram showing a hot water supply operation, FIG. 15 is a diagram showing a reheating operation, and FIG. FIG. 17 is a diagram showing a heat-utilizing hot water supply operation, FIG. 17 is a diagram showing a hot-water supply heat-utilizing additional heating operation, and FIG. In each drawing, the same parts and corresponding parts as those of the first embodiment are designated by the same reference numerals, and the configurations, operations and the like are the same, and thus detailed description thereof will be omitted. In each figure, the indoor heat exchanger 6, the hot water supply heat exchanger 8, the reheating heat exchanger 13, and the outdoor heat exchanger 16 are switched to the high pressure gas pipe 3 and the low pressure gas pipe 4 respectively in the first embodiment. Two-way valves, 31a, 31b, 31c, 31d, 31e, 31
The operation performed at f and 31g, 31h is performed by one three-way valve, 310a, 310b, 310c, 310d. Further, a check valve 330 is provided on the low-pressure gas pipe 4 side of the outdoor heat exchanger 16.

The operation as a heat pump system is as follows.
Basically, it is the same as the first embodiment, but in the case of the second embodiment, switching of the refrigerant flowing through each heat exchanger to the high pressure gas pipe and the low pressure gas pipe is performed by one three-way valve, respectively. ,
The number of actuators (two-way valve) to control decreases,
The circuit can be simplified. In addition, in the hot water supply heating additional heating operation of FIG. 17 and the bathtub waste heat utilization hot water supply operation of FIG. 18, the check valve 330 provided on the low pressure gas pipe 4 side of the outdoor heat exchanger 16 prevents outside air such as in the winter. When the temperature is low, the refrigerant flowing through the low-pressure gas pipe 4 flows into the outdoor heat exchanger 16 and is condensed, so that the low pressure is reduced and the effect of utilizing the heat from the hot water supply and the effect of utilizing the waste heat from the bathtub are prevented from being reduced.

Example 3. FIG. 19 shows the configuration of the third embodiment. In the figure, 1 is a compressor, 2 is an accumulator,
3 is a high pressure gas pipe, 4 is a low pressure gas pipe, 5 is a liquid pipe, 6 is an indoor heat exchanger, 7 is a hot water supply unit, 8 is a hot water supply heat exchanger, 9 is a hot water supply pump, 10 is a hot water storage tank, 11 is for heating Heater, 12
Is a reheating unit, 13 is a reheating heat exchanger, 14 is a reheating pump, 15 is a bathtub, 16 is an outdoor heat exchanger, 17 is an outlet side water pipe of the hot water heat exchanger, and 18 is a hot water heat exchanger. Inlet side water pipe, 19 is tap water pipe, 20 is water supply pipe, 31
a, 31b, 31c, 31d, 31e, 31f, 31
g and 31h are two-way valves, 32a, 32b and 32c are refrigerant flow rate control valves, and 40 is a hot water supply pump inverter which is a rotation speed control means for controlling the rotation speed of the hot water supply pump which constitutes the heat exchange amount adjusting means.

Next, the operation will be described. The operation of the heat pump system of the present invention will be described. In addition, here, only the hot-water supply heat-utilizing additional heating operation, which is particularly effective, will be described.

(1) Reheating operation using hot water supply heat will be described with reference to FIG. The high-temperature and high-pressure refrigerant gas discharged from the compressor 1 passes from the gas pipe 3 through the reheating heat exchanger 13 via the two-way valve 31e. On the other hand, the water in the bathtub 15 is sucked from the lower part of the bathtub 15 by the reheating pump 14 and flows into the reheating heat exchanger 13 having a double pipe structure. Here, the refrigerant becomes a high-pressure liquid refrigerant while heating the circulating water by exchanging heat with the circulating water, and the reheating heat exchanger 13
More outflow. On the other hand, the heated circulating water returns to the bathtub 15. The high-pressure liquid refrigerant flowing out of the reheating heat exchanger 13 becomes a low-pressure two-phase refrigerant by passing through the refrigerant flow control valve 32c, and has a double pipe structure via the liquid pipe 5 and the refrigerant flow control valve 32b. It flows into the hot water supply heat exchanger 8. On the other hand, the high temperature water in the hot water storage tank 10 is supplied from the lower portion of the hot water storage tank 10 to the hot water supply pump 9
Is sucked by and flows into the hot water supply heat exchanger 8 through the inlet water pipe 18 of the hot water supply heat exchanger. Here, the low-pressure two-phase refrigerant becomes a low-pressure gas refrigerant by exchanging heat with the circulating high-temperature water, and returns to the suction side of the compressor 1 via the two-way valve 31d, the low-pressure gas pipe 4, and the accumulator 2. The circulating high-temperature water returns to the upper part of the hot water storage tank 10 through the outlet side water pipe 17 of the hot water supply heat exchanger. The pressure of the refrigerant in the system is detected by a pressure sensor (not shown), and the rotation speed of the hot water supply pump 9 is changed by the hot water supply pump inverter 40 so that the refrigerant pressure in the system does not rise abnormally. The amount of circulating water can be changed to control the amount of heat exchange in the hot water supply heat exchanger 8.

As described above, in the present embodiment, the hot water supply pump inverter can be used to change the rotation speed of the hot water supply pump to change the circulating water amount and control the heat exchange amount in the hot water supply heat exchanger. In the usage reheating operation, there is an effect that the refrigerant pressure in the system can be prevented from rising abnormally even if heat is taken from the hot water.

The problem of the hot-water heating reheating operation is that the low-temperature rises and the compressor operation limit pressure is exceeded because heat is collected from the high-temperature hot-water supply heat. Therefore, it can be said that it is desirable to detect the low pressure. In any case, the pressure of the refrigerant may be monitored so as not to exceed the limit pressure. That is, it is necessary to prevent abnormal pressure and operate in an appropriate pressure range.

Example 4. FIG. 20 shows the configuration of the fourth embodiment. In the figure, 1 is a compressor, 2 is an accumulator,
3 is a high pressure gas pipe, 4 is a low pressure gas pipe, 5 is a liquid pipe, 6 is an indoor heat exchanger, 7 is a hot water supply unit, 8 is a hot water supply heat exchanger, 9 is a hot water supply pump, 10 is a hot water storage tank, 11 is for heating Heater, 12
Is a reheating unit, 13 is a reheating heat exchanger, 14 is a reheating pump, 15 is a bathtub, 16 is an outdoor heat exchanger, 17 is an outlet side water pipe of the hot water heat exchanger, and 18 is a hot water heat exchanger. Inlet side water pipe, 19 is tap water pipe, 20 is water supply pipe, 31
a, 31b, 31c, 31d, 31e, 31f, 31
g and 31h are two-way valves, 32a, 32b and 32c are refrigerant flow control valves, 41 is a throttle device for the circulating water bypass passage, and 42 is a two-way valve in the circulating water bypass passage. The 41 throttle device, 42 two-way valve and the bypass passage constitute heat exchange amount adjusting means.

Next, the operation will be described. The operation of the heat pump system of the present invention will be described. In addition, here, only the hot-water supply heat-utilizing additional heating operation, which is particularly effective, will be described.

(1) Reheating operation using hot water supply heat will be described with reference to FIG. The high-temperature and high-pressure refrigerant gas discharged from the compressor 1 passes from the gas pipe 3 through the reheating heat exchanger 13 via the two-way valve 31e. On the other hand, the water in the bathtub 15 is sucked from the lower part of the bathtub 15 by the reheating pump 14 and flows into the reheating heat exchanger 13 having a double pipe structure. Here, the refrigerant becomes a high-pressure liquid refrigerant while heating the circulating water by exchanging heat with the circulating water, and the reheating heat exchanger 13
More outflow. On the other hand, the heated circulating water returns to the bathtub 15. The high-pressure liquid refrigerant flowing out of the reheating heat exchanger 13 becomes a low-pressure two-phase refrigerant by passing through the refrigerant flow control valve 32c, and has a double pipe structure via the liquid pipe 5 and the refrigerant flow control valve 32b. It flows into the hot water supply heat exchanger 8. On the other hand, the high temperature water in the hot water storage tank 10 is supplied from the lower portion of the hot water storage tank 10 to the hot water supply pump 9
Is sucked by and flows into the hot water supply heat exchanger 8 through the inlet water pipe 18 of the hot water supply heat exchanger. Here, the low-pressure two-phase refrigerant becomes a low-pressure gas refrigerant by exchanging heat with the circulating high-temperature water, and returns to the suction side of the compressor 1 via the two-way valve 31d, the low-pressure gas pipe 4, and the accumulator 2. The circulating high-temperature water returns to the upper part of the hot water storage tank 10 through the outlet side water pipe 17 of the hot water supply heat exchanger. Note that the pressure of the refrigerant in the system is detected by a pressure sensor (not shown), and the two-way valve 41 in the bypass passage of the hot water supply circulating water is opened so that the refrigerant pressure in the system does not rise abnormally. By bypassing the circulating water, the circulating water flowing into the hot water supply heat exchanger 8 can be reduced and the amount of heat exchange in the hot water supply heat exchanger 8 can be controlled.

As described above, in this embodiment, the amount of circulating water can be reduced and the amount of heat exchange in the hot water supply heat exchange passage can be controlled by opening the two-way valve in the bypass passage of the hot water supply circulating water. Even if heat is taken from the hot water for hot water supply during the hot water supply hot water reheating operation, it is possible to prevent the refrigerant pressure in the system from rising abnormally.

Here, as the heat exchange amount adjusting means, the control of the hot water supply circulating water amount has been described. A flow chart relating to this control is shown in FIG. In addition, another method of this heat exchange amount adjusting means will be described below.

Example 5. FIG. 22 shows the configuration of the fifth embodiment. In the figure, 1 is a compressor, 2 is an accumulator,
3 is a high pressure gas pipe, 4 is a low pressure gas pipe, 5 is a liquid pipe, 6 is an indoor heat exchanger, 7 is a hot water supply unit, 8 is a hot water supply heat exchanger, 9 is a hot water supply pump, 10 is a hot water storage tank, 11 is for heating Heater, 12
Is a reheating unit, 13 is a reheating heat exchanger, 14 is a reheating pump, 15 is a bathtub, 16 is an outdoor heat exchanger, 17 is an outlet side water pipe of the hot water heat exchanger, and 18 is a hot water heat exchanger. Inlet side water pipe, 19 is tap water pipe, 20 is water supply pipe, 31
a, 31b, 31c, 31d, 31e, 31f, 31
g and 31h are two-way valves, 32a, 32b and 32c are refrigerant flow control valves, and 43 is a flow control valve of the circulating water bypass passage. The 43 flow rate control valve and the bypass passage constitute heat exchange amount adjusting means.

Next, the operation will be described. The operation of the heat pump type heating and cooling / hot water supply additional heating system of the present invention will be described. In addition, here, only the hot-water supply heat-utilizing additional heating operation, which is particularly effective, will be described.

(1) Reheating operation using hot water supply heat The operation will be described with reference to FIG. The high-temperature and high-pressure refrigerant gas discharged from the compressor 1 passes from the gas pipe 3 through the reheating heat exchanger 13 via the two-way valve 31e. On the other hand, the water in the bathtub 15 is sucked from the lower part of the bathtub 15 by the reheating pump 14 and flows into the reheating heat exchanger 13 having a double pipe structure. Here, the refrigerant becomes a high-pressure liquid refrigerant while heating the circulating water by exchanging heat with the circulating water, and the reheating heat exchanger 13
More outflow. On the other hand, the heated circulating water returns to the bathtub 15. The high-pressure liquid refrigerant flowing out of the reheating heat exchanger 13 becomes a low-pressure two-phase refrigerant by passing through the refrigerant flow control valve 32c, and has a double pipe structure via the liquid pipe 5 and the refrigerant flow control valve 32b. It flows into the hot water supply heat exchanger 8. On the other hand, the high temperature water in the hot water storage tank 10 is supplied from the lower portion of the hot water storage tank 10 to the hot water supply pump 9
Is sucked by and flows into the hot water supply heat exchanger 8 through the inlet water pipe 18 of the hot water supply heat exchanger. Here, the low-pressure two-phase refrigerant becomes a low-pressure gas refrigerant by exchanging heat with the circulating high-temperature water, and returns to the suction side of the compressor 1 via the two-way valve 31d, the low-pressure gas pipe 4, and the accumulator 2. The circulating high-temperature water returns to the upper part of the hot water storage tank 10 through the outlet side water pipe 17 of the hot water supply heat exchanger. The pressure of the refrigerant in the system is detected by a pressure sensor (not shown), and the opening of the flow control valve 43 in the bypass path of the hot water supply circulating water is controlled so that the refrigerant pressure in the system does not rise abnormally. By bypassing an appropriate amount of circulating water, the circulating water flowing into the hot water supply heat exchanger 8 can be adjusted and the amount of heat exchange in the hot water supply heat exchanger 8 can be controlled.

As described above, in this embodiment, by controlling the opening degree of the flow rate control valve in the bypass passage of the hot water circulating water,
Since the amount of circulating water can be adjusted and the amount of heat exchange in the hot water supply heat exchanger can be controlled, during hot water heating and reheating operation,
Even if heat is taken from hot water, it is possible to prevent the refrigerant pressure in the system from rising abnormally. By bypassing an appropriate amount of circulating water, the maximum amount can be secured within the range where the pressure of the refrigerant, particularly the low pressure, does not exceed the compressor operation limit pressure.

Example 6. FIG. 23 shows the configuration of the sixth embodiment. In the figure, 1 is a compressor, 2 is an accumulator,
3 is a high pressure gas pipe, 4 is a low pressure gas pipe, 5 is a liquid pipe, 6 is an indoor heat exchanger, 7 is a hot water supply unit, 8a and 8b are hot water heat exchangers, 9 is a hot water pump, 10 is a hot water tank, 11 Is a heater for heating, 12 is a reheating unit, 13 is a reheating heat exchanger, 14 is a reheating pump, 15 is a bathtub, 16 is an outdoor heat exchanger, 17 is outlet water pipe of the hot water heat exchanger, and 18 is Inlet-side water pipe of the heat exchanger for hot water supply, 19 is a hot water supply pipe, 20 is a water supply pipe, 31a, 31b, 31c, 31d, 31e, 3
1f, 31g, 31h are two-way valves, 32a, 32b, 32
Reference numeral c is a refrigerant flow control valve, and 44a and 44b are two-way valves for bypassing the hot water supply heat exchanger. The hot water supply heat exchanger 8b
Is 1/5 or less of the length of the hot water heat exchanger 8a. In addition,
The hot water supply heat exchangers 8a and 8b and the two-way valves 44a and 44b constitute a heat exchange amount adjusting means.

Next, the operation will be described. The operation of the heat pump type heating and cooling / hot water supply additional heating system of the present invention will be described. In addition, here, only the hot-water supply heat-utilizing additional heating operation, which is particularly effective, will be described.

(1) Reheating operation using hot water supply heat will be described with reference to FIG. The high-temperature and high-pressure refrigerant gas discharged from the compressor 1 passes from the gas pipe 3 through the reheating heat exchanger 13 via the two-way valve 31e. On the other hand, the water in the bathtub 15 is sucked from the lower part of the bathtub 15 by the reheating pump 14 and flows into the reheating heat exchanger 13 having a double pipe structure. Here, the refrigerant becomes a high-pressure liquid refrigerant while heating the circulating water by exchanging heat with the circulating water, and the reheating heat exchanger 13
More outflow. On the other hand, the heated circulating water returns to the bathtub 15. The high-pressure liquid refrigerant flowing out of the reheating heat exchanger 13 becomes a low-pressure two-phase refrigerant by passing through the refrigerant flow control valve 32c, and has a double pipe structure via the liquid pipe 5 and the refrigerant flow control valve 32b. It flows into the hot water supply heat exchanger 8. On the other hand, the high temperature water in the hot water storage tank 10 is supplied from the lower portion of the hot water storage tank 10 to the hot water supply pump 9
Is sucked by and flows into the hot water supply heat exchanger 8 through the inlet water pipe 18 of the hot water supply heat exchanger. Here, the low-pressure two-phase refrigerant becomes a low-pressure gas refrigerant by exchanging heat with the circulating high-temperature water, and returns to the suction side of the compressor 1 via the two-way valve 31d, the low-pressure gas pipe 4, and the accumulator 2. The circulating high-temperature water returns to the upper part of the hot water storage tank 10 through the outlet side water pipe 17 of the hot water supply heat exchanger. In addition, the refrigerant pressure in the system is detected by a pressure sensor (not shown), and the bypass two-way valve 44a of the hot water supply heat exchanger is opened and 44b is closed so that the refrigerant pressure in the system does not rise abnormally. Thus, heat can be exchanged only by the hot water supply heat exchanger 8b, and the amount of heat exchange can be reduced.

As described above, in this embodiment, the length of the hot water supply heat exchanger is shortened by opening and closing the bypass two-way valve of the hot water supply heat exchanger, and the heat exchange amount in the hot water supply heat exchanger is reduced. Therefore, there is an effect that the refrigerant pressure in the system can be prevented from rising abnormally even if heat is taken from the hot water for hot water supply during the hot water supply hot water reheating operation.

The hot water supply heat exchanger is divided so that the shorter one is ⅕ or less of the longer one, which is, as shown in FIG. 24, the high pressure side limit of 24 kg / cm2ab which is the pressure limit of the refrigerant.
s and the low pressure limit of 8.08 kg / cm2abs, the required length of the hot water heat exchanger is 3.5m for securing a reheating capacity of 4500kcal / h at the same time. )It can be seen that it is. That is, it is necessary to set the compressor frequency to a predetermined frequency by making the shorter one ⅕ or less of the longer one.

Example 7. FIG. 25 shows the configuration of the seventh embodiment. In the figure, 1 is a compressor, 2 is an accumulator,
3 is a high pressure gas pipe, 4 is a low pressure gas pipe, 5 is a liquid pipe, 6 is an indoor heat exchanger, 7 is a hot water supply unit, 8a and 8b are hot water heat exchangers, 9 is a hot water pump, 10 is a hot water tank, 11 Is a heater for heating, 12 is a reheating unit, 13 is a reheating heat exchanger, 14 is a reheating pump, 15 is a bath, 16a, 16b
Is an outdoor heat exchanger, 17 is an outlet side water pipe of the hot water supply heat exchanger,
18 is an inlet side water pipe of the hot water supply heat exchanger, 19 is a hot water supply pipe, 20 is a water supply pipe, 31a, 31b, 31c, 31
d, 31e, 31f, 31g, 31h are two-way valves, 32
Reference numerals a, 32b and 32c are refrigerant flow rate control valves, and 45 is a two-way valve for bypassing the outdoor heat exchanger.

Next, the operation will be described. The operation of the heat pump system of the present invention will be described. In addition, here, only the hot water supply operation and the additional heating operation, which are particularly effective, will be described.

(1) Hot water supply operation The operation will be described with reference to FIG. The high-temperature high-pressure refrigerant gas discharged from the compressor 1 passes through the gas pipe 3 and the hot water heat exchanger 8 via the two-way valve 31c. On the other hand, the water in the hot water storage tank 10 is sucked from the lower part of the hot water storage tank 10 by the hot water supply pump 9, and flows from the inlet side water pipe 18 of the hot water supply heat exchanger into the hot water supply heat exchanger 8 having a double pipe structure. Here, the refrigerant becomes a high-pressure liquid refrigerant while heating the circulating water by exchanging heat with the circulating water, and flows out from the hot water supply heat exchanger 8. on the other hand,
The heated circulating water is supplied to the outlet side water pipe 17 of the hot water supply heat exchanger 8.
The high-pressure liquid refrigerant flowing out of the hot water supply heat exchanger 8 returning to the upper part of the hot water storage tank 10 becomes a low-pressure two-phase refrigerant by passing through the refrigerant flow control valve 32b, and passes through the liquid pipe 5 to the outdoor heat exchanger. It flows into 16a and 16b. Here, the low-pressure two-phase refrigerant becomes a low-pressure gas refrigerant by exchanging heat with the outside air, and returns to the suction side of the compressor 1 via the two-way valve 31h, the low-pressure gas pipe 4, and the accumulator 2. Further, if necessary, the heater 11 is used to further raise the temperature. When the outside air temperature is high, such as in the summer, the two-way valve 45 is closed to allow the refrigerant to flow only to the outdoor heat exchanger 16a, thereby reducing the heat exchange amount in the outdoor heat exchanger and reducing the refrigerant pressure. An abnormal rise can be prevented.

(2) Reheating operation will be described with reference to FIG. The high-temperature and high-pressure refrigerant gas discharged from the compressor 1 passes from the gas pipe 3 through the reheating heat exchanger 13 via the two-way valve 31e. On the other hand, the water in the bathtub 15 is sucked from the lower part of the bathtub 15 by the reheating pump 14 and flows into the reheating heat exchanger 13 having a double pipe structure. Here, the refrigerant becomes a high-pressure liquid refrigerant while heating the circulating water by exchanging heat with the circulating water, and flows out from the reheating heat exchange 13. On the other hand, the heated circulating water returns to the bathtub 15. The high-pressure liquid refrigerant flowing out of the reheating heat exchanger 13 becomes a low-pressure two-phase refrigerant by passing through the refrigerant flow control valve 32c, and flows into the outdoor heat exchangers 16a, 16b through the liquid pipe 5. Here, the low-pressure two-phase refrigerant becomes a low-pressure gas refrigerant by exchanging heat with the outside air, and the two-way valve 31h,
It returns to the suction side of the compressor 1 via the low-pressure gas pipe 4 and the accumulator 2. When the outside air temperature is high, such as in the summer, the two-way valve 45 is closed to allow the refrigerant to flow only to the outdoor heat exchanger 16a, thereby reducing the heat exchange amount in the outdoor heat exchanger and reducing the refrigerant pressure. An abnormal rise can be prevented.

As described above, in this embodiment, the heat exchange amount in the outdoor heat exchanger is controlled by opening / closing the bypass two-way valve of the outdoor heat exchanger to change the capacity of the outdoor heat exchanger. Therefore, when performing hot water supply operation or reheating operation when the outside air is high such as in summer, the effect of reducing the heat exchange amount in the outdoor heat exchanger and preventing the refrigerant pressure in the system from rising abnormally can be obtained. is there.

Example 8. FIG. 27 shows the structure of the eighth embodiment. In the figure, 1 is a compressor, 2 is an accumulator,
3 is a high pressure gas pipe, 4 is a low pressure gas pipe, 5 is a liquid pipe, 6 is an indoor heat exchanger, 7 is a hot water supply unit, 8 is a hot water supply heat exchanger, 9 is a hot water supply pump, 10 is a hot water storage tank, 11 is for heating Heater, 12
Is a reheating unit, 13 is a reheating heat exchanger, 14 is a reheating pump, 15 is a bathtub, 16 is an outdoor heat exchanger, 17 is an outlet side water pipe of the hot water heat exchanger, and 18 is a hot water heat exchanger. Inlet water pipe, 19 hot water pipe, 20 water supply pipe, 21 outdoor fan, 22 bathroom drying heat exchanger, 23 bathroom drying unit, 310a, 310b, 310c, 310d
Is a three-way valve, 310e is a two-way valve, 32a, 32b, 32c
Is a refrigerant flow control valve, 330 is a check valve, and 45 is a pressure detecting means.

Next, the operation will be described. The operation of the heat pump system of the present invention will be described. It should be noted that only the bathroom drying alone operation, which is particularly effective, will be described here. (1) Bathroom dry operation alone The operation will be described with reference to FIG. The high-temperature high-pressure refrigerant gas discharged from the compressor 1 passes through the gas pipe 3 and the bathroom drying heat exchanger 22 via the three-way valve 310c. Bathroom dry heat exchanger 22
In the above, the refrigerant gas becomes a high-pressure liquid refrigerant while heating the air by exchanging heat with the air in the bathroom, and flows out from the bathroom drying heat exchanger 22. The liquid refrigerant that has flowed out becomes a low-pressure two-phase refrigerant by passing through the refrigerant flow control valve 32c, and enters the liquid pipe 5. On the other hand, a part of the high-temperature and high-pressure refrigerant gas discharged from the compressor 1 is supplied from the gas pipe 3 to the three-way valve 310a.
After entering the indoor heat exchanger 6 via the, and radiating heat, it enters the liquid pipe 5 via the refrigerant flow control valve 32a. The low-pressure two-phase refrigerant in the liquid pipe 5 flows into the outdoor heat exchanger 16 through the two-way valve 310e. Here, the low-pressure two-phase refrigerant becomes a low-pressure gas refrigerant by exchanging heat with the outside air, and the three-way valve 310
It returns to the suction side of the compressor 1 via d, the low pressure gas pipe 4, and the accumulator 2.

As described above, in this embodiment, when the bathroom drying unit is connected in series with the reheating unit and the bathroom drying operation is performed independently, the heat exchanger capacity of the bathroom drying unit which becomes the condenser is equal to that of the compressor. When the capacity is considerably smaller than the capacity, even if the frequency of the compressor is lowered to the minimum, the refrigerant pressure on the high-pressure side rises abnormally and operation becomes impossible. Therefore, the three-way valve on the indoor heat exchanger side is switched to the high-pressure gas pipe side, and the refrigerant flow rate control valve opening on the indoor heat exchanger side is changed according to the outside air temperature, that is, when the outside air temperature is high, the refrigerant flow rate control valve is opened. Temperature, the opening is reduced when the outside air temperature is low, and the refrigerant flow rate is adjusted according to the outside air temperature to eliminate the difference in the amount of condensation heat escaped based on the difference between the refrigerant temperature and the outside air temperature. By bypassing an appropriate amount of high-pressure refrigerant to the indoor heat exchanger that is not operating, part of the heat of condensation is released to the indoor heat exchanger, and an abnormal increase in high pressure can be prevented.

Although the reheating unit and the bathroom drying unit are connected in series in FIG. 27, they may be connected in parallel. Further, in this embodiment, the refrigerant flow rate control valve opening is changed based on the outside air temperature, but this is because it can be considered that the temperature of the indoor air that exchanges heat with the refrigerant in the indoor heat exchanger corresponds to the outside air temperature. Therefore, if the temperature of the indoor air that exchanges heat with the indoor heat exchanger is measured by the indoor temperature detecting means and the refrigerant flow control valve opening is changed according to the indoor temperature, a more accurate control of the escape amount of the condensation heat can be achieved. It is possible. Further, in FIG. 27, an example in which the high pressure refrigerant gas is bypassed to the indoor heat exchanger 6 to release a part of the condensation heat is shown. However, in FIG. 27, 6 is an outdoor heat exchanger and 16 is an indoor heat exchanger. The same effect can be obtained in a so-called cooling exhaust heat utilization drying operation in which part of the heat of condensation of the high-pressure refrigerant gas is released to the container 6.

FIG. 28 is a flowchart showing the control based on the outside air temperature. In FIG. 28A, S2
At S3, the outside temperature Tout is detected by the outside temperature detecting means.
If Tout> set outside air temperature Ta, the indoor refrigerant flow rate control valve opening is set to a predetermined opening Va in S4, and To in S3.
When ut <the set outside air temperature Ta, the indoor-side refrigerant flow control valve opening is set to a predetermined opening Vb smaller than the predetermined opening Va in S5.
Is set, and the flow rate of the refrigerant is adjusted according to the outside air temperature to keep the escape amount of the condensation heat substantially constant. In FIG. 28 (b),
The outside air temperature Tout is detected in S2, and the valve setting opening is set to α × Tout (where α is a constant) in S3. This control method enables more accurate control by faithfully reflecting the outside air temperature as compared with FIG.

Example 9. The configuration and the flow of the refrigerant are the same as those in the first and second embodiments, and the description thereof will be omitted. In this system, when hot water supply operation, reheating operation, and bathroom drying operation are performed, the outdoor heat exchanger is operated as an evaporator as shown in Examples 1 and 2, so that the outside temperature is high such as in summer.
When the compressor is operated at the normal starting frequency, the pressure of the refrigerant rises above the pressure limit and it becomes impossible to continue the operation. Therefore, in modes such as hot water supply operation, reheating operation, and bathroom drying operation in which the outdoor heat exchanger operates as an evaporator, if the outside air temperature is higher than a certain set value, lower the initial frequency of the compressor. By starting, it is possible to prevent an abnormal pressure rise of the refrigerant. The startup time pressure adjusting means is composed of a compressor and a compressor inverter that changes the rotation speed of the compressor. Further, FIG. 29 shows a flowchart regarding the above control.

Example 10. The configuration and the flow of the refrigerant are the same as those in the first and second embodiments, and the description thereof will be omitted. In this system, when hot water supply operation, reheating operation, and bathroom drying operation are performed, since the outdoor heat exchanger is operated as an evaporator as shown in Examples 1 and 2, it is normally used under high ambient temperature conditions such as in summer. When the outdoor fan is rotated at full speed as described above, the evaporation pressure of the refrigerant exceeds the allowable low pressure limit of the compressor.
Therefore, in modes such as hot water supply operation, reheating operation, and bathroom drying operation in which the outdoor heat exchanger operates as an evaporator, if the outside air temperature is higher than a certain set value, the initial outdoor fan rotation speed at the start of operation. By lowering, it is possible to prevent the evaporation pressure at the time of startup from rising above the limit. The outdoor heat exchanger 16, the outdoor fan 21, and the outdoor fan inverter that changes the number of rotations of the outdoor fan constitute the startup pressure adjusting means. Further, a flow chart regarding the above control is shown in FIG. In FIG. 30, the outside air temperature Tout is detected by the outside air temperature detecting means in S2, and in S3,
When Tout> set outside air temperature Ta, the initial outdoor fan rotation speed is minimized, and in S4, Tout <set outside air temperature T
In the case of a, the initial outdoor fan rotation speed is maximized.

Example 11. The configuration and the flow of the refrigerant are the same as those in the first and second embodiments, and will be omitted. In this system, if the reheating operation command comes during the cooling operation, if the compressor is operated at a frequency higher than the sufficient reheating capacity, the cooling heat exhaust heating operation is performed. Both indoor cooling and reheating can be performed, and also
In order to secure the reheating capacity by giving priority to the reheating operation when the compressor is operated at a frequency lower than the frequency that can sufficiently secure the reheating capacity, and by stopping the cooling operation and performing the additional heating operation. If the required cooling capacity is small (for example, cooling on a day that is not too hot), the cooling capacity may be unnecessarily high, if the frequency is increased to secure the reheating capacity. Although the temperature of the indoor heat exchanger drops too much and frost is generated, these problems can be prevented and a sufficient reheating capability can be secured. A flowchart relating to the above control is shown in FIG.

[0079]

Since the heat pump system according to the present invention can use the hot water supply heat to perform the additional heating operation, it is possible to perform high-speed and high-speed boiling without being affected by the outside air temperature.

Further, according to the present invention, the refrigerant pressure of the refrigerant system is detected to adjust the heat exchange amount of the hot water supply heat exchanger, so that the abnormality of the refrigerant pressure in the system can be prevented.

Further, according to the present invention, the refrigerant pressure is detected, and the rotation control means controls the number of revolutions of the oil supply pump according to the refrigerant pressure to change the circulating water amount to change the heat exchange amount in the hot water supply heat exchanger. Since it can be controlled, it is possible to prevent the refrigerant pressure in the system from rising abnormally even if heat is taken from the hot water for hot water supply during the hot water heating and reheating operation.

Further, according to the present invention, by detecting the low pressure of the refrigerant and opening the on-off valve in the bypass passage for the hot water circulating water,
Since the amount of circulating water can be reduced and the amount of heat exchange in the hot water supply heat exchanger can be controlled, the refrigerant pressure in the system will rise abnormally even when heat is taken from the hot water for hot water supply during hot water reheating operation. Can be prevented.

Further, in the heat pump system according to the present invention, by controlling the opening degree of the flow rate control valve in the bypass path of the hot water circulating water, the circulating water amount is adjusted and the heat exchange amount in the hot water heat exchanger is controlled. Therefore, there is an effect that the refrigerant pressure in the system can be prevented from rising abnormally even if heat is taken from the hot water for hot water supply during the hot water supply hot water reheating operation.

Further, in the heat pump system according to the present invention, in the operation mode in which the outdoor unit is the evaporator such as the hot water supply operation, the additional heating operation, and the drying operation, the startup pressure is adjusted by the startup pressure adjusting means according to the outside air temperature. Therefore, it is possible to prevent an abnormal stop due to a high voltage rise at startup.

Further, in the heat pump system according to the present invention, the initial compressor frequency at the start of operation is changed according to the outside temperature in the operation mode in which the outdoor unit is the evaporator such as the hot water supply operation, the additional heating operation, and the drying operation. It is possible to prevent an abnormal stop due to a high voltage rise at startup.

Further, in the heat pump system according to the present invention, in the operation mode in which the outdoor unit is the evaporator such as the hot water supply operation, the additional heating operation, and the drying operation, the initial outdoor fan rotation speed at the start of operation is changed according to the outside temperature. Therefore, it is possible to prevent an abnormal stop due to a high pressure rise at the time of startup.

Further, in the heat pump system according to the present invention, the length of the hot water supply heat exchanger is shortened by opening and closing the bypass opening / closing valve of the hot water supply heat exchanger, and the heat exchange amount in the hot water supply heat exchanger is reduced. Since it can be controlled, there is an effect that the refrigerant pressure in the system can be prevented from rising abnormally even if heat is taken from the hot water for hot water supply during the hot water supply hot water reheating operation.

Further, the heat pump system according to the present invention comprises the reheating unit and the bathroom drying heat exchanger of the bathroom drying unit connected to the reheating unit, and when the bathroom drying operation is performed, one of high pressure refrigerant gas from the compressor is removed. Since the part is bypassed to the indoor heat exchanger or the outdoor heat exchanger to release part of the condensation heat, even if the capacity of the compressor is larger than the bathroom dry heat exchanger capacity, an abnormal rise in high pressure can be prevented.

In the heat pump system according to the present invention, the bathroom drying unit is connected to the reheating unit,
When the bathroom drying is operated independently, the open / close valve on the indoor heat exchanger side is switched to the high pressure gas pipe side, and the refrigerant flow rate control valve opening on the indoor heat exchanger side is changed according to the outside air temperature, and the indoor heat exchange is not in operation. By bypassing an appropriate amount of high-pressure refrigerant to the compressor, part of the condensation heat is released to the indoor heat exchanger, preventing an abnormal rise in high pressure even if the compressor capacity is larger than the bathroom dry heat exchanger capacity. be able to.

[0090]

[0091]

[0092]

Further, in the heat pump system according to the present invention, when the reheating operation command is received during the cooling operation, when the compressor is operated at a frequency higher than the sufficient reheating capacity, When performing the cooling exhaust heat reheating operation, if the compressor is operating at a frequency lower than the frequency that can sufficiently secure the reheating capacity, priority is given to the reheating operation,
Since the cooling operation is stopped and the additional heating operation is performed, it is possible to secure a sufficient additional heating capacity without causing a problem such as frost formation due to excessive cooling of the room or excessive cooling of the indoor heat exchanger.

[Brief description of drawings]

FIG. 1 is a configuration diagram of a heat pump system showing an embodiment of the present invention.

FIG. 2 is a system diagram showing heating operation in the heat pump system according to the embodiment of the present invention.

FIG. 3 is a system diagram showing a cooling operation in the heat pump system according to the embodiment of the present invention.

FIG. 4 is a system diagram showing a hot water supply operation in the heat pump system according to the embodiment of the present invention.

FIG. 5 is a system diagram showing a reheating operation in the heat pump system according to the embodiment of the present invention.

FIG. 6 is a system diagram showing a hot water supply operation using cooling waste heat in the heat pump system according to the embodiment of the present invention.

FIG. 7 is a system diagram showing a hot water supply-based additional heating operation in the heat pump system according to the embodiment of the present invention.

FIG. 8 is a system diagram showing a hot water supply operation using bathtub waste heat in the heat pump system according to the embodiment of the present invention.

FIG. 9 is a diagram showing a comparison of heating capacities according to water temperatures according to an embodiment of the present invention.

FIG. 10 is a diagram showing a comparison of boiling times according to an embodiment of the present invention.

FIG. 11 is a configuration diagram of a heat pump system showing another embodiment of the present invention.

FIG. 12 is a system diagram showing a heating operation in the heat pump system according to another embodiment of the present invention.

FIG. 13 is a system diagram showing a cooling operation in the heat pump system according to another embodiment of the present invention.

FIG. 14 is a system diagram showing a hot water supply operation in the heat pump system according to another embodiment of the present invention.

FIG. 15 is a system diagram showing a reheating operation in a heat pump system according to another embodiment of the present invention.

FIG. 16 is a system diagram showing a hot water supply operation using cooling waste heat in the heat pump system according to another embodiment of the present invention.

FIG. 17 is a system diagram showing an additional heating operation using hot water supply heat in a heat pump system according to another embodiment of the present invention.

FIG. 18 is a system diagram showing hot water supply operation using bathtub waste heat in a heat pump system according to another embodiment of the present invention.

FIG. 19 is a system diagram showing a hot water supply-based additional heating operation in a heat pump system according to another embodiment of the present invention.

FIG. 20 is a system diagram showing a hot water supply-based additional heating operation in a heat pump system according to another embodiment of the present invention.

FIG. 21 is a control flowchart of another embodiment of the present invention.

FIG. 22 is a system diagram showing an additional heating operation using hot water supply heat in a heat pump system according to another embodiment of the present invention.

FIG. 23 is a system diagram showing a hot water supply-based additional heating operation in a heat pump system according to another embodiment of the present invention.

FIG. 24 is a diagram showing a relationship between hot water supply heat exchanger length and pressure in a hot water supply heat-addition operation of another embodiment of the present invention.

FIG. 25 is a system diagram showing a hot water supply operation in a heat pump system according to another embodiment of the present invention.

FIG. 26 is a system diagram showing a reheating operation in a heat pump system according to another embodiment of the present invention.

FIG. 27 is a system diagram showing a bathroom drying operation in a heat pump system according to another embodiment of the present invention.

FIG. 28 is a control flowchart in a bathroom drying operation in the heat pump system according to another embodiment of the present invention.

FIG. 29 is a flow chart of compressor startup control during hot water supply operation, additional heating operation, or bathroom drying operation in the heat pump system according to another embodiment of the present invention.

FIG. 30 is a flowchart of outdoor fan control during hot water supply operation, additional heating operation, or bathroom drying operation in the heat pump system according to another embodiment of the present invention.

FIG. 31 is a control flow chart at the time of simultaneous cooling and heating operation in the heat pump system according to another embodiment of the present invention.

FIG. 32 is a system diagram showing an additional heating operation in a conventional heat pump system.

[Explanation of symbols]

1 compressor, 2 accumulator, 3 high pressure gas pipe,
4 low-pressure gas pipe, 5 liquid pipe, 6 indoor heat exchanger, 7 hot water supply unit, 8 hot water heat exchanger, 9 hot water pump, 10
Hot water storage tank, 11 heating heater, 12 reheating unit,
13 reheating heat exchanger, 14 reheating pump, 15 bathtub, 16 outdoor heat exchanger, 17 hot water heat exchanger outlet side water piping, 18 hot water heat exchanger inlet side water piping, 19 hot water piping, 20 water supply piping , 21 outdoor fan, 22 bathroom dry heat exchanger, 23 bathroom drying unit, 31a two-way valve, 31b two-way valve, 31c two-way valve, 31d two-way valve, 31e two-way valve, 31f two-way valve, 31g two-way Valve, 31h two-way valve, 32a refrigerant flow control valve, 32b
Refrigerant flow control valve, 32c Refrigerant flow control valve, 40 Hot water supply pump inverter, 41 Circulating water bypass passage throttle device, 42 Two-way valve in circulating water bypass passage, 43 Circulating water bypass passage flow control valve, 44a, 44b Two-way valve for bypassing heat exchanger for hot water supply, 45 pressure detection means, 50
Low pressure detection means, 310a three-way valve, 310b three-way valve,
310c three-way valve, 310d three-way valve, 310e three-way valve, 330 check valve.

─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Tetsuji Okada 3-18-1, Ogashi, Shizuoka City Mitsubishi Electric Co., Ltd. Living Environment Engineering Coordination Center (72) Inventor Yoshiaki Tanimura 3-18-1 Oga, Shizuoka No. Mitsubishi Electric Co., Ltd. Living Environment Engineering Control Center (72) Inventor Iijima, et al. 3-18-1, Oga, Shizuoka City Mitsubishi Electric Co., Ltd. Living Environment Engineering Control Center (56) Reference JP-A-61 -149771 (JP, A) JP 50-15149 (JP, A) JP 2-85656 (JP, A) JP 1-212872 (JP, A) JP 4-332352 (JP, A) ) (58) Fields surveyed (Int.Cl. ⁷ , DB name) F25B 29/00 361 F25B 29/00 371 F25B 13/00 104 F25B 27/00 F24D 17/02 F24H 1/00

Claims (12)

(57) [Claims] 1. A compressor and an indoor heat exchanger are connected by a gas pipe.
The indoor heat exchanger and the outdoor heat exchanger through a flow control valve.
And connect it with a liquid pipe to lower the outdoor heat exchanger and the compressor.
A refrigeration cycle in which a refrigerant is circulated by connecting with a pressure gas pipe
And, in any possible operating a heat pump system of at least heating and cooling, to heat the circulating water to the tub with refrigerant exchanges heat discharged from the compressor, connected to the gas pipe one end provided additional heating unit The other end is the liquid
A reheating heat exchanger connected to the pipe, the reheating heat exchanger being connected to the reheating heat exchanger via the liquid pipe, and the other end being the low pressure gas
A hot water supply heat exchanger that is connected to the cooling water pipe and that exchanges heat between the refrigerant and high temperature water stored in a hot water storage tank and circulated by a hot water supply pump, and is discharged from the compressor.
The condensed refrigerant is condensed in the reheating heat exchanger to become a liquid refrigerant.
After that, it evaporates into a gas refrigerant in the hot water heat exchanger.
The heat pump system is characterized in that the reheating operation is performed by utilizing the heat of the high temperature water stored in the hot water storage tank by circulating the hot water to the compressor . 2. A pressure detecting means for detecting the pressure of the refrigerant in the refrigerant system for circulating the refrigerant, and a heat exchange amount adjusting means for adjusting the heat exchange amount of the hot water supply heat exchanger to reduce the refrigerant pressure during the reheating operation. The heat pump system according to claim 1, further comprising: 3. A hot water supply pump in the hot water supply unit is provided with a rotation speed control means for detecting the pressure of the refrigerant to control the rotation speed, and by varying the circulating amount of water, heat exchange in the hot water supply heat exchanger. The heat pump system according to claim 2, wherein the amount is controlled. 4. In the hot water supply unit, a bypass passage through an on-off valve is provided between an inlet side water pipe and an outlet side water pipe of the hot water heat exchanger so that the pressure of the refrigerant is detected and the hot water heat exchanger is used. The heat pump system according to claim 2, wherein, when the amount of heat exchange is excessive, the amount of heat exchange is controlled by bypassing water. 5. In the hot water supply unit, a bypass passage via a water flow rate control valve is provided between an inlet side water pipe and an outlet side water pipe of the hot water heat exchanger to detect the pressure of the refrigerant and perform hot water heat exchange. 3. When the amount of heat exchange in the vessel is too large, a proper amount of water is bypassed to control the amount of heat exchange.
The heat pump system described. 6. An outside air temperature detecting means and a starting pressure adjusting means.
And has at least one of hot water supply operation and reheating operation.
There, according to claim 1 that time, the evaporator the outdoor heat exchanger, and that the temperature detected by said outside air temperature detecting means, by the startup pressure adjusting means, and adjusting the pressure during startup The heat pump system described . 7. The heat pump system according to claim 6 , wherein the frequency of the compressor at the start of operation is changed according to the outside air temperature to adjust the pressure at the start. 8. The heat pump system according to claim 6 , wherein the number of rotations of the outdoor fan of the outdoor heat exchanger at the start of operation is changed according to the outside air temperature to adjust the pressure at the start. 9. A compressor and an indoor heat exchanger are connected by a gas pipe.
The indoor heat exchanger and the outdoor heat exchanger through a flow control valve.
And connect it with a liquid pipe to lower the outdoor heat exchanger and the compressor.
A refrigeration cycle in which a refrigerant is circulated by connecting with a pressure gas pipe
However, at least one of the heating and cooling
Pump system, the refrigerant discharged from the compressor
To heat the circulating water to the bath by exchanging heat with
On one side and one end connected to the gas pipe and the other end connected to the liquid
A reheating heat exchanger connected to a pipe, and the reheating heat exchanger
To the low-pressure gas
Installed in the hot water supply unit with the refrigerant
Heat exchange with high-temperature water stored in a hot water storage tank and circulated by a hot water supply pump
A hot water heat exchanger to be exchanged and a refrigerant system to circulate the refrigerant.
Pressure detection means for detecting the pressure of the refrigerant in the stem.
The hot water supply heat exchanger is divided so that the length of the shorter hot water supply heat exchanger is 1/5 or less of that of the longer hot water supply heat exchanger, and the shorter hot water supply heat exchanger is arranged on the liquid pipe side. However, the longer hot water supply heat exchanger is arranged on the gas pipe side, and the outlet side refrigerant pipe of the shorter hot water supply heat exchanger is connected to the inlet side refrigerant pipe of the longer hot water supply heat exchanger through the two-way valve. If the amount of heat exchange in the hot water heat exchanger is too large by detecting the pressure of the refrigerant by connecting to the outlet side refrigerant pipes and detecting the pressure of the refrigerant, shorten the total length of the hot water heat exchanger by opening and closing the on-off valve. A heat pump system characterized by controlling the amount of heat exchange. 10. A compressor and an indoor heat exchanger are connected by a gas pipe.
The indoor heat exchanger and the outdoor heat exchanger through a flow control valve.
And connect it with a liquid pipe to lower the outdoor heat exchanger and the compressor.
A refrigeration cycle in which a refrigerant is circulated by connecting with a pressure gas pipe
And, in any possible operating a heat pump system of at least heating and cooling, one end provided reheating unit and refrigerant exchanges heat discharged from the compressor to heat the circulating water to the tub is connected to the gas pipe The other end is the liquid pipe
To the additional heating unit and the additional heating heat exchanger connected to the
A bathroom drying heat exchanger of a bathroom drying unit connected via the gas pipe , wherein the indoor heat exchanger or the outdoor heat exchanger is allowed to bypass a part of the high-pressure refrigerant gas from the compressor to perform a bathroom drying operation. A heat pump system characterized by performing. 11. An indoor heat exchanger is provided with an outside air temperature detecting means, and the outside air temperature is detected by the outside air temperature detecting means.
The heat pump system according to claim 10, wherein the opening degree of the flow control valve is changed to bypass the high pressure refrigerant gas from the compressor to the indoor heat exchanger. 12. The compressor and the indoor heat exchanger are connected by a gas pipe.
The indoor heat exchanger and the outdoor heat exchanger through a flow control valve.
And connect it with a liquid pipe to lower the outdoor heat exchanger and the compressor.
A refrigeration cycle in which a refrigerant is circulated by connecting with a pressure gas pipe
And, in any possible operating a heat pump system of at least heating and cooling, to heat the circulating water to the tub with refrigerant exchanges heat discharged from the compressor, connected to the gas pipe one end provided additional heating unit The other end is the liquid
With a reheating heat exchanger connected to the pipe, if a reheating operation command is received while performing cooling operation, if the compressor is operating at a frequency that is sufficient or higher to ensure the reheating capacity, The cooling exhaust heat reheating operation is performed, and if the compressor is operating at a frequency below the sufficient reheating capacity, priority is given to the reheating operation, and the cooling operation is stopped and the additional heating operation is performed. And heat pump system.