JPH0123089Y2 - - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a heat pump air conditioning/heating/water heater that uses only a refrigeration cycle and does not require any auxiliary heat source.

Multi-purpose devices that add hot water operation to heating and cooling operations using a compression refrigeration cycle are becoming popular as central heating devices in homes, but conventional systems have traditionally included an air conditioner and a large boiler that can heat and supply hot water using hot water. Regardless of whether the energy source for heating and hot water supply is electricity or other fuel, the fan coil unit inside the room has two routes for air and water. This method requires a large amount of installation space, requires four pipes, one for the refrigerant, and one for the water, making the construction work complicated.Furthermore, there are other problems such as troublesome handling.

The present invention has been made with attention to these points and an attempt to provide a heat pump type air-conditioning/heating water heater that can eliminate the deficiencies of conventional devices of this type.

That is, as shown in the basic circuit diagram of FIG. 1, the present invention provides a user-side heat exchanger 8 having two refrigerant systems, a first refrigerant passage 9A and a second refrigerant passage 9B.
A compressor 1A, a four-way switching valve 2A, an air-type heat source side heat exchanger 3A, a heating pressure reducer 4A with a check valve 6A connected in parallel, and a cooling system with a check valve 7A connected in parallel. pressure reducer 5A and the first refrigerant passage 9
A as an element, a first refrigeration system A formed into a reversible heat pump refrigeration cycle that can be switched between cooling operation and heating operation, a compressor 1B, a four-way switching valve 2B,
An air-type heat source side heat exchanger 3B, a heating pressure reducer 4B with a check valve 6B connected in parallel, a cooling pressure reducer 5B with a check valve 7B connected in parallel, and the second refrigerant passage 9B. A second refrigeration system B formed into a reversible heat pump refrigeration cycle capable of switching between cooling operation and heating operation, and a hot water supply heat exchanger 10 and a control valve provided in connection with the first refrigeration system A, respectively. 12, and the control valve 12 is connected to the compressor 1.
The discharge ports of A are connected to the inflow side ports of the four-way switching valve 2A during the cooling cycle and the heating cycle, respectively, and are connected to the inflow side ports of the four-way switching valve 2A during the hot water supply cycle, and the hot water supply heat exchanger 1 is connected during the hot water supply cycle.
The hot water supply heat exchanger 10 is switchably interposed in the discharge gas pipe 14 so as to communicate with the refrigerant inlet of
The hot water supply side port of the control valve 12 and the heating pressure reducer 4
A refrigerant side passage is interposed in a high-pressure pipe 15 that is provided so as to communicate between A and the inlet side of the cooling pressure reducer 5A only during hot water supply operation, and the first refrigeration system A is connected to the heating side of the four-way switching valve 2A. switching operation to side or cooling side,
By switching the control valve 12 and forcibly closing the cooling pressure reducer 5A, the cooling pressure reducer 5A, or the heating pressure reducer 4A,
While the hot water supply heat exchanger 10 acts as a condenser, the heat source side heat exchanger 10 acts as an evaporator,
and the first hot water supply operation by the refrigeration cycle in which the first refrigerant passage 9A is inactive or the first refrigerant passage 9A
acts as an evaporator, and the heat source side heat exchanger 3A
A heat pump air-conditioning/heating water heater capable of switching to a second hot water supply operation using a refrigeration cycle in which the refrigeration cycle is inactive, the cooling-only operation and the heating-only operation using the same cycle of the first refrigeration system A and the second refrigeration system B, A dedicated hot water supply operation by the first hot water supply operation of the first refrigeration system A, a cooling hot water supply operation in which the second hot water supply operation of the first refrigeration system A is combined with the cooling operation of the second refrigeration system B, and the first hot water supply operation of the first refrigeration system A. Second refrigeration system B for hot water supply operation
The present invention is characterized in that it is possible to operate in five modes of heating hot water supply operation in combination with heating operation.

Hereinafter, specific aspects of the present invention will be described in detail with reference to specific examples shown in the accompanying drawings.

Figure 1 shows the basic refrigerant system of the air-conditioning/heating water heater according to the present invention, in which two refrigeration circuits, a first refrigeration system A and a second refrigeration system B, are connected to a water-to-water user side heat exchanger. It is provided in connection with 8.

The user-side heat exchanger 8 has a double bundle structure including a first refrigerant passage 9A and a second refrigerant passage 9B, and the shell side is formed as a flow path for water for heating and cooling.

The first refrigeration system A includes a compressor 1A, a four-way switching valve 2A,
A heating pressure reducer 4A with an air-type heat source side heat exchanger 3A and a check valve 6A connected in parallel, such as an automatic expansion valve, and a cooling pressure reducer 5A with a check valve 7A connected in parallel, such as an automatic expansion valve. , the liquid receiver 11 and the first refrigerant passage 9A are used as elements to form a reversible heat pump refrigeration cycle that can be switched between cooling operation and heating operation, and further includes a hot water supply heat exchanger 10,
It has a control valve 12 and a check valve 13 in association with each other, and is formed into a refrigeration circuit capable of further hot water supply operation as described later. Note that 16 is a high pressure liquid pipe.

On the other hand, the second refrigeration system B has a compressor 1B, a four-way switching valve 2B, an air-type heat source side heat exchanger 3B, and a check valve 6.
Cooling operation is performed using a heating pressure reducer 4B, for example, a capillary reach tube, and a cooling pressure reducer 5B, for example, a capillary reach tube and the second refrigerant passage, connected in parallel to each other. It is a reversible heat pump refrigeration cycle that can be switched between heating and heating operation.

The control valve 12 is an electromagnetic switching valve such as a three-way switching valve, and is connected to the discharge port of the compressor 1A and the four-way switching valve 2.
The discharge port of the compressor 1A is connected to the inlet port of the four-way selector valve 2A during the cooling cycle and during the heating cycle, respectively, and hot water is supplied. During the cycle, the refrigerant inlet of the heat exchanger 10 for hot water supply is switchably provided.

The hot water supply heat exchanger 10 is a heat exchanger that is provided with a refrigerant side passage and a water side passage for heat exchange, and the refrigerant side passage is connected to the hot water supply side port of the control valve 12, the heating pressure reducer 4A, and the water supply side port of the control valve 12. A check valve 13 is interposed in series on the downstream side in a high pressure pipe 15 connecting the inlet side of the cooling pressure reducer 5A.
The flow prevention effect of 3 prevents the refrigerant from flowing to the high pressure pipe 15 side except during hot water supply operation.

The apparatus having such a basic structure can be operated by selecting five operating modes as follows.

(a) Cooling-only operation is performed by operating the four-way switching valves 2A and 2B to the valve positions shown by solid lines, and operating the control valve 12 to the valve positions shown by solid lines to energize both compressors 1A and 1B.

Both the first refrigeration system A and the second refrigeration system B form a cooling cycle in which the refrigerant flows in the direction indicated by the solid line arrow in FIG.
By each of the first refrigerant passage 9A and the second refrigerant passage 9B acting on the evaporator, low-temperature water for cooling can be obtained in the user-side heat exchanger 8 with the sufficient capacity of the two refrigeration systems.

In this case, the heating pressure reducer 4A is automatically controlled to close, but it may be forcibly closed. Since both ends of the hot water supply heat exchanger 10 are closed on the refrigerant side by the control valve 12 and the check valve 13, the operation is stopped.

(b) For heating-only operation, switch the four-way switching valves 2A and 2B to the dashed line valve positions,
The control valve 12 is operated in the same way as during cooling, and both compressors 1
Operate by energizing A and 1B.

Both the first refrigeration system A and the second refrigeration system B form a warm-back cycle in which the refrigerant flows in the direction indicated by the broken line arrow, and the first refrigerant passage 9A and the second refrigerant passage 9B are connected to the condenser,
As the heat source side heat exchangers 3A and 3B act on the evaporator, high temperature water for heating is obtained in the user side heat exchanger 8 with sufficient capacity of both the refrigeration systems A and B.

In this case, the cooling return pressure reducer 5A is automatically or forcibly closed.

The hot water supply heat exchanger 10 is not operating as in the case of cooling.

(c) Operation exclusively for hot water supply, the second refrigeration system B stops operation, the first refrigeration system A operates the four-way switching valve 2A to the heating side, and the control valve 1
2 to the illustrated broken line valve position and energizes the compressor 1A.

In the first refrigeration system A, the refrigerant flows in the direction indicated by the wavy line in the diagram, forming a first hot water supply operation in which the hot water supply heat exchanger 10 acts on the condenser and the heat source side heat exchanger 3A acts on the evaporator. As a result, high-temperature water for hot water supply is obtained in the heat exchanger 10 for hot water supply.

Note that the maximum hot water supply capacity is about 50% compared to when it is only used for heating, which is sufficient for hot water supply.On the other hand, during the cooling season, it is necessary to further reduce the capacity, so heat exchange on the heat source side is used. The evaporation capacity may be reduced by dividing the container 3A into two and separating one from the refrigerant circuit, or by reducing the air volume of the outdoor fan.

(d) Combined operation of cooling and hot water supply, the second refrigeration system B is operated in the cooling operation in the same manner as in the previous (a), while the first refrigeration system A is operated with the four-way switching valve 2A.
This is done by switching the control valve 12 to the cooling return side, switching the control valve 12 to the hot water supply operation side, forcing the heating pressure reducer 5A to close, and energizing the compressor 1A.

In the first refrigeration system A, the refrigerant flows in the direction indicated by the wavy line in FIG. By forming a second hot water supply operation in which the evaporators act on the respective evaporators, hot water supply heat exchanger 10 can obtain hot water for hot water supply, while user side heat exchanger 8 can achieve 100% capacity from both refrigeration systems A and B. Low-temperature water for air conditioning can be obtained.

In this case, in the first refrigeration system A, the heat source side heat exchanger 3A is inactive, and the operation is such that the heat of condensation is released to the hot water supply water and the heat of evaporation is captured in the first refrigerant passage 9A, so the heat recovery operation is performed. is carried out effectively.

(e) Combined heating and hot water supply operation, operate the first refrigeration system A in the same manner as in the previous (c), and
Operate refrigeration system B in the same manner as in the previous (b).

At this time, in the first refrigeration system A, the hot water supply heat exchanger 10 acts on the condenser, the heat source side heat exchanger 3A acts on the evaporator, and the first refrigerant passage 9A becomes inactive.

Therefore, the refrigeration capacity of the first refrigeration system A is used for hot water supply, and the refrigeration capacity of the second refrigeration system A is
The refrigeration capacity of refrigeration system B is used for heating, and both have 50% capacity.

It has been clarified through the explanation of each section above that five types of operation modes can be performed, and next, a specific implementation apparatus according to the present invention will be illustrated with reference to FIGS. 2 and 3.

In this device, 1A, 1B to 7A, 7B,
Since each member numbered 8 to 16 is the same member corresponding to the same numbered member in FIG. 1, a description thereof will be omitted, and the other members will be described below.

17A and 17B are three-way solenoid valves for unloading, with the inlet port P ₁ connected to the operating section of the unloading mechanism of the compressors 1A and 1B, and the switching port P ₂ connected to the low pressure side.
The switching port _P3 is connected to the high pressure side through the gauge joint 36 with a check valve, and the inflow port _P1 and the switching port _P3 are connected to operate the unloading mechanism to reduce the capacity of the compressors 1A and 1B by half. On the other hand, the inflow port _P1 and the switching port _P2 are communicated with each other to disable the unloading mechanism and to operate the compressors 1A and 1B at full capacity.

Reference numeral 18A is a startup load reduction valve that is operated to reduce the load applied to the motor when the compressor 1A is started, and is interposed in the discharge pipe 14 using an inflow port and one switching port, and is inserted into the discharge pipe 14 using an inflow port and one switching port. is connected to the low pressure side of the compressor 1A, and at startup, the discharge port of the compressor 1A is short-circuited to the low pressure side to reduce the load, and during normal operation, the discharge port of the compressor 1A is connected to the control valve 12. It has the function of a three-way valve.

Note that this starting load reduction valve 18A uses a pilot pressure operating valve and is associated with a three-way solenoid valve 19A for operation, and by connecting the pilot port to the high pressure side by switching the three-way solenoid valve 19A. By connecting to the low pressure side during normal operation, it is possible to correspond to load reduction operation.

20A and 20B are accumulators interposed in the suction pipe, and 21 is a dryer, which is a well-known device installed in a general refrigeration circuit.

The heat source side heat exchangers 3A and 3B are formed by two cross fin coils 3A- ₁ , 3A- ₂ and 3B- ₁ , 3B- _2, respectively, and in particular, the heat source side heat exchangers of the first refrigeration system A are Exchanger 3A- ₁ , 3A
- ₂ is connected to one heat source side heat exchanger 3A- ₁ in accordance with the unloading of the compressor 1A in order to prevent the high pressure from rising abnormally during hot water supply-only operation in the summer.
Alternatively, this control controls to stop the fan of 3A- ₂ , suppressing the high pressure rise by reducing the capacity of the heat source side heat exchanger that acts as an evaporator, and also reduces the refrigeration capacity in conjunction with unload control. We are trying to reduce it to about 25%.

In addition, since the heat source side heat exchanger 3A is divided into two, two heating pressure reducers, 4A- ₁ and 4A- ₂ , and two check valves, 6A- ₁ and 6A- _2, are used. ing.

Automatic expansion valves are used for the pressure reducers 4A- ₁ , 4A- ₂ and the cooling pressure reducer valve 5A, and the temperature sensing tube 3
3, 34 and 32 as shown in _FIG .
- Attached to the gas pipes connected to _{each of} the temperature sensing tubes 32
is attached to the gas pipe connected to the first refrigerant passage 9A.

Further, the pressure reducer valves 4A- ₁ and 4A- ₂ are connected to the discharge pressure or the gas pipes connected to the respective heat source side heat exchangers 3A- ₁ and 3A- ₂ via the three-way solenoid valves 22 and 22 for each pressure equalizing pipe. The internal refrigerant pressure is switched and supplied, and during cooling operation and cooling hot water supply operation, discharge pressure is supplied to force the valve to close, and during other operations, evaporation pressure is supplied and the original automatic expansion valve is closed. I am trying to make it function as.

On the other hand, the cooling pressure reducer 5A is configured to switch and supply the discharge pressure or the refrigerant pressure in the gas pipe connected to the first refrigerant passage 9A to the pressure equalizing pipe via the three-way solenoid valve 28, and is exclusively used for heating. The valve is forcibly closed during operation and hot water supply-only operation, and functions as an original automatic expansion valve during other operations.

The circuit including the solenoid valve 23 and the check valves 24 and 35 is a control circuit for refrigerant recovery, and the solenoid valve 23 is opened during cooling hot water supply operation to close the heat source side heat exchanger 3.
The refrigerant in A- ₁ and 3A- ₂ is recovered into the system.

The circuit connected in series with the solenoid valve 25 and the check valve 26 is also a control circuit for refrigerant recovery, and when the solenoid valve 25 is opened for both hot water supply and heating and hot water supply operations, the first solenoid valve 25 is opened.
The refrigerant in the refrigerant passage 9A is recovered into the system.

The circuit including the solenoid valve 29 and the check valves 30 and 31 is also a control circuit for refrigerant recovery, and is used exclusively for cooling.
During both heating-only operations, the solenoid valve 29 is opened and the refrigerant in the hot water supply heat exchanger 10 is recovered into the system.

Although each member for control has been described above, various forms of the control valve 12 can be used as long as it has a function as a three-way valve.
The device shown in FIG. 2 uses a general-purpose four-way switching valve, the main part of which is shown in _FIG . The inflow port _P1 is connected to the discharge side of the compressor 1A, the switching port _P2 is connected to the hot water supply heat exchanger 10, and the switching port _P3 is connected to the four-way switching valve 2A.

By switching the pilot three-way solenoid valve 37, the discharged gas is sent to the hot water supply heat exchanger 10 or the four-way switching valve 2A.

The solenoid valve 27 is opened for about 10 seconds when the control valve 12 is switched to ensure that the spool moves reliably and smoothly.

The operation mode of the apparatus shown in _FIG .
By lowering the capacity of one of the compressors 3A- ₂ and unloading the compressor 1A, an abnormal rise in high pressure can be prevented, and the operating range can be expanded to include cooling at the same time.

The present invention has the above-mentioned configuration and function, and has two refrigerant circuits, a hot water heat exchanger built into one system, and four-way switching valves 2A and 2B.
Since five operating modes can be operated by operating the control valve 12, there is no need for any other energy source other than the refrigerator for hot water supply; the system is entirely electric, and only requires two piping for heating and cooling. This simplifies the device.

In particular, this invention is ideal for use in all seasons because it detects the water temperature at the cold/hot water inlet and the hot water temperature and automatically switches between five modes for appropriate operation.

Furthermore, in the case of combined cooling and hot water supply operation, the waste heat released from the heat source side heat exchanger 3A can be used as a hot water heat source, so the overall capacity can be increased by 150% due to the heat recovery effect.
The running cost is significantly reduced compared to the conventional method.

As described above, the present invention is a heat pump air-conditioning/heating water heater that exhibits various excellent effects and is most suitable as a central heating device.

[Brief explanation of drawings]

Figure 1 is a basic refrigeration circuit diagram according to the present invention, Figure 2
The figure is a detailed diagram of a refrigeration circuit according to an example of the present invention, and FIG. 3 is a mechanical diagram of the control valve in FIG. 2. A...First refrigeration system, B...Second refrigeration system, 1A,
1B...Compressor, 2A, 2B...Four-way switching valve, 3
A, 3B...Heat source side heat exchanger, 4A, 4B...Heating pressure reducer, 5A, 5B...Cooling pressure reducer, 6
A, 6B, 7A, 7B...Check valve, 8...Using side heat exchanger, 9A...First refrigerant passage, 9B...Second
Refrigerant passage, 10... Heat exchanger for hot water supply, 11... Liquid receiver, 12... Control valve, 14... Discharge gas pipe, 1
6...High pressure liquid pipe.

Claims (1)

[Scope of utility model registration request] 2 of the first refrigerant passage 9A and the second refrigerant passage 9B
A user side heat exchanger 8 having a refrigerant system and a compressor 1
A, a four-way switching valve 2A, an air-type heat source side heat exchanger 3A, a heating pressure reducer 4A with a check valve 6A connected in parallel, and a cooling pressure reducer 5A with a check valve 7A connected in parallel. and a first refrigeration system A that includes the first refrigerant passage 9A as an element and is formed into a reversible heat pump refrigeration cycle that can be switched between cooling operation and heating operation.
A compressor 1B, a four-way switching valve 2B, an air-type heat source side heat exchanger 3B, a heating pressure reducer 4B with a check valve 6B connected in parallel, and a cooling device with a check valve 7B connected in parallel. pressure reducer 5B and the second refrigerant passage 9
A second refrigeration system B is formed into a reversible heat pump refrigeration cycle capable of switching between cooling operation and heating operation, and a hot water supply heat exchanger 10 and a hot water supply heat exchanger 10 respectively provided in relation to the first refrigeration system A. The control valve 12 connects the discharge port of the compressor 1A to the inlet port of the four-way selector valve 2A during the cooling cycle and the heating cycle, and connects the outlet of the compressor 1A to the inflow side port of the four-way switching valve 2A during the hot water supply cycle, and connects the discharge port of the compressor 1A to the inlet port of the four-way switching valve 2A during the hot water supply cycle. The hot water supply heat exchanger 10 is connected to the hot water supply side port of the control valve 12, the heating pressure reducer 4A, and the cooling pressure reducer 5A. A refrigerant side passage is interposed in the high pressure pipe 15 which is provided so as to communicate with the inlet side only during hot water supply operation, and the first refrigeration system A is connected to the four-way switching valve 2A.
switching operation to the heating side or cooling side, switching operation of the control valve 12, and the cooling pressure reducer 5A.
Alternatively, by forcibly closing the heating pressure reducer 4A, the hot water supply heat exchanger 10 acts as a condenser, the heat source side heat exchanger 10 acts as an evaporator, and the first refrigerant passage 9A is disabled. The first hot water supply operation can be switched to the first hot water supply operation using the refrigeration cycle, in which the first refrigerant passage 9A acts as an evaporator, and the second hot water supply operation using the refrigeration cycle, in which the heat source side heat exchanger 3A is inactive. Refrigeration system A and second refrigeration system B operate in the same cycle for cooling only and heating only, first refrigeration system A performs hot water only in the first hot water supply operation, and first refrigeration system A performs the second hot water supply operation in the second hot water supply operation. Possible to operate in 5 modes: cooling hot water supply operation that combines cooling operation of refrigeration system B, and heating hot water supply operation that combines the first hot water supply operation of first refrigeration system A with heating operation of second refrigeration system B. A heat pump air-conditioning/heating/water heater that is characterized by the following.