JP2614798B2 - Combined heat pump device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a combined heat pump device capable of simultaneously performing a plurality of heatings having different set temperatures in parallel.

[0002]

2. Description of the Related Art In recent years, air conditioning and hot water supply systems have become widespread as part of measures to improve comfort, and accordingly, research and development of a multifunctional heat pump system have been advanced.

[0003]

However, this type of conventional heat pump device (for example, Japanese Patent Application Laid-Open No. 59-138)
868)), various functions such as cooling and heating, hot water supply, etc. are diversified, but each of these functions operates independently, for example, heating and heating of a hot water storage tank are simultaneously effective. It is practically impossible to perform a plurality of functions simultaneously, such as performing the functions in parallel.

[0004] In the above example, this means that the flow rate and temperature of the refrigerant to the heat exchanger performing the heating function and the heat exchanger performing the hot water storage function (both operating as a condenser) are appropriately controlled. Because they cannot do it. Therefore, in a conventional heat pump device or the like that requires a large number of heat exchangers, there is a limit to multifunctionality, and the effect has not been sufficiently expected.

The present invention has been made in view of such a conventional situation, and variably controls the ratio of the flow rate of refrigerant to a plurality of heat exchangers used as a condenser to thereby control the flow rate around the heat exchanger. It is an object of the present invention to provide a combined heat pump device capable of performing control according to a temperature state and heating with a different set temperature.

[0006]

SUMMARY OF THE INVENTION Therefore, a composite heat pump apparatus according to the present invention includes at least a condenser in a composite heat pump apparatus including three or more heat exchangers and connected in a circulating manner to form a heat pump cycle. A plurality of heat exchangers used simultaneously as a heat exchanger are connected in parallel with each other, and are branched from the discharge side of the compressor when at least two of the plurality of heat exchangers are condensing. a refrigerant passage leading to the refrigerant inlet side of, coagulation of heat exchanger
The heat exchanger connected to the downstream side during evacuation
Refrigerant on the refrigerant inlet side and refrigerant outlet side during the evaporation operation
A passage and a refrigerant control valve whose opening can be freely adjusted continuously from fully closed to fully open are respectively provided.

[0007]

The refrigerant discharged from the compressor is supplied to a plurality of heat exchangers connected in parallel that operate as a condenser via a refrigerant control valve. Here, the discharge pressure of the compressor can be variably controlled by adjusting the opening of the refrigerant control valve. For example, by narrowing one refrigerant control valve from the opening degree of the other refrigerant control valve, the discharge pressure of the compressor can be increased, and the condensation point of the heat exchanger connected to the other refrigerant control valve can be reduced by one. It is relatively higher than the condensation point connected to the refrigerant control valve. In this way, heating control with different set temperatures can be performed.
Also, at this time, the heat exchanger operating as the condenser
Cooling of the heat exchanger connected downstream and operating as an evaporator
Refrigerant control installed in the refrigerant passage on the medium inlet side and the refrigerant outlet side
The opening of the valve can be adjusted according to the surrounding temperature.
This allows for more precise control according to temperature conditions
It can be performed.

[0008]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. In FIG. 1 showing the overall configuration of one embodiment, four first refrigerant branch passages 3A to 3D branching to a compressor 1 for refrigerant compression from the middle of a discharge side refrigerant passage in four directions (when not particularly distinguished below). Use the generic number 3. The same applies to the other numbers 4 to 9) are connected to one ends of the heat exchangers 4A to 4D, respectively. Each of the first refrigerant branch passages 3A to 3D has a refrigerant control valve 5A to 5D having a structure and function described later.
Is interposed.

At the other end of each of the heat exchangers 4A to 4D,
The second refrigerant branch passages 6A to 6D are connected to each other, and the other ends are connected to each other and connected. Refrigerant control valves 7A to 7D having the same structure and function as described above are also interposed in the second refrigerant branch passages 6A to 6D. In addition, the refrigerant control valves 5A to 5D of the first refrigerant branch passages 3A to 3D and the heat exchangers 4A to 4D.
The other end of each of the third refrigerant branch passages 8A to 8D branched from between the first refrigerant passage 4D and the fourth refrigerant branch 4D is connected to the suction-side refrigerant passage 10 of the compressor 1. Each third
The refrigerant branch passages 8A to 8D are also provided with refrigerant control valves 9A to 9D having the same structure and function as described above. An accumulator 11 is interposed in the suction-side refrigerant passage 10.

FIG. 2 shows the structure and various opening positions of the refrigerant control valve. However, the refrigerant control valve 7 interposed in the second refrigerant branch passage 6 is shown, but other refrigerant control valves 5, 9
The same applies to. In the drawing, a refrigerant control valve 7 has a cylindrical housing 7a in which the second refrigerant branch passages 6 on the inflow side and the outflow side of the refrigerant oppose each other and is opened on the peripheral wall, and is free to slide around an inner peripheral wall of the housing 7a. (Including 360 °)
And a cylindrical valve element 7b fitted into the valve body. Valve element 7
A valve hole 7c penetrating in a direction orthogonal to the rotation axis of the valve body 7b is formed in the opening b on both sides of the housing 7a so as to overlap at a predetermined rotation position.

One open end of the valve hole 7c is provided with a valve body 7
The opening area is increased by a slit 7d formed by cutting one side in the circumferential direction of b in the radial direction of the valve body 7b, and the other open end is also formed by cutting the same side in the circumferential direction in the radial direction. Although the opening area can be increased by the slit 7e, the slit 7d is formed larger than the slit 7e.

When the valve body 7c is set at the position shown in FIG. 2A, the axis of the valve hole 7c coincides with the axis of the second refrigerant branch passage 6, and is fully opened. As shown in FIG. 2 (B), the valve element 7b
Is set to the intermediate opening, the flow rate of the refrigerant can be connected according to the opening. At the position of the valve element 7b shown in FIG. 2 (C), the opening degree is reduced to a very small degree, whereby the refrigerant flowing out of the slit 7e expands.

At the position of the valve body 7b in FIG.
Is completely shut off and fully closed. In each of the refrigerant control valves 5, 7, and 9 having such a structure and function, a stepping motor (not shown) is connected to an end of the valve body, and the valve body is driven to rotate by the motor. Further, a temperature sensor 12A for detecting a temperature around each of the heat exchangers 4A to 4D.
To 12D are provided, and temperature signals from these temperature sensors 12A to 12D are input to the control unit 13,
Operates a predetermined heat exchanger from among the four heat exchangers 4A to 4D as a condenser and operates a predetermined heat exchanger as an evaporator according to the application by a resident operating a changeover switch (not shown). As well as these heat exchangers 4A-
Refrigerant control valves 5, 7, 9 so that the heat exchange capacity of 4D is adjusted according to the temperature detected by the temperature sensors 12A to 12D.
Of the refrigerant control valves 5, 7, and 9 are controlled.

The total number of operating modes of the heat pump cycle using the four heat exchangers is 50.
Representative operating modes (applications) are listed and described.
FIG. 3 shows the degree of opening of the heat exchanger and each refrigerant control valve in these various embodiments. [A]: One in which two heat exchangers, for example, the heat exchangers 4A and 4B are used for an indoor cooling / heating unit and one heat exchanger 4C is used for an outdoor heat source unit (the heat exchanger 4D is not operated).

A-1: Heating in Two Rooms Simultaneously (When Heating Capacity is Fully Opened) The refrigerant control valves 5A and 5B of the first refrigerant branch 3 are fully opened (FIG. 2).
(A) position), and the refrigerant control valves 5C and 5D are fully closed (FIG. 2).
(D) position), the refrigerant control valves 7A, 7 of the second refrigerant branch 6
B is in the expansion position (FIG. 2 (C) position), the refrigerant control valve 7C is fully opened, the refrigerant control valve 7D is fully closed, the refrigerant control valves 9A and 9B of the third refrigerant branch 8 are fully closed, and the refrigerant control valves 9C and 9C 9D is controlled to be fully open.

At this time, as shown by arrows in FIG. 4A, the refrigerant discharged from the compressor 1 is supplied from the discharge side refrigerant passage 2 to the first refrigerant branch passages 3A, 3A with the refrigerant control valves 5A, 5B opened.
B flows into the heat exchangers 4A and 4B on the indoor side, radiates heat in the heat exchangers 4A and 4B, condenses, and heats each room. After that, the refrigerant flows out into the second refrigerant branch passages 6A and 6B, is expanded and vaporized by the refrigerant control valves 7A and 7B, respectively, then merges once and flows into the second refrigerant branch passage 6C, where the heat exchanger 4C
And heat is absorbed from outside air in the heat exchanger 4C to evaporate. Further, the first refrigerant branch 3C to the third refrigerant branch 8
C, flows into the suction-side refrigerant passage 10, and accumulators
It is returned to the compressor 1 via 11.

A-2: Regarding the function of each heat exchanger, A-
1 but the refrigerant control valve 5 in the first refrigerant branch 3
When A and 5B are set at an intermediate opening (position (FIG. 2B)) to control the heating capacity to an appropriate level, the refrigerant circulation circuit is the same as A-1, but the refrigerant control valve 5
By setting A and 5B to the intermediate opening degree, the flow rate of the refrigerant is controlled, and the heat exchange capacity of each of the heat exchangers 4A and 4B is controlled to perform appropriate heating.

The switching between A-1 and A-2 can be performed artificially. In this embodiment, however, the temperature sensors 12A,
Based on the signal from 12B, for example, while the room temperature is low, A-1
After the room temperature has risen, the refrigerant control valves 5A and 5B can be automatically controlled so as to maintain the appropriate temperature by adjusting the opening of the valves 5A and 5B. A-3: When cooling two rooms simultaneously (when the cooling capacity is fully opened) Refrigerant control valves 5A to 5C, 9A to 9C of first refrigerant branch 3
Opening and closing of the refrigerant control valve 7C
Is in the expansion position, and the refrigerant control valves 5D, 7D, 9D are fully closed.

The circulation circuit of the refrigerant is as shown by an arrow in FIG. 4 (B), and the indoor heat exchangers 4A and 4B operate as evaporators to cool the interior of the room, and as an outdoor condenser. The heat is radiated from the activated heat exchanger 4C. A-4: In the case of A-3, when the cooling capacity is appropriately set with the refrigerant control valve 5C at the intermediate opening [B]: As shown in FIG. 7, one heat exchanger 4A is connected to the indoor cooling / heating unit. Use one heat exchanger 4B for hot water tank
A heat exchanger 4C installed in the inside 22 and one heat exchanger 4C used for an outside air heat source unit 23 using outside air as a heat source, and one heat exchanger 4D used for a groundwater heat source unit 24 using groundwater (well water) as a heat source B -1: When performing indoor heating and hot water tank heating using outside air and groundwater as heat sources (when the difference between the indoor temperature and the water temperature in the hot water tank 22 is small) The refrigerant control valves 5A and 5B of the first refrigerant branch 3 are fully opened. The refrigerant control valves 5C and 5D are closed, the refrigerant control valves 7A and 7B of the second refrigerant branch 6 are in the expansion position, the refrigerant control valves 7C and 7D are fully open, and the refrigerant control valves 9A and 9A of the third refrigerant branch 8 are open. 9B is closed,
The refrigerant control valves 9C and 9D are fully opened.

The refrigerant circulation circuit is as shown by the arrow in FIG. 5C, and the heat exchangers 4C and 4D which operate as evaporators.
To absorb heat from the outside air and the groundwater, respectively, and to heat the indoor and hot water storage tanks using heat exchangers 4A and 4B that operate as condensers.
22 heatings are performed. B-2: Indoor heating and hot water tank heating are performed, but when the room temperature is higher than the hot water tank 22 (for example, heating is performed first to
When heating the hot water storage tank 22 from a cold water state while maintaining the temperature at about 20 ° C.) The difference from B-1 is that the first refrigerant branching to the heat exchanger 4B of the hot water storage tank 22 The point is that the refrigerant control valves 5C and 7D of the second refrigerant branch paths 6C and 6D leading to the heat exchangers 4C and 4D functioning as evaporators have the intermediate opening degrees.

The refrigerant circuit is the same as in the case of B-1, but the flow rate of the refrigerant to the heat exchanger 4B in the hot water storage tank 22 increases. That is, since the temperature in the hot water storage tank 22 is low, the refrigerant flowing into the heat exchanger 4B is easily condensed, and the condensing pressure is lower than the condensing pressure of the indoor side heat exchanger 4A under the condition of B-1. (See FIG. 8A). For this reason, the heat exchanger 4 in the hot water storage tank 22 remains open with the refrigerant control valve at the B-1 condition.
The refrigerant flow to the indoor heat exchanger 4A decreases in contrast to the increase in the refrigerant flow to B, and the pressure of the refrigerant (gas) discharged from the compressor 1 due to the low refrigerant condensation pressure of the heat exchanger 4B. Combined with the temperature drop, the heating capacity of the heat exchanger 4A is sharply reduced.

Accordingly, the refrigerant control valve 5B is throttled to an intermediate opening to prevent a decrease in the condensing pressure of the heat exchanger 4B in the hot water tank 22, thereby preventing a decrease in the discharge pressure of the compressor 1. This allows
A decrease in the flow rate and pressure of the refrigerant to the indoor side heat exchanger 4A is suppressed, and a simultaneous operation of heating and heating of the hot water storage tank 22 can be effectively performed while suppressing a decrease in the heating capacity. B-3: Contrary to B-2, when heating is started at a low room temperature (for example, 5 ° C) when the water temperature in the tank during heating the hot water storage tank 22 is as high as 50 ° C or more, Conversely, the refrigerant control valve 5A of the first refrigerant branch 3A leading to the indoor heat exchanger 4A is set to an intermediate opening degree, and the refrigerant control valve 5B reaching the heat exchanger 4B in the hot water storage tank 22 is fully opened.

For the same reason as described in B-2, simultaneous operation of heating and hot water tank heating can be effectively performed. In each of the embodiments described above, only the case where the refrigerant control valve 5D is always closed is shown. If the refrigerant control valve 5D is used only in such a mode, the refrigerant control valve 5D and the passage (the compressor 1) Discharge side, first refrigerant branch 3D and third refrigerant branch 8
A passage portion connecting the connection point with D) can be omitted. Also,
The refrigerant control valves 9A to 9D are also shown only for the case of opening / closing operation. If the refrigerant control valves 9A to 9D are used only in such a mode, an on / off valve having only an opening / closing function may be used instead of the refrigerant control valve capable of controlling the opening degree. .

[C]: Two heat exchangers 4A and 4B are each used for an indoor cooling and heating unit, one heat exchanger 4C is used in a hot water tank, and one heat exchanger 4D is used for an outside air heat source unit. C-1: When heating is performed at night in winter, when only outside air is used as a heat source and the heating capacity is insufficient, when the heating temperature in the hot water tank is used as a heat source to supplement the heating capacity, each refrigerant is used. The opening of the control valve is as shown in FIG. 3C, and the refrigerant circulation circuit is as shown by the arrow in FIG. 5 (D).

In this case, the refrigerant control valve 7C and the heat exchanger 4C in the second refrigerant branch 6C reaching the heat exchanger 4C in the hot water tank.
The opening degree of the refrigerant control valve 9C of the third refrigerant branch passage 8C flowing out of the outlet is defined as an intermediate opening degree. That is, when the refrigerant control valves 7C and 9C before and after the heat exchanger 4C are fully opened, the temperature of the hot water is higher than that of the outside air, so that the evaporation capacity of the heat exchanger 4C is higher than that of the heat exchanger 4D for the outside air heat source. Since it is larger than that (see FIG. 8 (B)), heat is mainly absorbed by the hot water storage tank, and the temperature of the hot water in the hot water storage tank is significantly reduced.

Therefore, as in the present embodiment, the refrigerant control valve 7
By setting C and 9C to the intermediate opening, the flow rate of the refrigerant to the outdoor heat exchanger 4D is relatively increased, and the heat absorption from the outside air is mainly performed, and the heat absorption from the hot water is supplementarily performed. Suppress large temperature drop. C-2: When simultaneous cooling is performed in the chambers and heating of the hot water tank is stopped, the refrigerant control valves 5A, 5B and 5C are fully closed, the refrigerant control valves 7A and 7B are in the expansion position, and the refrigerant control valve 7C is fully closed. ,
The refrigerant control valve 7D is fully open, the refrigerant control valves 9A and 9B are fully open,
The refrigerant control valves 9C and 9D are fully closed.

The refrigerant circulation circuit is as shown by an arrow in FIG. 6 (E). The indoor heat exchangers 4A and 4B operate as evaporators to cool each room, and as a condenser outside the room. The heat is released from the operating heat exchanger 4D. C-3: One of the rooms is equipped with a computer, for example. Even in winter, air conditioning is performed to suppress the temperature rise due to the heat generated by the computer, and the other room is an office room or the like and is heated. When the heating of the hot water tank is stopped, the heat absorption from the computer is large and it is necessary to radiate the heat outside the room. However, when the heating capacity is to be increased as much as possible, the refrigerant control valve 5A is completely closed, The control valve 5B is fully open, the refrigerant control valve 5C is fully closed, the refrigerant control valve 5D is at an intermediate opening, the refrigerant control valves 7A and 7B are in the expansion position, and the refrigerant control valve 7C
Is fully closed, the refrigerant control valve 7D is fully open, the third refrigerant branch 9A is fully open, the refrigerant control valve 9B is fully closed, the refrigerant control valve 9C is fully closed,
The refrigerant control valve 9D is fully closed.

The refrigerant circuit is as shown by the arrow in FIG. 6 (F). The heat exchanger 4A in the room where the computer is installed operates as an evaporator, and the heat exchanger 4B in the office room condenses. The heat exchanger 4D operates as a condenser and performs heating, and at the same time, radiates heat from the heat exchanger 4D that operates as an outdoor condenser. Next, an embodiment applied to a refrigerating / warming apparatus using three heat exchangers will be described.

As shown in FIG. 9, the circuit configuration of the heat pump device is the same as that shown in FIG. Heat exchanger 4A, 4B
As shown in FIG. 10, two thermally refrigerated storage
The heat exchangers 4C are provided inside the storage chambers 31 and 32, respectively, and the heat exchanger 4C is provided outside to absorb heat or release heat from the outside.

Reference numeral 33 denotes a unit including a compressor, each refrigerant control valve, and the like. The operation of this will be described. Refrigeration of both refrigeration and warming rooms 31, 32 (including cold source)
When operating: The refrigerant control valves 5C, 7A, 7B, 9A, 9B are opened, the refrigerant control valve 7C is in the expansion position, and the refrigerant control valves 5A, 5B, 9C are closed.

The refrigerant circulation circuit in this case is as shown by an arrow in FIG. 7, and the heat exchangers 4A, 4A,
The inside of the refrigeration / warming chambers 31 and 32 is cooled by 4B to absorb heat, and is radiated to the outside by the heat exchanger 4C operating as a condenser. In this case, the temperature sensors 34, 35 are provided in both chambers 31, 32, respectively.
By adjusting the opening of the refrigerant control valve based on the detected temperature, the cooling capacity can be controlled by controlling the flow rate of the refrigerant. For example, control can be performed so as to eliminate the temperature difference between the two chambers 31, 32, or it can be controlled so as to positively have a temperature difference (for example, one of them is frozen).

When one of the refrigeration / warming chambers 31 is refrigerated and the other refrigeration / warming chamber 32 is refrigerated, especially when it is desired to ensure a high refrigeration capacity, the heat exchanger 4C
The refrigerant control valves 5B, 7
A, 9A are fully opened, the refrigerant control valve 7B is in the expansion position, and the refrigerant control valves 5A, 5C, 7C, 9B, 9C are in the closed position.

When it is desired to increase the refrigerating capacity relatively (for example, during a freezing operation), the refrigerant control valves 5B, 5C, 7A, 9A are opened, the refrigerant control valves 7B, 7C are in the expansion positions, and the refrigerant control valves 5A, 9
B and 9C are closed. That is, the two heat exchangers 4B and 4C
Is operated as a condenser, heat is radiated to one of the refrigeration / warming chambers 32 and the outside to enhance the heat radiation capacity, and the other refrigeration / warming chamber 31 is operated.
Increase the cooling capacity of the. In this case, the cooling capacity can be controlled by adjusting the opening of the refrigerant control valve.

When the two refrigerating / warming chambers 31, 32 are operated for warming, the refrigerant control valves 5A, 5B, 7A, 7C, 9C are in the expansion position, and the refrigerant control valves 5C, 9A, 9B are closed. The two refrigerating / warming chambers 31 and 32 are absorbed and cooled by the heat exchangers 4A and 4B, and radiated to the outside by the heat exchanger 4C. Also in this case, by controlling the opening degree of the refrigerant control valve in accordance with the two chambers 31, 32, it is possible to equalize the temperatures of the two chambers 31, 32 or to control the temperature so as to have a positive temperature difference. The same is true.

Although the case where four heat exchangers are used and the case where three heat exchangers are used have been described above, it is needless to say that more heat exchangers can be added depending on the application. FIG. 11 shows another embodiment of the refrigerant control valve. That is, the refrigerant control valve 41 includes a housing 41a interposed in the refrigerant branch passage, for example, the first refrigerant branch passage 3, and a valve body that slides in the housing 41a perpendicular to the axial direction of the first refrigerant branch passage 3. A cut 41c is formed at the center of one end edge of the valve element 41b.
2A shows a fully open position, FIG. 2B shows an intermediate opening degree, FIG. 2C shows an expanded position, and FIG. 2D shows a fully closed position. In these positions, functions similar to those of the refrigerant control valve of the first embodiment are shown. Having.

The two types of refrigerant control valves described above have low resistance to the flow of the refrigerant, thereby improving the operation efficiency and reducing the operating cost.

[0037]

As described above, according to the present invention,
In the combined heat pump device, a refrigerant control valve whose opening degree can be freely adjusted is interposed in a refrigerant passage leading to a plurality of parallel-connected heat exchangers functioning as a condenser, so that heating control is performed simultaneously and in parallel. By controlling the degree of opening of each refrigerant control valve, the operation of the heat exchanger can be operated in the most balanced and favorable mode according to the surrounding temperature condition, or controlled to a different set temperature. Can be.

[Brief description of the drawings]

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

FIG. 2 is a sectional view showing each switching position of the refrigerant control valve applied to the embodiment.

FIG. 3 is a diagram showing each operation example of a system using the apparatus of the embodiment, a heat exchanger function, and an opening degree of a refrigerant control valve.

FIG. 4 is a diagram showing a refrigerant circuit in each operation example of the above.

FIG. 5 is a diagram showing a refrigerant circuit in each operation example of the above.

FIG. 6 is a diagram showing a refrigerant circuit in each operation example of the above.

FIG. 7 is a sectional view showing an example of a system using the apparatus of the embodiment.

FIG. 8 is a Mollier diagram of a condensation operation heat exchanger and an evaporation operation heat exchanger when the temperature difference is large.

FIG. 9 is a refrigerant circuit diagram according to a second embodiment of the present invention.

FIG. 10 is a system diagram of the embodiment.

FIG. 11 is a cross-sectional view showing various switching positions of another embodiment of the refrigerant control valve.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Compressor 2 Discharge side refrigerant passage 3A-3D 1st refrigerant branch 4A-4D Heat exchanger 5A-5D, 7A-7D, 9A-9D, 41 Refrigerant control valve 6A-6D 2nd refrigerant branch 8A-8D 3 refrigerant branch passage 10 suction side refrigerant passage

Claims (1)

(57) [Claims] In a combined heat pump apparatus including three or more heat exchangers and circulated to form a heat pump cycle, at least a plurality of heat exchangers simultaneously used as a condenser are connected in parallel to each other. disposed Te, a refrigerant passage leading to the refrigerant inlet side branches from the discharge side of the compressor when the condensation operation of at least two heat exchangers of said plurality of heat exchangers, condensing operation of these heat exchangers Sometimes downstream
Of the heat exchanger which is connected to
A composite heat pump device characterized in that the refrigerant passages on the refrigerant inlet side and on the refrigerant outlet side are provided with a refrigerant control valve whose opening degree can be continuously adjusted from fully closed to fully open.