JPS6217574A - Composite type heat pump device - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

Detailed Description of the Invention (Industrial Field of Application) The present invention uses a plurality of heat exchangers as condensers or evaporators depending on the purpose, thereby converting atmospheric heat, solar heat,
A composite heat pump device that can effectively utilize various heat sources such as geothermal heat or waste heat in parallel, and can also be used in various forms simultaneously and effectively on the heat utilization side. Regarding.

(Conventional technology) In recent years, heating, cooling, and hot water systems have become popular as part of measures to improve livability, and along with this, research and development of total systems that incorporate multifunctional heat pump devices are progressing.

In other words, simultaneous operation of air conditioners in multiple rooms, addition of hot water supply functions, multi-use of heat sources (in addition to air heat sources, use of ground water, solar heat collected hot water, recovered waste heat, etc.), and multi-use of heat sources (simultaneous use of multiple heat sources) heat source).

(Problems to be Solved by the Invention) However, in conventional heat pump devices of this type (see, for example, Japanese Unexamined Patent Publication No. 59-138868, etc.), the configuration of the refrigerant circuit becomes complicated due to the multiplication of functions. However, since a considerable number of on-off valves and expansion valves for circuit switching are required, there are still considerable disadvantages in terms of cost and equipment.

Moreover, it is difficult to properly control the refrigerant flow rate to each heat exchanger, resulting in a decrease in efficiency. In particular, by improving the valve function, we not only can appropriately control the flow rate of refrigerant to each heat exchanger depending on the function, but also make the configuration of the refrigerant circuit more compact.

The purpose of this invention is to improve the above-mentioned problems as much as possible by reducing the number of valves installed.

Means for Solving the Problems> For this reason, the present invention branches into a plurality of refrigerant passages from the middle of the discharge side refrigerant passage of a compressor, and after passing through two heat exchangers each functioning as a condenser and an evaporator, In a composite heat pump device comprising a plurality of refrigerant branch passages that are finally gathered together and connected to the suction side refrigerant passage of the compressor, in the middle of the passage connecting the two heat exchangers of each refrigerant branch passage. are assembled in one place, and each passage connecting the gathering point and each heat exchanger is provided with a control valve that can adjust the opening from fully closed to fully open, and has the functions of opening/closing, controlling the refrigerant flow rate, and expanding the refrigerant. The configuration is as follows.

The refrigerant discharged from the compressor flows into the refrigerant branch passage from the middle of the discharge side refrigerant passage, passes through the heat exchanger that functions as a condenser, and then controls the flow rate by fully opening or adjusting the opening. The refrigerant is returned to the compressor via a valve and a control valve that throttles and expands the refrigerant by narrowing its opening (the control valves may be arranged in the reverse order), and then a heat exchanger that functions as an evaporator.

By switching the opening and closing of each control valve and adjusting the opening degree, it is possible to perform variable control of the heat exchange capacity by switching the refrigerant flow path and controlling the refrigerant flow rate.

<Example> Embodiments of the present invention will be described below based on the drawings.

In FIG. 1, a plurality of refrigerant branches are branched from the middle of a discharge side refrigerant passage 2 of a compressor 1 for compressing refrigerant via radial connectors 3, and then converged at one place via a radial connector 4. Routes 5A to 5D (hereinafter, the generic number 5 will be used unless otherwise specified) are provided.

In addition, branching from the middle of each of the refrigerant branch paths 5A to 5D;
A suction side refrigerant passage 7 to the compressor 1 via the connector 6
A plurality of refrigerant branch paths 8A to 8D for refrigerant return that merge with the
(Hereinafter, the generic number 8 will be used unless there is a particular distinction). A liquid storage device (accumulator) 9 is interposed in the suction side refrigerant passage 7.

In the portion of each refrigerant branch passage 5A to 5D from the branch point with the discharge side refrigerant passage 2 to the branch point with the refrigerant branch passage 8A to 8D,
On-off valves 9A to 9D are interposed, and on-off valves 10A to IOD are interposed in the refrigerant branch paths 8A to 8D.

Moreover, the refrigerant branch paths 8A to 5D of the refrigerant branch paths 5A to 5D are
Connector 4 (all refrigerant branches 8A to 8) from the branch point with 8D
Heat exchangers 11A to 11L are installed in the portions leading to the assembly point D, respectively.
Control valves 12A to 12D having ID and functions described below are sequentially installed.

Furthermore, heat exchangers 11A to IID and control valves 12A to 12
The refrigerant branch paths 5A to 5D between the refrigerant and the liquid receivers 13A to 13D and the check valves 1 that only allow flow from the heat exchangers 11A to 11D in the direction of the control valves 12A to 12D
4A to 14D, and the check valves 14A to 14D.
14D and a passage section in which check valves 15A to 15D are interposed in the opposite direction is provided in parallel.

In addition, if a liquid receiver is not provided, there will be one passage without a check valve.

As shown in FIG. 2, the heat exchanger 11A is installed in the indoor heat exchange unit 21, and the heat exchanger 11B is installed in the hot water storage tank
Inside, the heat exchanger 11C is disposed in a first outdoor heat exchange unit 23 that uses outside air as a heat source, and the heat exchanger 11D is disposed in a second outdoor heat exchange unit 24 that uses groundwater as a heat source. , the function as a condenser or an evaporator can be switched by switching the on-off valves 9A-9D, IOA-IOD, and adjusting the opening degrees of the control valves 12A-12D.

FIG. 3 shows the control valves 12A to 12D (hereinafter generically numbered 1).
2) and shows the structure and various opening positions.

In the figure, the control valve 12 includes a cylindrical housing 12a in which the refrigerant branch passages 5 on the inflow side and the outflow side of the refrigerant face each other and are opened in the peripheral wall. A cylindrical valve body 12b is fitted into the inner circumferential wall so as to freely slide (including 360 degrees) around the axis. The housing 1 is attached to the valve body 12b.
Valve holes 12c are formed in the openings on both sides of the valve body 12b so as to overlap at a predetermined rotational position and extend through the valve body 12b in a direction perpendicular to the rotation axis thereof.

One opening end of the valve hole 12c has an opening area enlarged by a slit 12d formed by cutting one circumferential side of the valve body 12b in the radial direction of the valve body 12b, and the other opening end Although the opening area can be expanded by the slit 126 formed by cutting the same side in the circumferential direction in the radial direction, the slit 12d is formed larger than the slit 12e.

When the valve body 12b is set to the position shown in FIG. 3, the axis of the valve hole 12c coincides with the axis of the refrigerant branch passage 5, and is fully opened.

As shown in FIG. 3, when the valve body 12b is set to an intermediate opening degree, the flow rate of the refrigerant can be controlled according to the opening degree.

At the position of the valve body 12b shown in FIG. 30, the opening is narrowed to a very small degree, so that the refrigerant flowing out from the slit 12e expands.

At the valve body 12b position shown in FIG. 3, the valve hole 12c is completely blocked and is fully closed.

Next, the operation of this embodiment will be explained using various usage examples and with reference to FIGS. 4 to 6 (only the refrigerant flowing portions are numbered).

i) When heating the room and heating the hot water tank 22 in winter (
(See FIG. 4) The on-off valves 9A and 9B are open, the on-off valves 9C to 9D are closed, the on-off valves 10A and IOB are closed, and the on-off valves 10C and IOD are open. In addition, the control valves 12A and 12B are set to the expansion positions shown in FIG. Ru.

In this case, the refrigerant discharged by the compressor 1 is transferred from the discharge side refrigerant passage 2 to the refrigerant branch passage 5 where the on-off valves 9A and 9B are opened.
It branches into A and 5B and flows into it. After passing through the heat exchangers 11A, IIB, liquid receivers 13A, 13B, check valves 14A, 14B, and control valves 12A, 12B installed in these refrigerant branch paths 5A, 5B, the refrigerant is once connected to the connector 4. After merging, the refrigerant branches and flows into refrigerant branch paths 5C and 5D.

The refrigerant that has flowed into the refrigerant branch paths 5C and 5D passes through the control valve 12C.
, 12D, check valve 15C, 15D, heat exchanger 11C91
1D, the refrigerant flows into the refrigerant branch paths 8C and 8D with the on-off valves 10C and IOD opened, joins the suction side refrigerant path 7 via the connector 6, and returns to the compressor 1 via the liquid storage container 9. It will be done.

At this time, each heat exchanger 11A, IIB in the indoor heat exchange unit 21 and the hot water storage tank 22 functions as a condenser, and each heat exchanger in the first and second outdoor heat exchange units 23 and 24 functions as a condenser. The vessels 11C and IID function as evaporators.

Therefore, heat is absorbed from the outside air and groundwater by the heat exchangers 11C and IID on the outdoor side, and the heat exchanger 1 on the indoor side
The room is heated by the heat radiated from the heat exchanger 11A, and the hot water tank 22 is heated by the heat radiated from the heat exchanger 11B.

ii) When performing indoor heating and defrost operation to melt frost on the first outdoor heat exchange unit using the outside temperature as a heat source (see Fig. 5), the hot water storage tank 22. Second outdoor heat exchange unit 24
In some cases, heat is absorbed from at least one of the hot water storage tanks 22, but a case where heat is absorbed only from the hot water storage tank 22 will be described below.

Open the on-off valves 9A, 9C, IOB, on-off valves 9B, 9D,
IOD is closed, control valves 12A and 12C are in expanded position,
Control valve 12B is fully opened, and control valve 12D is fully opened.

The refrigerant discharged from the compressor 1 branches from the connector 3 and flows into the refrigerant branch paths 5A and 5C, as shown by the arrow in FIG. 5, and then flows from the connector 4 into the refrigerant branch path 5B.
The refrigerant is returned to the compressor 1 via the refrigerant branch 8B.

Therefore, the heat exchanger 11B absorbs heat from the hot water tank 22, and the heat exchanger 11A performs indoor heating, while the heat exchanger 11C functioning as a condenser absorbs heat from the first outdoor heat exchange unit 23. The frost that adheres to the surface is melted.

iii) When performing indoor cooling and hot water supply (see Figure 6; however, the second outdoor heat exchange unit is not used as a heat source) Open the on-off valves 9B, IOA, and IOC, and open the on-off valves 9A,
9C, 9D, IOB, and IOD are closed, the control valve 12B is set to the expanded position, and the control valves 12A and 12C are set to the intermediate opening degree.

The refrigerant discharged from the compressor 1 flows from the connector 3 into the refrigerant branch path 5B as shown by the arrow in FIG. The refrigerant is returned to the compressor 1 through the 8C1 suction side refrigerant passage 7.

Therefore, the heat exchangers 11A and IIC absorb heat from inside and outside the room to cool the room, and at the same time, the heat exchanger 11B heats the hot water tank 22 and supplies hot water (however, hot water is supplied to the hot water tank 22). The water temperature is at a certain level, for example 40-50
).

In this way, each on-off valve 9A to 9D and on-off valve 10A to I
By combining the opening and closing of the OD and adjusting the opening of the control valves 12A to 12D, the four heat exchangers can be switched to a wide variety of modes.At the same time, by adjusting the refrigerant flow rate, heating, cooling, hot water supply (hot water tank heating) capacity can also be controlled.

In particular, as a configuration according to the present invention, the control valves 12A to 12D
Because it has the functions of an on-off valve, a flow rate control valve, and an expansion valve, the number of installed valves and the number of pipes are significantly reduced, reducing pressure loss due to refrigerant flow resistance and improving heat pump efficiency. It is advantageous in terms of space and cost, and improves reliability.

In addition, since the control valves 12A-12D have an opening/closing function,
Any configuration is sufficient as long as the refrigerant branch paths 5A to 5D and the refrigerant branch paths 8A to 8D are selectively opened and closed. Therefore, as shown in FIG. 25 may be provided.

For example, if the three-way valve 25 is installed at the branch point between the refrigerant branch path 5A and the refrigerant branch path 8A and the heat exchanger 11A is to function as a condenser, the three-way switching valve 25 should be set to the position (2) in FIG. In order to function as an evaporator, the three-way switching valve 25 may be set to the position (3) in FIG. 7, and the control valve 12A may be set to the fully open or intermediate opening position. In addition, when the heat exchanger 11A is not operated, the control valve 12A is fully closed, and the three-way switching valve 2
5 may be set to the prisoner position in Figure 7 or the 0 position.

In this way, the number of valves installed can be further reduced, which is advantageous in terms of valve operation and cost.

The opening/closing valves and control valves may be operated manually, but a control device may be provided so that they are automatically operated depending on the mode. In this case, both the hardware and software of the valve opening/closing control system are simplified. be converted into

In addition, if a separate heat exchanger is attached to a combined heat pump device that is unitized except for the heat exchanger, etc., or in combination with multiple units via separately provided multi-piping, etc., depending on the application. You can choose a lean system.

Furthermore, in this embodiment, each of the heat exchangers 11A to 110 is configured to be able to switch between the functions of a condenser and an evaporator.
It is also possible to have only one of the functions.

In this case, if it functions only as a condenser, the refrigerant branch connected to the suction side refrigerant passage and the on-off valve installed therein, the passage that bypasses the liquid receiver, and the two check valves are unnecessary. becomes. In addition, since the refrigerant branch path can be opened and closed only by the control valve, the on-off valve installed in the refrigerant branch path between the discharge side refrigerant passage and the heat exchanger can also be omitted (however, if the refrigerant capacity is large) (It is better to install an on-off valve.)

In addition, when functioning only as an evaporator, the receiver and two check valves can be omitted, and a refrigerant branch path connecting the discharge side refrigerant path and the heat exchanger and an on-off valve interposed therein, The on-off valve installed in the refrigerant branch path connected to the suction side refrigerant passage can be omitted.

FIG. 8 shows another embodiment of the control valve, that is, the control valve 31 has a housing 31a interposed in the refrigerant branch passage 5, and the inside of the housing 31a is perpendicular to the axial direction of the refrigerant branch passage 5. and a valve body 31b that slides.
A notch 31c is formed in the center of one end edge. The figure shows the fully open state, ■ indicates the intermediate opening, O indicates the expanded position, and ■ indicates the fully closed state. In these positions, the control of the first embodiment is performed. It has the same function as valve 12.

<Effects of the Invention> As explained above, according to the present invention, the passages connecting the two heat exchangers interposed in each refrigerant branch in a combined heat pump device are gathered at one place, and A control valve is installed between the assembly point and each heat exchanger, which has the functions of opening/closing, controlling refrigerant flow rate, and expanding refrigerant.
In addition to appropriately controlling the refrigerant flow rate to each heat exchanger according to its function, the overall number of valves installed is significantly reduced, and the piping configuration is significantly more compact, reducing installation space and lowering costs. can be significantly promoted.

Furthermore, when automatically controlling valve opening/closing operations, the hardware and software are greatly simplified and can be used not only for residential use but also for industrial systems, and the above advantages become more pronounced as multiplication progresses. .

[Brief explanation of the drawing]

Fig. 1 is a perspective view showing the refrigerant flow path configuration of one embodiment of the present invention, Fig. 2 is a sectional view showing the overall structure of the same embodiment, and Figs. 4 to 6 are diagrams showing the flow paths of the refrigerant in various usage conditions of the above embodiment, and Fig. 7 (2) and e are partially modified versions of the above embodiment. FIG. 8 is a sectional view showing each switching position of a control valve according to another embodiment. 1...Compressor 2...Discharge side refrigerant passage 3.4
... Connector 5A to 5D ... Refrigerant branch path 8
A to 8D... Refrigerant branch path 9A to 9D... On-off valve 10A to IOD... On-off valve 11A to IID...
Heat exchangers 12A to 12D... Control valve 31... Control valve Patent applicant Misawa Homes Co., Ltd. Agent Patent attorney Fujio Sasashima Figure 1A Figure 5 9A Figure 6 Figure 7 $8F = deceased 1a C

Claims (1)

[Claims] The refrigerant branches into a plurality of parts from the middle of the refrigerant passage on the discharge side of the compressor, passes through two heat exchangers each functioning as a condenser and an evaporator, and finally gathers and is connected to the refrigerant passage on the suction side of the compressor. In a composite heat pump device comprising a plurality of refrigerant branch passages, the passages connecting the two heat exchangers of each refrigerant branch passage are brought together at one place, and the assembly point and each heat exchanger are connected to each other. A composite heat pump device characterized in that a control valve is installed in each of the connecting passages, the opening degree of which can be adjusted from fully closed to fully open, and which has the functions of opening/closing, controlling refrigerant flow rate, and expanding refrigerant.