JP2008185276A - Heat pump type hot water supply apparatus - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve a COP by lowering the uppermost pressure of a coolant side to a predetermined pressure or less without enlarging a heat exchanger. <P>SOLUTION: The heat pump type hot water supply apparatus is comprised by providing a refrigeration cycle composed by sequentially connecting a compressor 1, a first water-coolant heat exchanger 2, an expansion valve 3, an evaporator 4, and a second water-coolant heat exchanger 6, an aqueduct 8 sending water to the first water-coolant heat exchanger 2, a tank 10 storing water sent by the aqueduct 8 and heated by the first water-coolant heat exchanger 2, and a circulation passage 12 circulating water between the first water-coolant heat exchanger 2 and the second water-coolant heat exchanger 6, and dissipating heat obtained in the first water-coolant heat exchanger 2 in the second water-coolant heat exchanger 6. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a heat pump type water heater using, for example, carbon dioxide as a refrigerant.

  As this type of heat pump type hot water heater, one that enables efficient heat exchange by flowing water and a refrigerant in a counterflow and that improves performance efficiency (hereinafter referred to as COP) is known ( For example, see Patent Document 1.)

By the way, generally, at the time of water-refrigerant heat exchange, the temperature change history of water and the temperature change history of the refrigerant are different, and a minimum temperature difference occurs between them.
JP-A-1-193561

  However, at present, the above-mentioned minimum temperature difference is about 1.5 ° C., and in order to further reduce this, it is necessary to enlarge the heat exchanger considerably.

  Of course, regardless of the size of the heat exchanger, the high-pressure side pressure of the carbon dioxide refrigerant cannot be lowered below the pressure at which the minimum temperature difference becomes 0 ° C., and the coefficient of performance (COP) There was a limit to improvement.

  The present invention has been made paying attention to the above circumstances, and the object of the present invention is to use a first water-refrigerant heat exchanger to remove a part of the temperature change history on the water side without causing heat loss. To provide a heat pump type hot water heater capable of improving the COP by reducing the high pressure on the refrigerant side below a predetermined pressure without increasing the size of the heat exchanger by slightly changing the heat exchanger. is there.

  In order to solve the above-mentioned problems, the invention according to claim 1 is configured by sequentially connecting a compressor, a first water refrigerant heat exchanger, an expansion valve, an evaporator, and a second water refrigerant heat exchanger. A refrigeration cycle, a water supply path for supplying water to the first water refrigerant heat exchanger, a tank for storing water supplied by the water supply path and heated in the first water refrigerant heat exchanger, Water is circulated between the first water refrigerant heat exchanger and the second water refrigerant heat exchanger, and the heat obtained by the first water refrigerant heat exchanger is converted into the second water refrigerant heat exchanger. And a circulating water channel to be discharged at the same time.

  According to the present invention, the coefficient of performance (COP) can be improved without increasing the size of the water-refrigerant heat exchanger.

Hereinafter, the present invention will be described in detail with reference to embodiments shown in the drawings.
(First embodiment)
FIG. 1 shows a configuration of a refrigeration cycle of a heat pump type water heater according to an embodiment of the present invention, and carbon dioxide is used as a refrigerant.

  The refrigeration cycle includes a compressor 1, and the compressor 1 is sequentially provided with a first water refrigerant heat exchanger 2, an expansion valve 3, an evaporator 4, an internal heat exchanger 5, and a first through a refrigerant pipe 13. 2 water refrigerant heat exchangers 6 are connected.

  A water flow path 8 as a water supply path is inserted into the first water refrigerant heat exchanger 2. A pump 7 is provided on the upstream side of the first water refrigerant heat exchanger 2 in the water flow path 8, and a tank 10 is connected on the downstream side.

  Further, the first water refrigerant heat exchanger 2 and the second water refrigerant heat exchanger 6 are connected via a circulation water channel 12. A pump 9 that circulates water along the arrow is provided in the middle of the circulation channel 12.

  FIG. 2 shows the configuration of the first water refrigerant heat exchanger 2.

  The first water-refrigerant heat exchanger 2 includes a refrigerant pipe 13 and a water flow path 8 joined to the upper surface side of the refrigerant pipe 13, and the water flow path 8 includes an outlet portion 8a and an inlet portion 8b. Is provided. The circulating water channel 12 has one end connected to the outlet 8a of the water channel 8 and the other end connected to the inlet 8b.

In the above-described configuration, when the compressor 1 is driven, carbon dioxide gas that is a refrigerant is compressed and discharged, and is sent to the first water-refrigerant heat exchanger 2. The refrigerant gas sent to the first water-refrigerant heat exchanger 2 is radiated and then sent to the evaporator 4 via the internal heat exchanger 5 and the expansion valve 3. The refrigerant liquid sent to the evaporator 4 absorbs heat and evaporates, and then is sucked into the compressor 1 through the internal heat exchanger 5 and the second heat exchanger 6 and compressed. 8 pump 7 and circulating water channel 12 pump 9 are respectively operated. With the operation of the pump 7, water is sent along the water flow path 8 to the first water refrigerant heat exchanger 2, and is heated by the high-pressure refrigerant gas flowing along the refrigerant pipe 13 in the first water refrigerant heat exchanger 2. The hot water is then stored in the hot water storage tank 10. In addition, due to the operation of the pump 9, a part of the hot water heated by the first water refrigerant heat exchanger 2 is sent from the water channel 8 to the second heat exchanger 6 through the circulation channel 12. The refrigerant gas is heated by the hot water sent to the second heat exchanger 6 and then sucked into the compressor 1 and compressed.

  By the operation of the pump 9 described above, the water flow rate changes in a part of the first water refrigerant heat exchanger 2, thereby changing a part of the temperature change history of the water.

  FIG. 3 shows, for convenience, the state of temperature change of the water refrigerant when the high-pressure side pressure of the refrigerant is the same, as compared with the conventional case.

  As can be seen from FIG. 3, in the present invention, the temperature change history of the water can be made gentler than that of the conventional type, and the inflow temperature on the refrigerant side can be increased by heat recovery, resulting in a minimum temperature difference between the water and refrigerant. It can be apparently enlarged.

  This means that in the case of the same water refrigerant minimum temperature difference, the high-pressure side pressure can be lowered, and the COP can be improved accordingly.

  FIG. 4 shows the improvement rate of COP when the circulating water flow rate circulating through the circulating water channel 12 is 30% of the main flow rate flowing through the water flow channel 8.

  A COP of 4.7 can be obtained with respect to COP4.5 of the conventional example.

  In addition, the branch inflow temperature ° C in FIG. 4 is the inflow temperature of warm water in the A part of FIG.

  FIG. 5 shows the improvement rate of the COP with respect to the ratio of the circulating water flow rate (main water flow rate / circulating water flow rate) during high-temperature heating in winter.

  The pump 9 in the circulation channel 12 may be controlled at a constant water flow rate from the viewpoint of cost. However, as shown in FIG. 5, there is a flow rate ratio at which the improvement rate of COP is improved. More preferably, the water flow rate of the main pump 7 is detected and the pump 9 is controlled so that the ratio with the flow rate is constant.

  As described above, according to this embodiment, the temperature change history of the water in the water flow path 8 in the first water-refrigerant heat exchanger 2 is partially moderated, and the inflow temperature on the refrigerant side is reduced by heat recovery. Can be high. Therefore, there is an advantage that the minimum temperature difference between the water refrigerant can be apparently increased, and the coefficient of performance (COP) can be improved by lowering the high-pressure side pressure.

  FIG. 6 shows a configuration example of a first water refrigerant heat exchanger 2A which is another embodiment of the present invention.

  In the first water refrigerant heat exchanger 2A, the water flow path 8 is joined to the upper surface portion side of the refrigerant pipe 13, and the circulating water passage 12 is joined to the lower surface portion side.

  In this embodiment, the water flowing in the water channel 8 and the water flowing in the circulation channel 12 are heated by the high-pressure refrigerant gas flowing in the refrigerant pipe 13 to become hot water.

  Note that the present invention is not limited to the above-described embodiment as it is, and can be embodied by modifying the constituent elements without departing from the scope of the invention in the implementation stage. Various inventions can be formed by appropriately combining a plurality of constituent elements disclosed in the above-described embodiments. For example, you may delete some components from all the components shown by embodiment mentioned above. Furthermore, you may combine the component covering different embodiment suitably.

The figure which shows the refrigerating cycle of the heat pump type water heater which is one embodiment of this invention. The figure which shows the 1st water-refrigerant heat exchanger of the refrigerating cycle of FIG. The graph which shows the temperature change log | history of the water and the refrigerant | coolant in the 1st water refrigerant | coolant heat exchanger of FIG. 2 compared with the past. The graph which shows the improvement effect of a coefficient of performance (COP). The graph which shows the relationship between a coefficient of performance (COP) and a circulating water flow rate ratio. The figure which shows the 1st water-refrigerant heat exchanger which is other embodiment of this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Compressor, 2 ... 1st water refrigerant heat exchanger, 3 ... Expansion valve, 4 ... Evaporator, 6 ... 2nd water refrigerant heat exchanger, 8 ... Water supply path, 10 ... Tank, 12 ... Circulation water path .

Claims (1)

A refrigeration cycle configured by sequentially connecting a compressor, a first water refrigerant heat exchanger, an expansion valve, an evaporator, and a second water refrigerant heat exchanger;
A water supply channel for supplying water to the first water refrigerant heat exchanger;
A tank for storing water supplied by the water supply passage and heated by the first water refrigerant heat exchanger;
Water is circulated between the first water refrigerant heat exchanger and the second water refrigerant heat exchanger, and heat obtained by the first water refrigerant heat exchanger is exchanged with the second water refrigerant heat exchanger. A heat pump type hot water heater comprising: a circulating water channel that is discharged by a water heater.

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