JP2010197030A - Heat pump hot water supply system utilizing solar heat - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a system capable of dispensing with double equipment of a boiler and the like, collecting heat from the outside of a system even in cloudy and rainy weather in winter, simplifying a system constitution, and improving costs, construction performance and maintenance performance. <P>SOLUTION: A heat collection-side heat exchanger 2 has the outer shape in which peaks and troughs are continuously formed at least at its outdoor side, a selective absorption film 2d is formed on a surface, and a refrigerant flow channel 2e is formed along an inclined section 2c connecting at least peaks 2a and troughs 2b inside. The heat collection-side heat exchanger 2 has a structure configured by vertically stacking two sheets of moldings obtained by molding metal into the corrugated shape, at least a part of the peak facing the outdoor side is thickened, and a number of refrigerant flow channels 2e in parallel with the inclined section 2c are formed between the inclined section 2c of the upper corrugated plate and the inclined section 2c of the lower corrugated plate. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a system for collecting heat from the heat of outside air (natural wind) in addition to solar heat in a solar water heating hot water supply system using a heat pump water heater. More specifically, a solar-powered heat pump hot water supply system that sends a refrigerant that contributes to heating and cooling by changing the gas-liquid phase to the roof of the building, and that can collect heat from natural winds even during cloudy rainy weather in winter due to its evaporation characteristics The present invention relates to an operation method that enables the system to be operated effectively and stably.

  10 to 13 show examples of the background art. FIG. 10 shows a solar water heater + auxiliary boiler system in which a solar heat collecting section with a glass surface on the roof surface, and a hot water tank, a heat collecting pump, and an auxiliary boiler are installed on the ground. During the day, a water pump as a heat collecting pump is operated to collect solar heat in a hot water tank using water as a medium. When solar heat is insufficient or at night, the hot water supply temperature is maintained with an auxiliary boiler.

  FIG. 11 shows a heat pump water heater system using a natural refrigerant as a heat source. Here, the heat pump water heater main body and hot water storage tank are installed on the ground. The heat pump water heater main body includes an air heat exchanger that forcibly vents outside air as a heat collecting side heat exchanger, and evaporates the refrigerant to pump up heat from the outside air. This system is often operated with inexpensive nighttime power in order to reduce operating costs. For example, carbon dioxide is used as the natural refrigerant. Conventional fluorocarbon refrigerants can only heat water up to about 50 to 60 ° C., but carbon dioxide can be heated up to about 90 ° C. and is used for hot water supply. A heat pump water heater using such a natural refrigerant has been jointly developed by an electric power company and a water heater manufacturer, and is marketed as “Ecocute (registered trademark)”.

  FIG. 12 shows a combination of a solar water heater and a heat pump water heater, and the hot water storage tank has a flow path communicating with the condenser of the solar water heater and the heat pump water heater.

  FIG. 13 shows a system called a parallel solar heat pump (in this case, which collects heat indirectly using air rather than directly using refrigerant), which was implemented by Toshiba Corporation in 1985. It is a heat pump used at the same time. When directly collecting heat with a refrigerant in this system, a solar heat collecting part is installed on the roof surface as an evaporator of the heat pump, and fins for collecting heat from outside air are attached to the back of the heat collecting part. A ventilation fan is installed in the attic, and the outside air is forcibly ventilated through the outside air passage on the back surface to pump heat from both solar energy and outside air. Since the heat collection temperature is lower than that of the solar water heater in the winter and intermediate periods, there is an advantage that the heat collection efficiency is higher than that of the above-described aqueous medium method.

  In addition to the system shown in FIGS. 10 to 13, there are the following as prior arts related to the present invention.

Japanese Utility Model Publication No.57-17262 Japanese Patent Publication No.57-55991 JP 59-217451 Japanese Patent Publication No. 3-32708 Japanese Utility Model Publication No.59-79772 JP-A-1-134164

  However, in the system of FIG. 10, since the hot water supply temperature is lower than the heat collection temperature, solar heat cannot be used sufficiently in the winter and intermediate periods, and it is necessary to catch up with an auxiliary boiler. In addition, since water is used as a heat medium, it is necessary to replenish brine periodically as a countermeasure against freezing in winter and to be careful of dirt and corrosion inside the heat collecting section.

  In the system of FIG. 11, the fact that the nighttime outside air temperature is lower than that of the daytime, and that the heat production loss and hot water use time zone are separated and the heat dissipation loss from the hot water storage tank is large are factors that reduce operating efficiency. It has become. In addition, since hot water is stored by estimating the amount of hot water used the next day, the amount of hot water stored is excessive or insufficient depending on the amount of hot water used during the day. When the amount of hot water storage is insufficient, it is necessary to operate the heat source machine other than 23:00 to 7 o'clock, which is an inexpensive electricity bill.

In the system of FIG. 12, the heat collecting pump is operated during the day to store hot water by circulating water, and when the amount of hot water is insufficient, the heat pump water heater is used to catch up. There is no merit in collecting solar heat unless the water temperature is low. That is, there is the above-mentioned problem due to the restriction of using water as a heat medium.
In addition, since hot water heated by solar heat is chased during the day, the operating efficiency is lower than that of heating low-temperature tap water, and chasing with expensive daytime power does not necessarily reduce the operating cost.

  In the system shown in FIG. 13, the structure of the rear surface of the heat collecting unit is complicated, and there is room for improvement in cost, weight, and maintainability. Moreover, since the thickness of the heat collecting part is increased, there is still room for improvement in fixing to the roof base as a roofing material. In addition, it is necessary to pay attention to the soundproofing measures of the fan for ventilation and the treatment of condensed water from the back of the heat collecting part. In this system, an example of collecting heat from the outside air by natural ventilation has also been implemented. However, it is necessary to expose the back of the heat collecting part to the outside air, and it is installed independently on a flat roof of a commercial building. It is difficult to fix it to the roof base as a roofing material for a house.

  Regarding the panel, which is a member constituting the solar heat collecting part, the thickness to be taken into consideration when transporting from the factory or construction on the roof surface. 10 and 12 have a hollow layer, so that the thickness is about 50 mm. In the method of FIG. In terms of production, there was room for improvement in reducing the number of parts, such as glass for forming a hollow layer and metal fins for ensuring heat transfer performance in the back air flow path.

  The present invention eliminates the need for a backup heat source such as a boiler and other double facilities, enables heat collection from outside the system even in cloudy weather in winter, and has a simple system configuration, cost and workability. An object of the present invention is to provide a heat pump hot water supply system using solar heat with improved maintainability and an operation method thereof.

  In order to achieve the above object, according to the first aspect of the present invention, a heat-collecting-side heat exchanger of a heat pump water heater is separated from a main body and installed on a roof surface of a building, and the compressor and heat collecting of the heat pump water heater A refrigerant contributing to heating and cooling is circulated and circulated between the side heat exchanger and the refrigerant that contributes to heating and cooling, and the refrigerant in the gas-liquid two phase that has become low pressure is introduced to the heat collection side heat exchanger via a decompression device. On the other hand, on the heat utilization side of the heat pump water heater, the refrigerant is circulated and circulated between the compressor and the heat utilization side heat exchanger, and the refrigerant in the gas phase is increased in pressure by the compressor. To the heat utilization side heat exchanger to dissipate heat by condensing, and further circulate and circulate water between the heat utilization side heat exchanger and the hot water storage tank. The external shape is expressed as a shape in which at least the outdoor side is continuous with peaks and valleys. Internal is characterized in that to form a refrigerant flow path through which the coolant along the inclined portion connecting at least the peaks and valleys as well as selective absorption film processing, a solar thermal heat pump hot water system.

  Invention of Claim 2 is a solar-heat-use heat pump hot-water supply system of Claim 1, Comprising: The said heat collection side heat exchanger is comprised with the connection body of several sheets of a corrugated board whose height is 5-15 mm. The corrugated plates are each provided with a refrigerant inlet and outlet, and a large number of flat refrigerant flow paths are built in, the connections are connected in parallel, and the longitudinal direction of the corrugated plates is The coolant is installed so as to stand up toward the top surface of the roof, and the refrigerant inlet is disposed below the roof, and the refrigerant outlet is disposed on the roof top.

  The peaks and valleys of the corrugated plate may be acute or curved. From the viewpoint of ensuring the airtight pressure resistance performance of the heat collecting part and workability, the unit body (panel) that has passed the airtight pressure resistance test with two corrugated plates and two headers connected at the factory is applied to the roof at the construction site. It is desirable to lift and install. Here, the “longitudinal direction of the corrugated plate” means a direction orthogonal to the direction in which waves are formed (the direction in which the waves are undulated).

The invention described in claim 3 is the solar heat-use heat pump hot water supply system according to claim 1 or 2, wherein the surface side of the heat collecting side heat exchanger is formed by stacking two metal plates in a corrugated shape vertically. A large number of refrigerants parallel to the inclined portion between the inclined portion of the upper corrugated plate and the inclined portion of the lower corrugated plate by providing a thickness to at least the mountain portion facing the outdoors. It is characterized in that a flow path is formed.
Here, for example, in order to flow carbon dioxide, which is a high-pressure refrigerant, between the heat pump water heater and the heat-collecting side heat exchanger, it is possible to braze the refrigerant pipe using fire, It is necessary to conduct a hermetic pressure resistance test in order to ensure this, but it may be difficult to carry out these operations and tests at the work site. In that case, the high-pressure refrigerant piping system is completed inside the heat pump water heater, and the refrigerant and brine heat exchangers are added separately, so that the piping from the heat collection side heat exchanger to the heat pump water heater is connected to the low-pressure brine piping. It is also possible.

  According to a fourth aspect of the present invention, in the solar heat utilization heat pump hot water supply system according to any one of the first to third aspects, a refrigerant tank is provided in the heat pump water heater, and the refrigerant tank includes the decompression device and the heat collecting side heat. A refrigerant pipe located between the refrigerant inlet of the exchanger and returning from the heat collection side heat exchanger to the compressor and the refrigerant tank are connected by a bypass pipe, and a second decompression is connected to the bypass pipe. It is characterized in that the apparatus is arranged so that the refrigerant in the refrigerant tank is decompressed and sucked into the compressor.

According to a fifth aspect of the present invention, in the solar heat-use heat pump hot water supply system according to the fourth aspect, a valve is provided in each of the pipe line connecting the refrigerant tank and the refrigerant inlet of the heat collecting side heat exchanger and the bypass pipe. The operation method of the system configured as described above, after hot water of a predetermined temperature is accumulated in the hot water storage tank and the compressor is once stopped, the valve of the refrigerant inlet pipe of the heat collecting side heat exchanger is closed, The operation method of the solar heat-based heat pump hot water supply system is characterized in that the valve of the bypass pipe is closed and the compressor is operated again.
The invention according to claim 6 separates the heat-collecting-side heat exchanger of the heat pump water heater from the main body and installs it on the roof surface of the building, and the first heat exchanger and the second heat exchanger are installed inside the heat pump water heater. The heat pump hot water supply provided with a heat exchanger, circulating brine between the heat collection side heat exchanger and the first heat exchanger, and in which the compressor and the second heat exchanger are arranged Through the first heat exchanger, a refrigerant that is phase-changed into a gas-liquid two phase that can exchange heat with the brine is circulated and circulated in a refrigerant pipe in the machine, and the refrigerant is connected between the heat pump water heater and the hot water storage tank. It is a system for circulating and circulating water that can exchange heat with the refrigerant through a second heat exchanger, and the outer shape of the heat collecting side heat exchanger is at least as a shape in which the outdoor side is a continuous mountain and valley The selective absorption membrane is processed and the inside is at least before Along the inclined portion connecting the peaks and valleys, characterized in that the formation of the coolant channel in which the brine flows, a solar thermal heat pump hot water system.

  According to the first aspect of the present invention, even in the winter season or in cloudy weather, the refrigerant evaporating temperature is lower than that of the outside air and heat can be collected from the outside air, so that a double facility such as a backup heat source is not required. Further, when there is solar radiation, the evaporating temperature is higher than in the case described above, and heat can be collected from both outside air and solar heat, so the utilization efficiency of the heat pump is improved. Furthermore, since the shape of at least the surface (outdoor side surface) of the heat collection side heat exchanger ensures a sufficient surface area to pump out sufficient heat from the outside air, the heat collection side heat exchanger as a heat collecting part There is no need for a blower or wind path. It is possible to provide a system that is simple in configuration and improved in cost, workability, and maintainability.

  Since the system configuration is simple, cost reduction and workability can be improved, and maintainability can be facilitated. In addition, the size of the hot water tank can be reduced as much as hot water loss is reduced, contributing to space saving. In addition, even when frost is formed on the heat collection part during winter operation, it is possible to maintain a certain heating capacity without the possibility that the outside of the air will not pass due to the gap between the fins being blocked by frost unlike the air heat exchanger. The system can be operated effectively and stably.

  According to the second aspect of the present invention, rainwater can be allowed to flow as it is, and the heat collection side heat exchanger can be used as an alternative to the roofing material. The height of the wave (the difference between the heights of the peaks and valleys) is 5 to 15 mm. However, if the height is less than 5 mm, there is a problem that the workability of the corrugated plate and the header deteriorates, and the height exceeds 15 mm. This is because there is a problem that the thickness of the heat collecting side heat exchanger becomes too large. In addition, by flowing the refrigerant from the bottom to the top, the flow of the refrigerant having evaporated and reduced in density at the heat collecting side heat exchanger is promoted. Furthermore, by making the outer shape of the heat collecting side heat exchanger corrugated, a large section modulus for bending can be secured, and high strength against deformation can be obtained.

  According to invention of Claim 3, the corrugated board which formed the refrigerant | coolant flow path inside can be manufactured cheaply, without taking the effort of welding, for example. Moreover, a heat transfer area can be taken wide by comprising the whole inclination part which connects a peak and a valley as a refrigerant | coolant flow path. That is, in the system of the present invention, a gas / liquid phase change and a gas, which is a gas / liquid two-phase mixed gas of carbon dioxide that preferably contributes to heating and cooling, are circulated on the roof surface of the building as a heat collection site. If the liquid ratio (wetness) of the refrigerant in the flow is low, the difference in the inlet refrigerant flow rate increases between the flow path close to the compressor and the flow path far from the compressor, resulting in a difference in the refrigerant flow rate, and the heat transfer area of the entire heat collecting section However, it is assumed that the entire inclined portion connecting the peaks and valleys functions as a refrigerant flow path, so that the heat transfer area can be widened.

  According to the invention described in claim 4, when the distance between the heat collecting side heat exchanger and the compressor is relatively long, there is a concern about the difference in the flow rate of refrigerant and the flow velocity depending on the degree of wetness, Since the gas refrigerant in the upper part of the refrigerant tank is sucked into the compressor from the bypass pipe, the low-pressure liquid refrigerant can be stored in the lower part of the refrigerant tank. Therefore, it becomes possible to collect only the refrigerant with high wetness, and the liquid can be sent to the heat collecting side heat exchanger.

According to the fifth aspect of the present invention, the heat collected in the hot water storage tank is radiated through the heat utilization side heat exchanger during operation of the system. However, after the compressor stops, the refrigerant flow stagnates and there is no heat escape, and the refrigerant expands in the heat collection side heat exchanger. Because it is collected in the inside, there is no problem when the operation is resumed. That is, when hot water supply stops in midsummer, the temperature of the heat collecting section (evaporator) becomes 100 ° C. or higher, and there is a concern that the pressure of the refrigerant piping system increases and causes mechanical damage. Since the refrigerant is forcibly returned from the heat collecting side heat exchanger by the suction force of the machine, the occurrence of mechanical damage can be avoided.
According to the sixth aspect of the present invention, the heat for exchanging heat between the refrigerant and the brine is obtained in addition to the heat exchanger for exchanging heat between the refrigerant and water by completing the high-pressure refrigerant pipe in the heat pump water heater. Since an additional exchanger is added and the piping from the heat collecting side heat exchanger to the heat pump water heater is a low-pressure brine pipe, pipe brazing and an airtight pressure resistance test can be performed in a factory that manufactures the heat pump water heater. This eliminates the need for pipe brazing and an airtight pressure resistance test at the work site, and can increase work efficiency. In addition, the airtight pressure resistance required for the brine piping system is significantly lower than that of the refrigerant piping, so the conventional solar water heater construction technology can be diverted, and the airtight pressure resistance of the pipe between the heat pump water heater and the heat collection side heat exchanger Can be easily secured.
Similarly, by making the piping from the heat collection side heat exchanger to the heat pump water heater a brine pipe, the heat exchange efficiency is somewhat reduced due to the double heat collection side heat exchanger, but the refrigerant piping is a heat pump. Since it can be stored in the water heater, there is no possibility that the refrigerant in the refrigerant piping system will be extremely heated when the hot water supply operation is stopped in a high temperature environment such as a midsummer, and a mechanism for collecting the refrigerant becomes unnecessary.

1 is a configuration diagram of an entire system according to Embodiment 1 of the present invention. The block diagram of the heat-collection side heat exchanger which comprises the system which concerns on Embodiment 1 of this invention. It is sectional drawing of the header of the heat collecting side heat exchanger which comprises the system which concerns on Embodiment 1 of this invention, Comprising: It is sectional drawing which follows the AA line of FIG. Sectional drawing which looked at the header in the heat collecting side heat exchanger of FIG. 3 from another direction. It is sectional drawing of the header of the heat collection side heat exchanger which comprises the system which concerns on Embodiment 1 of this invention. The arrangement | positioning at the time of installing the heat collection side heat exchanger which comprises the system which concerns on Embodiment 1 of this invention on a roof surface. The block diagram of the heat pump water heater which comprises the system which concerns on Embodiment 1 of this invention. The operation | movement flowchart at the time of driving | operating the apparatus of FIG. The block diagram of the whole system which concerns on Embodiment 2 of this invention. The figure which shows the prior art of this invention. The figure which shows the prior art of this invention. The figure which shows the prior art of this invention. The figure which shows the prior art of this invention.

  1 to 8 show Embodiment 1 of the present invention. FIG. 1 shows the overall configuration of this system. As will be described later, the heat pump water heater 1 includes a compressor 1a, a heat utilization side heat exchanger (acting as a condenser) 1c, an expansion valve 1b as a pressure reducing device, a refrigerant pipe connecting them, a hot water tank 3 outside the machine, It is mainly comprised from the water pump 1p which circulates the water as a heat medium between heat utilization side heat exchangers 1c.

  The heat-collecting side heat exchanger 2 acts as a solar heat collector and will be described in detail with reference to FIG. 2. However, the heat collecting side heat exchanger 2 is installed so as to incline so that the longitudinal direction of the corrugated plate rises toward the top surface of the roof 5 of the building. ing. It receives sunlight and collects heat. Further, in the vicinity of the surface of the roof 5, wind with a wind speed of 0.5 to 1.0 [m / s] or more blows intermittently or constantly, so heat exchange between the outside air and the refrigerant C is performed over a wide surface area.

  The heat pump water heater 1 and the heat collecting side heat exchanger 2 are connected by a return refrigerant pipe, and the refrigerant C circulates in both systems. As the circulating refrigerant C, a refrigerant that changes the gas-liquid phase and contributes to heating and cooling is used, but it is desirable to employ natural refrigerant, particularly carbon dioxide, in terms of higher heating capacity than the chlorofluorocarbon refrigerant.

  The heat utilization side heat exchanger 1c of the heat pump water heater 1 is connected to the hot water storage tank 3 via a water pipe. More specifically, water is taken out from the lower part of the hot water tank 3 by the water pump 1p described above, condensed heat is obtained by the heat utilization side heat exchanger 1c, and returned to the tank. Further, the hot water storage tank 3 is provided with a pump 3a for sending the stored hot water to a hot water tap 4 as a heat load, and a water supply pipe for replenishing the shortage of consumed hot water is connected.

  Next, the structure of the heat collection side heat exchanger 2 will be described with reference to FIG. The outer shape is such that at least the outdoor side is continuous with peaks 2a and valleys 2b (the present invention can be established even if the indoor side is flat), and the surface is treated with a selective absorption film. The interior forms a refrigerant flow path 2e through which the refrigerant C flows along at least the slope portion 2c connecting the peaks and valleys. Moreover, a unit body is formed with a corrugated plate having a wave height (difference between the heights of peaks and valleys) of 5 to 15 mm, provided with an inlet and an outlet for the refrigerant C, and the number of the slope portions 2c is set inside. A number of corresponding flat refrigerant flow paths 2e are incorporated.

  Here, the outdoor side surface of the heat collecting side heat exchanger 2 has a structure in which two pieces of metal, which is a heat conductive member such as aluminum, copper, stainless steel, etc., which are formed into a corrugated shape, are stacked one above the other. That is, the outdoor side surface of the heat collecting side heat exchanger 2 has a structure in which the corrugated plate 21 and the corrugated plate 22 are stacked one above the other. By providing a thickness to at least the portion of the mountain that faces the outdoors, the slope 2c of the upper corrugated plate 21 and the slope 2c of the lower corrugated plate 22 are parallel to the slope 2c. A similar refrigerant flow path 2e is formed. Thereby, many refrigerant | coolant flow paths 2e are produced without taking the effort of welding. In addition, a trough is not necessarily required on the lower side (indoor side), and may be a trapezoidal bottom instead of a mountain.

  As the selective absorption film treatment, the selective absorption film 2d is formed by coating a special electrolytic film on the aluminum surface. In addition, as a suitable selective absorption film treatment means, black chromium is used for copper. Examples thereof include a plating method, a method of chemical conversion treatment of stainless steel, and a coloring method. And the heat insulating material 2f, such as glass wool, is affixed on the indoor side of the heat collecting side heat exchanger 2. With this configuration, it can be placed directly on the base material of the roof 5 such as roofing.

  The heat collection side heat exchanger 2 manufactured as described above has a height from the top of the mountain 2a to the bottom surface of the heat insulating layer of the heat insulating material 2f on the back surface of 30 to 50 mm, and the above-described conventional heat collecting panel described above. Thinner and easier to handle. In the present invention, by collecting heat with the refrigerant C, the temperature is lower than the heat collecting temperature in the case of water collecting, thereby reducing the hollow layer of the prior art, and collecting heat from outside air on the upper surface of the heat collecting part. The back air flow path of the prior art is reduced.

  The heat collection side heat exchanger 2 is disposed on the roof 5, preferably on the south surface of the roof 5, for example, as shown in FIG. 6. Here, the heat collecting side heat exchanger 2 (heat collecting part) has a 3 × 6 rectangular panel shape, and its longitudinal direction is placed on the roof base along the inclination direction of the roof. In the wave composed of the peaks 2a and the valleys 2b, the direction of wave propagation is perpendicular to the longitudinal direction of the panel, and the extending direction of the inclined portion 2c extends parallel to the longitudinal direction of the panel. Therefore, the refrigerant flow path 2 e formed on the back surface along the inclined portion 2 c is positioned in parallel to the inclination direction of the roof 5.

  The heat-collecting side heat exchanger 2 manufactured in a size of 3 × 6 by the above-described manufacturing method is formed as a unit and connected. In FIG. 5, five heat collecting side heat exchangers 2 as unit bodies are installed adjacent to each other to constitute a whole series of panels. As shown in FIG. 5, one end 22a and the other end 22b of the lower corrugated plate 22 are abutted. One end 21 a of the upper corrugated plate 21 is joined to the end 22 a of the lower corrugated plate 22 in an overlapping state. Similarly, the other end 21 b of the upper corrugated plate 21 is joined to the end 22 b of the lower corrugated plate 22 so as to overlap. On the end face side of the end portions 21a and 21b of the upper corrugated plate 21, seal margins 2m for sealing the joint surface with the lower corrugated plate 22 are formed so as to extend in parallel with the refrigerant flow path 2e. Yes.

  The arrangement of the heat collecting side heat exchangers 2 as a unit body and the flow relationship of the refrigerant C will be described below. Supply of the refrigerant | coolant C to each panel is performed in parallel seeing from the refrigerant | coolant outbound pipe | tube 2k1 from the heat pump water heater 1. FIG. More specifically, as shown in FIGS. 3 and 4, the refrigerant forward pipe 2k1 extends along the back surface of the roof base 5b. Then, the leading end side of the refrigerant forward pipe 2k1 is raised up to the surface of the roof 5 through the roof base 5b and the waterproof paper 5a, and the leading end of the raised refrigerant outgoing pipe 2k1 is connected to the refrigerant inlet 2j of the header 2g. To do. The header 2g is provided for each heat collection side heat exchanger 2 as a unit body. The header 2g has the same length along the short direction of the heat collecting side heat exchanger 2, and is provided adjacent to the heat insulating layer 2f. The headers 2g are connected to each other after being carried into the roof 5, and after the connection, the refrigerant inlet 2j of the header 2g is connected to the socket 2h.

  Here, the downstream end portion of the refrigerant forward pipe 2k1 is connected only to the refrigerant inlet 2j of the header 2g of the specific heat collecting side heat exchanger 2 among the plurality of heat collecting side heat exchangers 2, and is integrated after the connection. And is distributed in the longitudinal direction of the header 2g which has almost the same length as the aggregate of the heat collecting side heat exchangers 2.

  The socket 2h connected to the refrigerant outgoing pipe 2k1 has a bifurcated refrigerant outlet so as to distribute the refrigerant C to the refrigerant flow paths 2e of the left and right heat collecting side heat exchangers 2. Similarly, the outlet side of the refrigerant C is returned to the heat pump water heater 1 from the outlet side socket 2i arranged on the top surface side of the roof 5 through the outlet side header 2g and the refrigerant return pipe 2k2.

  In this way, the heat collecting side heat exchanger 2 is arranged in parallel when viewed from the refrigerant C, and the refrigerant flow path 2e is linearly supplied from the bottom toward the top surface of the roof 5, thereby reducing the low pressure of the refrigerant C. The effect of damage can be obtained. In addition, arranging the refrigerant C inflow port below the roof 5 and arranging the refrigerant C outflow port on the top surface side of the roof 5 evaporates the refrigerant C in the heat collecting side heat exchanger 2 and reduces the density of the refrigerant C. Facilitate. In addition, when the heat collecting side heat exchanger 2 is defrosted, a heat pump circuit to be described later is dealt with by reverse rotation operation. However, since the frost melting water flows along the slope of the roof 5 in the rain gutter, There is no risk of stagnation and refreezing.

  In the above configuration, when the solar radiation is strong, such as in midsummer, the evaporating temperature is increased by increasing the opening degree of the expansion valve 1b or decreasing the rotational speed of the compressor 1a, thereby reducing the power consumption of the heat pump water heater 1. To do. In addition, the set hot water temperature of the hot water tank 3 is desirably set to the minimum necessary temperature in order to reduce the condensing temperature and reduce the power consumption of the heat pump water heater 1. And when there exists a possibility that the pressure of the carbon dioxide piping system of the heat pump water heater 1 may rise excessively, the rotation speed of the compressor 1a is dropped or the compressor 1a is stopped.

  The heat collection side heat exchanger 2 can also be installed as an alternative to the roofing material. Although it is a part of the roof 5 in FIG. 3, you may install the heat collecting side heat exchanger 2 more than a required number for a design reason. In this case, if the capacity seems to be too high, the headers 2g of some of the unit bodies (panels) are not connected and used as a simple roofing material.

The minimum required number of panels used in the practice of the present invention can be determined by calculating the required surface area from the surface heat transfer coefficient according to the minimum wind speed expected on the roof surface and the amount of solar radiation in cloudy weather. For example, in the heat pump water heater 1 having a heating capacity of 4.5 kW, when the horizontal solar radiation amount is 50 [W / m ² ], the outside air temperature is 5 ° C., and the wind speed is 1 [m / s], the 3 × 6 panel is 4 It becomes ~ 6 sheets.

  The panel is sealed with a known sealing material, but it is convenient to provide notches on both end faces parallel to the refrigerant flow path 2e of the heat collecting side heat exchanger 2 as sealing margins.

  In the system according to the present invention, since the refrigerant is transported relatively far away, as described above, the refrigerant flow rate and flow velocity are biased depending on the site at the inlet portion of the heat collecting side heat exchanger 2, and the entire heat collecting side heat exchanger 2 is There is concern that it cannot be used effectively. Further, since the refrigerant is supplied to each of a large number of panels, the present inventors pay attention to the property of the supplied refrigerant C as a measure for improving the heat collection efficiency, and are liquid-rich even under reduced pressure through the expansion valve 1b. I came up with a gas-liquid two-phase flow. Therefore, an invention for dealing with this will be described with reference to FIG.

  A heat pump water heater 1 which is a heat source device according to the present invention includes a compressor 1a, an expansion valve 1b as a pressure reducing device, and a heat utilization side heat exchanger 1c acting as a condenser. Up to this point, in a known refrigeration cycle, the gas refrigerant that has been heated to high pressure and high pressure by the compressor 1a passes through the check valve 1i, dissipates heat in the heat utilization side heat exchanger 1c, and liquefies (the water in the hot water storage tank 3 at this time). The heat is sent to the heat collecting side heat exchanger 2 as a low-pressure gas-liquid two-phase refrigerant by the expansion valve 1b. In the figure, the compressor 1a appears in the middle of the pipe line from the heat utilization side heat exchanger 1c to the expansion valve 1b. However, this is for the convenience of drawing and the pipe line bypasses the compressor 1a. .

  In addition to this, the present invention includes a refrigerant tank 1d, a bypass pipe 1g, and a second decompression device 1h interposed in the bypass pipe 1g.

  The refrigerant tank 1d is positioned between the expansion valve 1b and the refrigerant inlet of the heat collecting side heat exchanger 2.

  The bypass pipe 1g is provided between the refrigerant pipe 1g returning from the refrigerant outlet of the heat collecting side heat exchanger 2 to the compressor and the refrigerant tank 1d.

  Note that the refrigerant tank 1d, the bypass pipe 1g, and the second decompression device 1h are not necessarily installed in the machine, and may be added to the outside of the machine as an installation facility for a commercially available heat pump.

  The flow of the refrigerant C in the configuration is as follows. The process is the same as before until the returned refrigerant C exits the expansion valve 1b. After the low-pressure gas-liquid two-phase refrigerant exiting the expansion valve 1b is discharged to the refrigerant tank 1d, only the gas refrigerant in the upper part of the refrigerant tank 1d flows into the bypass pipe 1g, and a cavity tube or the like interposed therebetween The pressure is reduced by the second pressure reducing device 1h. The outlet of the bypass pipe 1g merges with the refrigerant return pipe toward the compressor 1a, and is sucked into the compressor 1a as a gas refrigerant having high dryness, and this cycle is repeated. On the other hand, low-pressure liquid refrigerant is accumulated at the bottom of the refrigerant tank 1d, and this liquid refrigerant is sucked by the suction force of the compressor 1a from the take-out opening at the bottom of the tank and flows in the refrigerant forward pipe toward the heat collecting side heat exchanger 2. . That is, only a highly wet refrigerant can be collected and sent.

  Thereby, for example, it is possible to avoid the problem that a difference in the refrigerant inflow amount occurs due to an increase in the difference in the inlet refrigerant flow rate between the flow paths closer to the compressor 1a and the flow paths far from the compressor 1a.

  Furthermore, this invention provides the method of avoiding the damage accompanying the high pressure of the refrigerant | coolant inside a heat collecting part at the time of hot water supply stop in the high temperature environment like a midsummer. This will be described with reference to FIGS. First, as a device configuration, in addition to the device configuration shown in FIG. 4, two valves 1e and 1f (here, electromagnetic valves. It is preferable to use an automatic valve or a self-powered valve rather than a manual valve) around the refrigerant tank 1d. . These may also be provided outside the in-flight machine. The electromagnetic valve 1e is provided in a pipe line connecting the refrigerant tank 1d and the refrigerant inlet of the heat collecting side heat exchanger 2. The electromagnetic valve 1f is provided upstream of the second pressure reducing device 1h in the pipeline of the bypass pipe 1g.

  In the present invention, the refrigerant is removed from the heat collecting side heat exchanger 2 by returning the refrigerant C to the refrigerant tank 1d in the system having the above configuration. This operation will be described with reference to FIG. In particular, the operation corresponding to the problem is the “refrigerant recovery operation” in step S4.

  As shown in FIG. 8, in step S1, the operation of the solar heat utilization heat pump hot water supply system is started. Here, the operation start condition of the system is when the temperature detected by the temperature sensor T3 in FIG. 7 is 1 to 3 ° C. lower than the set hot water temperature. At the start of operation in step S1, the solenoid valve 1e in FIG. 7 is opened, and the compressor 1a is operated at the minimum capacity. At the start of operation, the opening degree of the expansion valve 1b is set to 20%, for example.

  Next, as shown in step S <b> 2, when a certain time has elapsed from the start of operation, the hot water storage operation is started, and hot water storage in the hot water storage tank 3 is started. The hot water start condition is set after 2 to 5 minutes have elapsed since the start of operation of the system. In the operation in step S2, the solenoid valve 1e in FIG. 7 remains open, and the compressor 1a is subjected to capacity control. This hot water storage operation is conditional on the temperature detected by the temperature sensor T3 in FIG. 7 being in the range of 1 to 3 ° C. with respect to the set hot water temperature. Further, the opening degree of the expansion valve 1b is controlled under a certain condition. That is, the degree of opening control of the expansion valve 1b is controlled when the difference between the temperature sensor T1 and the temperature sensor T2 in FIG. 7 is in the range of 2 to 5 ° C., or overheating calculated from the temperature sensor T2 and the pressure sensor P2 in FIG. It is performed when the degree is higher than 1 to 3 ° C.

  Step S3 indicates that the hot water storage operation is stopped. Here, the operation stop condition of the system is that the temperature detected by the temperature sensor T3 in FIG. 7 is 1 to 3 ° C. higher than the set hot water temperature. In step S3, the solenoid valve 1e in FIG. 7 is closed and the compressor 1a is stopped. The expansion valve 1b is set to the minimum opening.

  Step S4 shows the refrigerant recovery operation. The refrigerant recovery operation is performed by detecting the temperature from the temperature sensor T2 of the refrigerant pipe immediately adjacent to the suction port of the compressor 1a after a lapse of a fixed time after the compressor 1a is stopped (a state where hot water has accumulated). This fixed time ΔT is set shorter as the temperature of the temperature sensor T2 when the hot water storage operation is stopped is higher. For example, when the temperature of the part is 40 ° C., the predetermined time ΔT is about 10 minutes.

  In step S4, when the stop state of the compressor 1a continues after the lapse of the predetermined time ΔT, the electromagnetic valve 1e for sending the refrigerant from the refrigerant tank 1d to the heat collecting side heat exchanger 2 is closed, and the expansion valve 1b is fully opened and the compressor 1a is fully operated. At this time, the solenoid valve 1f is opened. Then, the refrigerant C is forcibly returned from the heat collecting side heat exchanger 2 by the suction force of the compressor 1a, and the refrigerant C accumulates in the refrigerant tank 1d as a liquid.

  And as shown to step S5, a refrigerant | coolant collection | recovery driving | operation stops on the following conditions. That is, when the pressure in the portion P2 of the refrigerant pipe in the immediate vicinity of the suction port of the compressor 1a falls below 0.2 to 0.3 MPa, it is determined that the refrigerant C in the system is almost exhausted, and the refrigerant recovery operation is stopped. In step S5, the compressor 1a is stopped and the expansion valve 1b is set to the minimum opening in order to reset the opening to zero in preparation for restarting operation.

  The operation start condition for the refrigerant recovery operation may be the outside air temperature. In this embodiment, since each sensor is often equipped in the site | part shown in FIG. 7 of the general purpose heat pump water heater 1, it is set as the form which utilizes them.

  FIG. 9 shows a second embodiment of the present invention. The difference between the second embodiment and the first embodiment is the presence or absence of a brine piping system, and the other parts conform to the first embodiment, and therefore, by attaching the same reference numerals as those of the first embodiment to the conforming parts, The description is omitted. As shown in FIG. 9, the heat collection side heat exchanger 2 is connected to the heat pump water heater 11 via the refrigerant forward pipe 2k1 and the refrigerant return pipe 2k2. In the second embodiment, the refrigerant forward pipe 2k1 and the refrigerant return pipe 2k2 constitute a brine pipe through which a brine (secondary refrigerant) C1 flows. The heat pump water heater 11 is connected to a hot water storage tank 13 through a hot water supply pipe 12. The brine pipe in the heat pump water heater 11 is provided with a brine pump 11f that sends the brine C1 to the heat collecting side heat exchanger 2 side. A valve 11e capable of bypassing part of the brine C1 from the refrigerant return pipe 2k2 to the refrigerant forward pipe 2k1 is provided downstream of the brine pump 11f in the brine pipe in the heat pump water heater 11. In the heat pump water heater 11, a hot water storage pump 11 g that circulates the water stored in the tank 13 a of the hot water storage tank 13 is provided.

  In the heat pump water heater 11, a refrigerant pipe 11a as a refrigerant pipe for circulating the refrigerant C is accommodated. The refrigerant pipe 11a is provided with a compressor 11d for compressing the refrigerant C. A first heat exchanger 11b and a second heat exchanger 11c are provided in the middle of the refrigerant pipe 11a. The first heat exchanger 11b performs heat exchange between the refrigerant C and the brine C1, and the second heat exchanger 11c performs heat exchange between the refrigerant C and water from the hot water tank 13. is there. In the heat pump water heater 11, a hot water storage pump 11g for supplying water stored in the tank body 13a of the hot water storage tank 13 to the second heat exchanger 11c is provided. In the hot water storage tank 13, a valve 13 c and a hot water supply pump 13 d for supplying hot water stored in the tank body 13 a to the hot water tap 4 are provided. A valve 13b for supplying water from the outside into the tank body 13a is provided at the upper part of the tank body 13a.

  In Embodiment 2 configured as described above, the brine C1 sent from the heat collection side heat exchanger 2 to the heat pump water heater 11 via the refrigerant return pipe 2k2 is supplied to the refrigerant pipe by the first heat exchanger 11b. Heat is exchanged with the refrigerant C flowing through 11a. And in the 2nd heat exchanger 11c, heat exchange with the refrigerant | coolant C and the water supplied from the hot water storage tank 13 side is performed, and the water which became high temperature is returned to the tank main body 13a. Here, the flow rate of the brine flowing into the first heat exchanger 11b of the brine C1 can be reduced by the valve 11e, but in order to collect as much heat as possible from the solar radiation, as long as the pressure in the refrigerant pipe 11a does not exceed the limit. It is desirable not to limit the amount of brine C1 flowing into the first heat exchanger 11b by the valve 11e. In addition, the set hot water temperature of the hot water storage tank 13 is desirably set to the minimum necessary temperature in order to reduce the pressure of the refrigerant pipe 11a system as much as possible.

  As described above, in the case of the configuration using the brine C1, the pipe for use in the work site can be performed in the factory that manufactures the heat pump water heater 11 because the pipe brazing and the airtight pressure resistance test of the refrigerant pipe 11a through which the high-pressure refrigerant C flows can be performed. Brazing and airtight pressure resistance tests are not required, and work efficiency can be increased. Furthermore, since the airtight pressure resistance required for the brine piping (refrigerant outgoing pipe 2k1 and refrigerant return pipe 2k2) system can be significantly lower than that of the refrigerant piping 11a using the refrigerant C, the construction technology of the conventional solar water heater can be diverted. It is also easy to ensure the airtight pressure resistance performance of the pipe between the heat pump water heater 11 and the heat collecting side heat exchanger 2. Similarly, when the configuration using the brine C1 is adopted, the heat exchange efficiency is somewhat lowered due to the double heat collecting side heat exchanger, but since the refrigerant pipe 11a can be stored in the heat pump water heater 11, the summer When the hot water supply operation is stopped under such a high temperature environment, there is no possibility that the refrigerant C of the refrigerant pipe 11a system is extremely heated, and a mechanism for collecting the refrigerant becomes unnecessary.

  The present invention can be applied to, for example, a house and configured as an all-electric heat pump solar system.

DESCRIPTION OF SYMBOLS 1 Heat pump water heater 1a Compressor 1b Expansion valve 1c Heat utilization side heat exchanger 1d Refrigerant tank 2 Heat collection side heat exchanger 21 Upper wave plate 22 Lower wave plate 2a Wave type heat collection side heat exchanger 2b Wave-shaped heat-collecting side heat exchanger valley 2c Inclined portion 2d Selective absorption film 2e Refrigerant flow path 2f Insulating material 11a Refrigerant pipe (refrigerant pipe line)
11b 1st heat exchanger 11c 2nd heat exchanger C Refrigerant C1 Brine

Claims (6)

  The heat collection side heat exchanger of the heat pump water heater is separated from the main body and installed on the roof surface of the building, and the gas-liquid phase changes between the compressor of the heat pump water heater and the heat collection side heat exchanger to heat and cool Circulates and circulates the refrigerant that contributes to the heat collecting side, introduces the gas-liquid two-phase refrigerant that has become low pressure through the decompression device to the heat collecting side heat exchanger, collects heat by evaporation, and on the heat utilization side of the heat pump water heater The refrigerant is circulated and circulated between the compressor and the heat utilization side heat exchanger, and the refrigerant in the gas phase that has become high pressure by the compressor is led to the heat utilization side heat exchanger to dissipate heat by the condensation action. Further, the system circulates and circulates water between the heat utilization side heat exchanger and the hot water storage tank, and the outer shape of the heat collection side heat exchanger has at least the outdoor side as a shape in which peaks and valleys are continuous. Selective absorption membrane treatment and the inside is at least before Along the inclined portion connecting the peaks and valleys, characterized in that the formation of the refrigerant flow path through which the coolant, solar thermal heat pump hot water system.   The heat-collecting side heat exchanger is configured by a plurality of connecting bodies of corrugated plates having an outer shape of 5 to 15 mm in height, each corrugated plate is provided with a refrigerant inlet and outlet, A flat refrigerant flow path is built in, the connection is parallel connection, and the longitudinal direction of the corrugated plate is inclined so as to stand up toward the top surface of the roof of the building, and the refrigerant inlet is provided. The solar heat-based heat pump hot water supply system according to claim 1, wherein an outlet of the refrigerant is arranged on a top surface side of the roof below the roof.   The surface side of the heat collecting side heat exchanger has a structure in which two pieces of metal formed in a corrugated shape are stacked one on top of the other. 3. The solar-powered heat pump hot water supply system according to claim 1, wherein a plurality of refrigerant flow paths parallel to the inclined portion are formed between the inclined portion of the plate and the inclined portion of the corrugated plate below. .   A refrigerant tank is provided in the heat pump water heater, and the refrigerant tank is located between the pressure reducing device and a refrigerant inlet of the heat collection side heat exchanger, and returns from the heat collection side heat exchanger to the compressor. And the refrigerant tank are connected by a bypass pipe, and a second pressure reducing device is interposed in the bypass pipe so that the refrigerant in the refrigerant tank is decompressed and sucked into the compressor. The solar heat utilization heat pump hot water supply system according to any one of claims 1 to 3.   The operating method of the system which comprised the pipe line which connects the said refrigerant | coolant tank and the refrigerant | coolant inlet_port | entrance of the said heat collection side heat exchanger, and the said bypass pipe to the solar heat utilization heat pump hot-water supply system of Claim 4 respectively. The hot water is accumulated in the hot water tank and the compressor is temporarily stopped, and then the refrigerant inlet pipe valve of the heat collecting side heat exchanger is closed, the bypass pipe valve is closed, and the compressor The operation method of the solar heat utilization heat pump hot water supply system characterized by operating again.   A heat collecting water heat exchanger of the heat pump water heater is separated from the main body and installed on the roof surface of the building, and a first heat exchanger and a second heat exchanger are provided inside the heat pump water heater, and the heat collecting A brine is circulated between the side heat exchanger and the first heat exchanger, and the refrigerant pipe in the heat pump water heater in which the compressor and the second heat exchanger are arranged is connected to the first heat exchanger. A refrigerant changing in phase into a gas-liquid two phase that can exchange heat with the brine is circulated and circulated through the heat exchanger, and the second heat exchanger is interposed between the heat pump water heater and the hot water storage tank. It is a system that circulates and circulates water that can exchange heat with the refrigerant, and the outer shape of the heat-collecting side heat exchanger is subjected to selective absorption film treatment on the surface so that at least the outdoor side has a continuous mountain and valley, and the inside is At least along the slope connecting the mountain and valley Characterized in that the formation of the coolant channel in which the brine flows Te, solar thermal heat pump hot water system.

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