JP4104261B2 - Water heater - Google Patents

Water heater Download PDF

Info

Publication number
JP4104261B2
JP4104261B2 JP33975099A JP33975099A JP4104261B2 JP 4104261 B2 JP4104261 B2 JP 4104261B2 JP 33975099 A JP33975099 A JP 33975099A JP 33975099 A JP33975099 A JP 33975099A JP 4104261 B2 JP4104261 B2 JP 4104261B2
Authority
JP
Japan
Prior art keywords
hot water
temperature
water supply
heat storage
pipe
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
JP33975099A
Other languages
Japanese (ja)
Other versions
JP2001153458A (en
Inventor
誠治 三輪
正彦 伊藤
智明 小早川
路之 斉川
久介 榊原
忠幸 百瀬
和俊 草刈
健一 藤原
Original Assignee
東京電力株式会社
株式会社デンソー
財団法人電力中央研究所
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 東京電力株式会社, 株式会社デンソー, 財団法人電力中央研究所 filed Critical 東京電力株式会社
Priority to JP33975099A priority Critical patent/JP4104261B2/en
Priority claimed from DE2000159134 external-priority patent/DE10059134B4/en
Publication of JP2001153458A publication Critical patent/JP2001153458A/en
Application granted granted Critical
Publication of JP4104261B2 publication Critical patent/JP4104261B2/en
Anticipated expiration legal-status Critical
Application status is Expired - Fee Related legal-status Critical

Links

Images

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a heat storage type hot water supply apparatus.
[0002]
[Prior art]
As a conventional technique, for example, there is a regenerative hot water supply apparatus disclosed in Japanese Patent Laid-Open No. 5-99507. As shown in FIG. 13, this hot water supply apparatus includes a tank 100 for storing heat storage fluid and a heat exchanger 110 provided outside the tank 100, and heat storage fluid in the tank 100 is heated by a heater 120. Then, the heated heat storage fluid is circulated to the heat exchanger 110 by the pump 130, and the hot water supply water flowing through the heat exchanger 110 is heated by the heat energy stored in the heat storage fluid.
[0003]
[Problems to be solved by the invention]
However, in the hot water supply apparatus described above, the temperature difference ΔT between the temperature of the heat storage fluid radiated by the heat exchanger 110 and the temperature of hot water before being heated by the heat exchanger 110 (unheated hot water) increases. . Since the amount of heat corresponding to this temperature difference ΔT is the amount of heat that is discarded without being used for heat exchange, it is an inefficient hot water supply system.
The present invention has been made based on the above circumstances, and an object of the present invention is to provide a hot water supply apparatus that is excellent in heat exchange capability and efficient.
[0004]
[Means for Solving the Problems]
(Means of Claim 1)
The first pipe through which the heat storage fluid flows and the second pipe through which the hot water supply water are provided are adjacent to each other, and the heat storage fluid and the hot water supply are configured to face each other, and heat exchange is performed between the two. A counter-flow heat exchanger that performs A hot water pipe connected to the second pipe and leading hot water to the terminal; A circulation passage for taking out the heat storage fluid heated from the upper portion of the tank and passing it through the first pipe, and then returning it to the lower portion of the tank; pump means for circulating the heat storage fluid in the circulation passage; and circulation passage And a flow rate control means for controlling the flow rate of the heat storage fluid flowing through the first pipe.
In this configuration, the temperature of the heat storage fluid after passing through the first pipe is adjusted by using a counter-flow heat exchanger and controlling the flow rate of the heat storage fluid flowing through the first pipe before heating. It can be reduced to near the temperature of hot water. As a result, it is possible to minimize heat loss during heat exchange between the heat storage fluid and the hot water supply water, thereby realizing an efficient hot water supply system.
[0005]
Also, a fluid heating passage is provided that takes out the heat storage fluid from the lower part in the tank and supplies it to the heating means, and returns the heat storage fluid heated by the heating means to the upper part in the tank.
The heat storage fluid is taken out from the upper part of the tank and flows to the first pipe of the counter flow heat exchanger, and the heat storage fluid after the heat exchange is returned to the lower part of the tank. The heat storage fluid whose temperature has been lowered is taken out from the lower part in the tank, heated by the heating means, and returned to the upper part in the tank, whereby heat can be efficiently stored in the heat storage fluid.
The flow rate control means includes first temperature detection means for detecting the temperature of the hot water for water flowing into the second pipe, and flow rate detection means for detecting the flow of the hot water for water passing through the second pipe, Based on the target temperature of hot water discharged from the hot water pipe, the temperature of hot water detected by the first temperature detection means, and the flow rate of hot water detected by the flow rate detection means, The temperature difference between the temperature of the heat storage fluid after heat exchange and the temperature of the hot water supply water flowing into the second pipe is within a predetermined range. The flow rate of the heat storage fluid flowing through the first pipe is adjusted.
In this configuration, by adjusting the flow rate of the heat storage fluid flowing through the first pipe in accordance with the temperature and flow rate of the hot water supply water, the heat storage fluid having a flow rate sufficient to heat the hot water supply water to the target temperature is obtained. It can be made to distribute | circulate to 1st piping. As a result, when the heat storage fluid flows out from the first pipe, the temperature of the heat storage fluid can be reliably lowered to the vicinity of the temperature of the hot water supply water before heating.
And 1st piping Heat mixing with the heat storage fluid flowing through the second pipe and mixing means for mixing hot water and unheated hot water flowing out from the second pipe, and the target temperature is a predetermined temperature higher than the temperature at which the hot water is actually supplied The hot water supply water set to a high temperature and heated to the target temperature is mixed with the unheated hot water supply water by the mixing means, thereby lowering the temperature of the hot water supply water to a temperature at which the hot water is to be supplied. If the temperature of the hot water supply water is directly adjusted by the flow rate control of the flow rate control means, the responsiveness of the temperature change is slow, so the accuracy of the temperature control may be reduced. However, as described in this means, when the mixing means is used, the temperature of the hot water supply water can be accurately adjusted to the temperature at which the hot water is actually supplied.
[0006]
( Claim 2 Means)
The heating means is a supercritical heat pump cycle in which the pressure of the refrigerant becomes equal to or higher than the critical pressure, and heats the heat storage fluid with the refrigerant whose pressure is increased to the critical pressure or higher.
In the supercritical heat pump cycle, when the heat storage fluid is heated to a target temperature (for example, 65 to 90 degrees), the lower the temperature of the hot water supply water before heating, the lower the high-pressure pressure, and thus the cycle efficiency (COP = heating capacity) / Power consumption) is improved. Therefore, by heating the heat storage fluid reduced to near the temperature of hot water before heating with a supercritical heat pump cycle, cycle efficiency is improved and power saving operation can be performed.
[0008]
(Claims 3 Means)
The flow rate control means includes second temperature detection means for detecting the temperature of the hot water for water flowing out from the second pipe, so that the temperature of the hot water for water detected by the second temperature detection means becomes the target temperature. The flow rate of the heat storage fluid flowing through the first pipe is corrected.
Thereby, the temperature of the hot water supply water can be accurately adjusted to the target temperature.
[0010]
(Claims 4 Means)
The target temperature is set to a constant temperature higher than the normally used hot water temperature. Regardless of the actual set hot water supply temperature, by making the target temperature constant, cold / hot water mixing by the mixing means can be performed with high accuracy.
[0011]
(Claims 5 Means)
heat An exchanger is located in the tank.
According to this configuration, since heat can be exchanged between the heated heat storage fluid and hot water supply water inside the tank, heat loss due to heat radiation is small, and hot water supply capability can be improved.
Furthermore, the hot water heated by the heat exchanger is mixed with the water before being heated by the heat exchanger, and hot water supply temperature adjusting means for adjusting the temperature of the hot water is provided. In this case, it is not necessary to change the flow rate of the fluid flowing through the circulation passage, and the fluid flow rate can be kept constant, so that the temperature fluctuation of the hot water heated by the heat exchanger can be reduced. Thereby, the temperature control of the hot water supply water can be accurately performed with respect to the set temperature.
[0012]
(Claims 6 Means)
The circulation passage and the pump means are provided in the tank. In this case, since the heated heat storage fluid is not taken out of the tank, heat loss can be further reduced as compared with the case where only the heat exchanger is arranged in the tank.
[0013]
(Claims 7 Means)
When the temperature of the heat storage fluid stored in the tank differs in the vertical direction in the tank (for example, when the fluid temperature is high on the upper side and the fluid temperature is low on the lower side), heat exchange is performed. By covering the vessel with a heat insulating material, it is possible to prevent the heat of the high-temperature fluid flowing through the heat exchanger from being released to the low-temperature fluid in the tank.
[0014]
(Claims 8 Means)
The pump means includes a first impeller that rotates in response to the energy of the hot water flowing through the hot water supply pipe, a second impeller that is provided in the circulation passage, and that rotates by transmitting the rotation of the first impeller. The heat storage fluid is circulated in the circulation passage by the rotation of the second impeller. According to this configuration, since the heat storage fluid can be caused to flow through the lubrication passage only by the energy of the supply water pressure, the driving power in the case where a general electric pump is used as the pump means becomes unnecessary.
[0015]
(Claims 9 Means)
By using a tank that is open to the atmosphere, a pressure-resistant design like a pressurized tank is not required, so that the tank itself can be molded from resin. In this case, a pressing process and a welding process necessary for processing stainless steel, which is usually used as a tank material, are unnecessary, and the manufacturing cost can be kept lower than before.
In addition, parts such as a pressure reducing valve, a pressure relief valve, a negative pressure operation valve, and a can body protection valve, which are necessary for a configuration using a pressure tank, are not necessary. Further, unlike the pressure tank, it is not necessary to form a cylindrical shape from the viewpoint of pressure resistance, and the degree of freedom in designing the tank shape can be increased.
[0018]
(Claims 10 Means)
Claim 5 The hot water supply temperature adjusting means described in 1 is a mixing valve provided downstream of the heat exchanger of the hot water supply pipe, a branch pipe branched from the hot water supply pipe upstream of the heat exchanger and connected to the mixing valve, and a mixing valve A water temperature sensor that detects the temperature of the hot water supply water downstream is provided, and the mixing ratio of hot water and water in the mixing valve can be adjusted based on the temperature detected by the water temperature sensor. According to this configuration, since the temperature of the hot water supply water can be controlled by adjusting the mixing ratio of hot water and water with the mixing valve, temperature control with respect to the set temperature is easy.
[0019]
DETAILED DESCRIPTION OF THE INVENTION
Next, embodiments of the present invention will be described with reference to the drawings.
(First embodiment)
FIG. 1 is a schematic diagram showing a configuration of a hot water supply apparatus.
The hot water supply apparatus 1 of this embodiment is used for general household use, and includes a tank 2 for storing a heat storage fluid W, a heating means (to be described later) for heating the heat storage fluid W in the tank 2, and a tank 2 The electric pump 3 for pumping up the heat storage fluid W in the inside, and for hot water supply for exchanging heat between the heat storage fluid W pumped up by the electric pump 3 and the hot water supplied to the hot water supply pipes (the water supply pipe 4 and the hot water supply pipe 5) It is comprised from the heat exchanger 6, the control apparatus (pump control part 7 and cycle control part 8) etc. which control the action | operation of this hot water supply system.
[0020]
a) The tank 2 is opened to the atmosphere through the air hole 2a, and the inside of the tank 2 is maintained at atmospheric pressure. The tank 2 is formed of a resin material, for example, and is provided in a rectangular parallelepiped shape. In order to reduce the heat stored in the heat storage fluid W in the tank 2 from being released into the atmosphere from the wall surface of the tank 2, the outer periphery of the tank 2 may be covered with a heat insulating material such as glass wool or urethane. good.
The main component of the heat storage fluid W is water, and a preservative, an antifreezing agent, LLC, and the like are added as necessary.
[0021]
b) The heating means uses a supercritical heat pump cycle C in which, for example, carbon dioxide gas is used as a refrigerant, so that the refrigerant pressure on the high pressure side becomes equal to or higher than the critical pressure of the refrigerant.
The heat pump cycle C includes functional parts such as a compressor 9, a heat storage heat exchanger 10, an expansion valve 11, an evaporator 12, and an accumulator 13.
The compressor 9 is driven by a built-in electric motor (not shown), and compresses and discharges the gas-phase refrigerant sucked from the accumulator 13 to a critical pressure or higher.
[0022]
The heat storage heat exchanger 10 exchanges heat between the refrigerant and the heat storage fluid W. For example, a refrigerant passage 10a through which the refrigerant flows and a heat storage fluid passage 10b through which the heat storage fluid W flows are provided in a double tube structure. The counter flow type heat storage heat exchanger 10 is configured so that the flow direction of the refrigerant and the flow direction of the heat storage fluid W are opposed to each other.
The expansion valve 11 decompresses the refrigerant flowing out from the heat storage heat exchanger 10 and supplies the decompressed refrigerant to the evaporator 12.
The evaporator 12 evaporates the refrigerant decompressed by the expansion valve 11 by heat exchange with the atmosphere.
The accumulator 13 gas-liquid separates the refrigerant flowing out from the evaporator 12 and causes the compressor 9 to suck only the gas-phase refrigerant and stores excess refrigerant in the cycle.
[0023]
The heat storage fluid passage 10b of the heat storage heat exchanger 10 is connected to the tank 2 via an inflow pipe 14 and an outflow pipe 15, and the electric pump 16 provided in the inflow pipe 14 is activated to store heat in the tank 2. The working fluid W circulates. However, the upstream end of the inflow pipe 14 opens at the bottom of the tank 2, and the downstream end of the outflow pipe 15 opens at the top of the tank 2. As a result, the heat storage fluid W heated by heat exchange with the refrigerant in the heat storage heat exchanger 10 is sent to the upper part of the tank 2 through the outflow pipe 15, so that the upper part in the tank 2 moves from the lower side toward the lower side. The heat is sequentially stored in the heat storage fluid W. In addition, since the heat storage fluid W in the tank 2 only needs to secure a heat storage amount corresponding to the amount of hot water used in the home, the entire heat storage fluid in the tank 2 is not necessarily maintained at a high temperature.
[0024]
Therefore, in a home where the amount of hot water used is small, for example, heat may be stored in about half of the heat storage fluid W in the tank 2. In this case, in the tank 2, as shown in FIG. 1, due to the specific gravity difference due to the temperature of the heat storage fluid W, the heat storage fluid W <b> 1 having a higher temperature from the upper side toward the lower side in the tank 2, the heat storage at the intermediate temperature Naturally separated into a heat storage fluid W3 and a low temperature heat storage fluid W3, the intermediate temperature heat storage fluid W2 also serves to insulate between the high temperature heat storage fluid W1 and the low temperature heat storage fluid W3. The thickness is small compared to the entire heat storage fluid.
[0025]
c) The electric pump 3 is installed, for example, in the upper part of the tank 2, connected to the tank 2 through the suction pipe 17, and connected to the hot water supply heat exchanger 6 through the discharge pipe 18. In addition, the upstream end (suction port) of the suction pipe 17 is open to the upper part (high temperature heat storage fluid W1) in the tank 2. Therefore, when the electric pump 3 is operated, the heat storage fluid W1 having a high temperature can be pumped and pumped to the hot water supply heat exchanger 6.
[0026]
d) The hot water supply heat exchanger 6 includes a primary side passage 6a through which the heat storage fluid W pumped up by the electric pump 3 flows, and a secondary side passage 6b connected to the hot water supply pipes (the water supply pipe 4 and the hot water supply pipe 5). For example, as shown in FIG. 2, the inner tube 6B that forms the secondary passage 6b is inserted into the outer tube 6A that forms the primary passage 6a.
Here, the outer tube 6A preferably uses a resin material in order to keep heat loss low, and the inner tube 6B preferably uses a copper material having a high thermal conductivity. Further, the inner tube 6B may be a cylindrical tube as with the outer tube 6A. However, for example, as shown in FIG. In this case, the heat transfer area between the primary side passage 6a and the secondary side passage 6b increases, and the heat exchange efficiency between the heat storage fluid W and the hot water supply water can be improved.
[0027]
As shown in FIG. 1, the hot water supply heat exchanger 6 is arranged in the vertical direction inside the tank 2, and the upper end of the primary passage 6 a is connected to the electric pump 3 via the discharge pipe 18. The lower end (outlet) of the passage 6 a is open at the bottom of the tank 2. Further, the lower end of the secondary passage 6 b is connected to the water supply pipe 4 at the lower part in the tank 2, and the upper end protrudes to the upper part of the tank 2 and is connected to the hot water supply pipe 5. Accordingly, the hot water supply heat exchanger 6 has a flow direction of the heat storage fluid W flowing from the top to the bottom in the primary passage 6a and a secondary passage 6b from the bottom to the top, as indicated by arrows in FIG. It is configured as a counterflow type in which the flow direction of hot water for water flowing in the opposite direction. The water supply pipe 4 and the hot water supply pipe 5 are part of the hot water supply pipe.
[0028]
e) The control device includes a pump control unit 7 that controls the operation of the electric pump 3, and the pump control unit 7 detects hot water supply sensor 19 that detects the presence or absence of “water flow” and a water temperature that detects the temperature of hot water supply water. The detection signal of the sensor 20 is input, the ON / OFF control of the electric pump 3 is performed based on the detection result of the hot water detection sensor 19, and the rotation speed control of the electric pump 3 is performed based on the detection result of the water temperature sensor 20. The hot water detection sensor 19 is provided in the hot water supply pipe 4 or the hot water supply pipe 5, and the water temperature sensor 20 is provided in the hot water supply pipe 5.
[0029]
Further, the control device includes a cycle control unit 8 that controls an electric motor built in the compressor 9 of the heat pump cycle C and an electric pump 16 provided in the inflow pipe 14. The cycle control unit 8 is based on the detected temperature of the heat storage temperature sensor 21 that detects the temperature of the heat storage fluid after heating in order to keep the temperature of the heat storage fluid W heated by the heat storage heat exchanger 10 at a constant temperature. Thus, the rotational speed of the electric pump 16 is controlled.
[0030]
Next, the operation of this embodiment will be described.
The heat storage fluid W in the tank 2 is heated and stored by a necessary amount, for example, by operating the heat pump cycle C and the electric pump 16 using midnight power. Thereafter, when the user opens the hot water tap (not shown) and a water flow is generated in the hot water supply pipe (hot water supply pipe 5), a “water flow” is detected by the hot water detection sensor 19 and is output from the pump control unit 7. The electric pump 3 is activated in response to the signal (ON signal). When the electric pump 3 is operated, a high-temperature heat storage fluid W is pumped from the upper portion of the tank 2, and a flow of the heat storage fluid W is generated in the primary passage 6 a of the hot water supply heat exchanger 6. Thereby, the hot water supply water flowing through the secondary side passage 6b of the hot water supply heat exchanger 6 receives the heat energy of the heat storage fluid W and is heated.
[0031]
Here, the pump control unit 7 controls the driving state (the number of rotations) of the electric pump 3 so that the temperature of the hot water detected by the water temperature sensor 20 becomes a desired hot water supply temperature (a hot water supply temperature set by the user). To do. That is, when the hot water temperature detected by the water temperature sensor 20 is lower than the desired hot water supply temperature, the rotational speed of the electric pump 3 is increased to increase the circulation amount of the heat storage fluid W flowing through the primary passage 6a. As a result, the amount of heat exchange between the heat storage fluid W flowing through the primary passage 6a and the hot water supply water flowing through the secondary passage 6b increases, and the temperature of the hot water rises. When the temperature of the hot water detected by the water temperature sensor 20 is higher than the desired hot water supply temperature, the rotational speed of the electric pump 3 is reduced to reduce the circulation amount of the heat storage fluid W flowing through the primary side passage 6a. As a result, the amount of heat exchange between the heat storage fluid W flowing through the primary side passage 6a and the hot water supply water flowing through the secondary side passage 6b is reduced, so that the temperature of the hot water is lowered.
[0032]
(Effects of the first embodiment)
Since the hot water supply device 1 of the present embodiment has the hot water supply heat exchanger 6 disposed in the tank 2, heat exchange between the heat storage fluid W and the hot water supply water can be performed inside the tank 2. As a result, since heat loss due to heat radiation to the atmosphere is reduced, the hot water supply capacity can be improved accordingly. In addition, space can be saved as compared with the case where the hot water heat exchanger 6 is disposed outside the tank 2.
[0033]
In the present embodiment, since the atmosphere open type tank 2 is used, the pressure resistance design such as a pressure tank (sealed type tank) is not required, and therefore the tank 2 can be formed of resin. In this case, a pressing process and a welding process necessary for processing stainless steel, which is usually used as a tank material, are unnecessary, and the manufacturing cost can be kept lower than before. In addition, parts such as a pressure reducing valve, a pressure relief valve, a negative pressure operation valve, and a can body protection valve, which are necessary for a configuration using a pressure tank, are not necessary. Further, unlike the pressure tank, it is not necessary to form a cylindrical shape from the viewpoint of pressure resistance, and there is an effect that the degree of freedom in designing the tank shape can be increased.
[0034]
By making the inner pipe 6B of the hot water supply heat exchanger 6 uneven, it is possible to increase the heat exchange area between the primary side passage 6a through which the heat storage fluid W flows and the secondary side passage 6b through which hot water supply water flows. For this reason, heat exchange capability improves compared with the case where the inner side pipe 6B is comprised with a round tube, and it is possible to shorten the full length of the heat exchanger 6 for hot water supply.
Since the heat pump cycle C is used as the heating means for the heat storage fluid W, the running cost (mainly electricity bill) is much lower than that of the gas type or kerosene type heating means.
The heated heat storage fluid W can be used not only for hot water supply but also for floor heating and indoor air conditioning. Further, the heat storage fluid W can be used as hot water for a bath. In this case, since the heat storage fluid W can be used without heat loss, the entire heat storage amount can be effectively utilized.
[0035]
(Second embodiment)
This embodiment is an example in which a turbine is used as means for circulating the heat storage fluid W in the hot water supply heat exchanger 6.
As shown in FIG. 3, the turbine includes a first impeller 22 that rotates in response to the flow of hot water supply water, and a second impeller 23 that rotates by transmitting the rotation of the first impeller 22. Is done.
[0036]
The first impeller 22 is stored in a storage chamber 24 provided in the hot water supply pipe 5, and when a water flow is generated in the hot water supply pipe 5, the first impeller 22 can rotate at a rotation speed corresponding to the flow rate.
The second impeller 23 is accommodated in a storage chamber 25 provided between the suction pipe 17 and the discharge pipe 18 and can pump the heat storage fluid W pumped up by its own rotation to the primary passage 6a. .
The first impeller 22 and the second impeller 23 can be interlocked by the attractive force of a magnet (not shown) embedded in each. In this configuration, since it is not necessary to connect the first impeller 22 and the second impeller 23 by a shaft or the like, the storage chamber 24 and the storage chamber 25 can be completely separated, and hot water supply water and heat storage Mixing with the working fluid W cannot occur.
[0037]
According to the configuration of the present embodiment, the heat storage fluid W can be circulated to the primary side passage 6a only by the energy of the water flow generated in the hot water supply pipe 5, and therefore it is necessary to use the electric pump 3 shown in the first embodiment. There is no need for electric power for driving the electric pump 3.
In addition, if the piping pressure loss is designed so that the hot water flow rate, the rotational speed of each impeller 22 and 23, and the flow rate of the heat storage fluid W flowing through the primary passage 6a are the target hot water temperature, the first is performed. Since the hot water detection sensor 19, the water temperature sensor 20, and the pump controller 7 shown in the embodiment are not required, an inexpensive system can be provided.
[0038]
(Third embodiment)
In this embodiment, as shown in FIG. 4, the flow rate of the heat storage fluid W flowing through the primary passage 6 a is controlled by an electric flow control valve 26.
The electric flow control valve 26 is installed either before or after the electric pump 3, and receives a command from the pump control unit 7 to vary the heat storage fluid flow rate.
According to this configuration, since the heat storage fluid flow rate is varied by the electric flow control valve 26, the rotational speed of the electric pump 3 can be made constant. When the rotational speed of the electric pump 3 is changed as in the first embodiment, a speed variable circuit such as an inverter is required if it is alternating current. However, the speed variable circuit is made constant by making the rotational speed of the electric pump 3 constant. Is no longer necessary.
The configuration of the present embodiment (electric flow control valve 26) can also be applied to a system that uses the turbine shown in the second embodiment.
[0039]
(Fourth embodiment)
In the present embodiment, as shown in FIG. 5, the flow rate of the heat storage fluid W flowing through the primary passage 6 a is controlled by the temperature detection type flow control valve 27.
The temperature detection type flow control valve 27 has a gas sealing part 27a in which an inert gas is sealed, and has a structure in which the valve opening degree is varied according to the internal pressure of the gas sealing part 27a. Is installed at a position where the temperature of the hot water heated by the hot water heat exchanger 6 can be sensed.
For example, when the hot water supply temperature decreases, the temperature detection type flow control valve 27 increases the valve opening degree by decreasing the internal pressure of the gas sealing portion 27a, and increases the heat storage fluid flow rate to increase the hot water supply temperature. . Further, when the hot water supply temperature is increased, the internal pressure of the gas sealing portion 27a is increased so that the valve opening is reduced, and the hot water supply temperature is decreased by reducing the heat storage fluid flow rate.
[0040]
According to the configuration of the present embodiment, the temperature detection type flow control valve 27 works to maintain the hot water supply temperature at a desired set temperature mechanically, so that the rotational speed of the electric pump 3 is the same as in the third embodiment. Can be kept constant, and a speed variable circuit such as an inverter becomes unnecessary.
Moreover, since the temperature detection type flow control valve 27 has a structure in which the valve opening degree is varied in accordance with the internal pressure of the gas sealing portion 27a, the water temperature sensor 20 for detecting the temperature of the hot water supply water is unnecessary.
In addition, the structure (temperature detection type flow control valve 27) of a present Example is applicable also to the system which uses the turbine shown in 2nd Example.
[0041]
(5th Example)
The present embodiment is an example in which the temperature of hot water supply water is adjusted by mixing hot water heated by the hot water supply heat exchanger 6 with water before being heated by the hot water supply heat exchanger 6. Specifically, as shown in FIG. 6, it has a branch pipe 28 branchedly connected to the water supply pipe 4, and the downstream end of the branch pipe 28 is connected to a mixing valve 29 provided in the hot water supply pipe 5. Is done.
The mixing valve 29 varies the amount of water flowing from the branch pipe 28 and receives a command from the pump control unit 7 so that the temperature of the hot water supply water detected by the water temperature sensor 20 becomes the set hot water supply temperature. The amount of water is adjusted.
[0042]
According to this configuration, since the temperature of the hot water supply water can be adjusted by the mixing valve 29, the temperature control of the hot water supply water with respect to the set temperature is possible even if there is some temperature fluctuation in the hot water heated by the hot water supply heat exchanger 6. Can be performed with higher accuracy.
The configuration of this embodiment can also be applied to a system that uses the turbine shown in the second embodiment.
[0043]
(Sixth embodiment)
In this embodiment, as shown in FIG. 7, the heat storage heat exchanger 10 of the heat pump cycle C, which is a heating means, is arranged in the tank 2. Moreover, the electric pump 16 is provided in the outflow pipe 15 with the movement of the heat storage heat exchanger 10. As in the first embodiment, the rotational speed of the electric pump 16 is controlled by the cycle control unit 8 so that the heat storage fluid temperature detected by the heat storage temperature sensor 21 is constant.
[0044]
According to this configuration, since the heat storage heat exchanger 10 is arranged in the tank 2, the required volume of the heat pump cycle C configured outside the tank 2 can be reduced and the heat exchanger cycle can be made compact. Moreover, since the heat loss from the heat storage heat exchanger 10 to the atmosphere is eliminated, the heat storage capacity is improved.
The configuration of this embodiment can also be applied to a system using the turbine shown in the second embodiment.
[0045]
(Seventh embodiment)
In this embodiment, as shown in FIG. 8, the pump function for circulating the heat storage fluid W in the hot water supply heat exchanger 6 and the pump function for circulating the heat storage fluid W in the heat storage heat exchanger 10 are electrically operated. This is an example performed by the pump 30. In addition, the heat pump cycle C is the structure which has arrange | positioned the heat exchanger 10 for thermal storage in the tank 2 similarly to 6th Example.
In this case, since the heat storage operation and the hot water supply operation are performed by one electric pump 30, it is necessary to switch the circulation path of the heat storage fluid W between the case of performing the heat storage operation and the case of performing the hot water supply operation. Therefore, as shown in FIG. 8, three-way valves 31 and 32 are respectively arranged before and after the electric pump 30, and the passage directions of the three-way valves 31 and 32 are determined according to instructions from the control device 50 (pump control unit, cycle control unit). Switching.
[0046]
Here, the flow of the heat storage fluid W when the passage directions of the three-way valves 31 and 32 are switched will be described.
a) When storing heat
Lower part in tank 2 (low temperature heat storage fluid W3) → heat storage fluid passage 10b of the heat storage heat exchanger 10 → first outlet pipe 15a → three-way valve 31 → common pipe 33 → electric pump 30 → common pipe 34 → three-way valve 32 → The second outflow pipe 15b → the heat storage fluid W flows into the upper part of the tank 2 (high temperature heat storage fluid W1).
[0047]
b) During hot water supply
Upper part of tank 2 (high temperature heat storage fluid W1) → suction pipe 17 → three-way valve 31 → common pipe 33 → electric pump 30 → common pipe 34 → three-way valve 32 → discharge pipe 18 → primary side passage of hot water supply heat exchanger 6 6a → The heat storage fluid W flows to the lower part of the tank 2 (low temperature heat storage fluid W3).
According to the configuration of the present embodiment, the heat storage operation and the hot water supply operation can be performed by one electric pump 30, so that the cost can be reduced compared to the case where two electric pumps are used.
[0048]
(Eighth embodiment)
As in the seventh embodiment, the present embodiment has one pump function for circulating the heat storage fluid W in the hot water supply heat exchanger 6 and one pump function for circulating the heat storage fluid W in the heat storage heat exchanger 10. As shown in FIG. 9, the heat storage heat exchanger 10 of the heat pump cycle C is arranged outside the tank 2 (the same as in the first embodiment). In this case, the same operation and effect as the seventh embodiment can be obtained.
[0049]
(Ninth embodiment)
This embodiment is an example in which the electric pump 3 is disposed in the tank 2 as shown in FIG. In this case, since the heated heat storage fluid W is not taken out of the tank 2, the heat loss can be further reduced as compared with the case where only the hot water supply heat exchanger 6 is disposed in the tank 2.
In this embodiment, the electric pump 3 is used as a means for circulating the heat storage fluid W in the primary passage 6a of the hot water supply heat exchanger 6. However, when the turbine described in the second embodiment is used. However, the turbine (the first impeller 22 and the second impeller 23) may be disposed in the tank 2 in the same manner.
[0050]
(Tenth embodiment)
The present embodiment is an example of a hot water supply system in which a hot water supply heat exchanger 6 is arranged outside the tank 2 as shown in FIG.
The hot water supply apparatus 1 of the present embodiment includes a tank 2 for storing the heat storage fluid W, a heating means (to be described later) for heating the heat storage fluid W, an electric pump 3 for pumping up the heat storage fluid W in the tank 2, and this electric pump. 3 for mixing the heat storage fluid W pumped up by the heat storage water 6 and the hot water supply water, the hot water supply water heated by the hot water supply heat exchanger 6 and the hot water supply water before being heated. 29 and a control device (described below) for controlling the operation of the hot water supply device 1.
[0051]
The tank 2 is opened to the atmosphere through the air hole 2a, and the inside of the tank 2 is maintained at atmospheric pressure.
The heating means is, for example, a supercritical heat pump cycle C that uses carbon dioxide as a refrigerant, as in the first embodiment, and is connected to the tank 2 via the inflow pipe 14 and the outflow pipe 15 as in the first embodiment. ing. The fluid heating passage of the present invention includes the inflow pipe 14 that supplies the heat storage fluid W to the heat pump cycle C by the operation of the electric pump 16 from the bottom of the tank 2, and the heat storage fluid W heated in the heat pump cycle C. And an outflow pipe 15 for returning the gas to the upper part in the tank 2.
[0052]
The electric pump 3 pumps the heat storage fluid W from the upper part of the tank 2 through the suction pipe 17, pumps it to the hot water supply heat exchanger 6, and exchanges heat with the hot water supply water in the hot water supply heat exchanger 6. W is returned to the lower part in the tank 2. In this embodiment, the electric pump 3 is installed on the upstream side (pressure feeding side) of the hot water supply heat exchanger 6, but may be installed on the downstream side (suction side) of the hot water supply heat exchanger 6. .
[0053]
As shown in FIG. 2, the hot water supply heat exchanger 6 is provided in a double-pipe structure including an outer pipe 6A (first pipe) and an inner pipe 6B (second pipe). The heat storage fluid W flows through the annular primary passage 6a formed between the pipes 6A, and hot water supply water flows through the secondary passage 6b formed inside the inner pipe 6B. However, the flow direction of the heat storage fluid W flowing through the primary side passage 6a and the flow direction of the hot water supply water flowing through the secondary side passage 6b are configured as opposite flow types.
As with the fifth embodiment, the hot water supply pipe through which the hot water supply circulates is provided with a mixing valve 29 in the hot water supply pipe 5, and the downstream end of the branch pipe 28 branched from the water supply pipe 4 is connected to the mixing valve 29. Has been.
[0054]
The control device includes a pump control unit 7 that controls the operation of the electric pump 3 and a cycle control unit 8 that controls the operation of the heat pump cycle C.
In the pump control unit 7, signals are input from a first temperature sensor 51 and a flow rate sensor 54 provided in the water supply pipe 4, and a second temperature sensor 52 and a third temperature sensor 53 provided in the hot water supply pipe 5, respectively. Based on these signals, a predetermined calculation is performed in accordance with a program inputted in advance, and the rotational speed of the electric pump 3 is controlled according to the calculation result.
[0055]
The first temperature sensor 51 detects the temperature T2i of the hot water supply water (unheated hot water supply water) supplied to the water supply pipe 4, and the second temperature sensor 52 passes through the hot water supply heat exchanger 6. The temperature T2o of the heated hot water supply water is detected, and the third temperature sensor 53 detects the temperature T2 of the hot water supply water obtained by mixing the unheated hot water supply water and the heated hot water supply water with the mixing valve 29. . The flow rate sensor 54 detects the flow rate of hot water supplied to the water supply pipe 4.
In the cycle control unit 8, the rotational speed of the electric pump 16 is controlled based on the temperature detected by the heat storage temperature sensor 21 that detects the temperature of the heat storage fluid W after heating.
[0056]
Next, the operation of this system will be described.
The set temperature of the hot water supply device 1 can be set in increments of 1 ° C. within a range of 35 to 50 ° C. (normal use temperature), and the temperature of the hot water flowing out from the hot water heat exchanger 6 is set to 50 ° C. as a target temperature. The Note that the set temperature can be set to 50 ° C. or more. In this case, the set temperature + α is set as the target temperature, or the set temperature itself is set as the target temperature. In addition, the target temperature can be set to a set temperature + α (variation value) at a normal use temperature.
[0057]
In order to obtain a constant hot water supply water temperature, the feed water temperature detected by the first temperature sensor 51, the feed water flow rate detected by the flow sensor 54, and the temperature of the heat storage fluid W detected by the heat storage temperature sensor 21 are parameters. The flow rate of the heat storage fluid W is calculated from the relational expression In this case, the flow rate of the heat storage fluid W is calculated such that the lower the feed water temperature, the higher the feed water flow rate, and the lower the temperature of the heat storage fluid W, the greater the flow rate of the heat storage fluid W. By sufficiently transferring heat from the heat storage fluid W having the flow rate thus obtained to the hot water supply water, the temperature T1o of the heat storage fluid W after heat exchange can be lowered to the vicinity of the temperature T2i of the hot water supply water. (For example, the temperature difference ΔT is within 5 ° C.).
Of course, as a premise, the heat exchanger for hot water supply 6 needs to have a heat exchanging capacity capable of sufficiently transferring heat from the heat storage fluid W to the hot water supply water, and for that reason, the flow direction of the heat storage fluid W It is comprised as a counterflow type heat exchanger with which the flow direction of hot water supply water opposes.
[0058]
The above control is so-called feedforward control, which is obtained in consideration of the flow rate and temperature of the heat storage fluid W necessary for heating hot water having a certain flow rate and temperature to the target temperature.
For this reason, in the flow volume of the heat storage fluid W actually calculated, the heating temperature of the hot water supply water may be too high or too low with respect to the target temperature. For this reason, the temperature T2o of hot water actually heated by the second temperature sensor 52 may be detected, and the flow rate of the heat storage fluid W may be corrected so that the temperature becomes the target temperature.
[0059]
In addition, by setting the target temperature to a temperature that is a predetermined temperature higher than the normally used hot water temperature, the temperature of the hot water can be accurately adjusted to the actual hot water temperature. That is, if the temperature of the hot water supply water is directly adjusted by the flow rate control of the pump control unit 7 (flow rate control means), the temperature control accuracy may be lowered because the responsiveness of the temperature change is slow. However, when the hot water heated by the hot water supply heat exchanger 6 and the cold water before being heated are mixed using the mixing valve 29 as in the present embodiment, the temperature of the hot water is actually set to the temperature at which the hot water is supplied. Can be adjusted accurately. In this case, while the temperature T2 of the hot water supply actually used is detected by the third temperature sensor 53, the hot water supply water heated to the target temperature and the unheated hot water supply water are mixed by the mixing valve 29. The temperature of the hot water supply water can be lowered to the temperature at which hot water should be supplied.
Moreover, by setting the target temperature to a constant temperature higher than the normally used hot water temperature, it is possible to stably and accurately mix cold / hot water.
[0060]
In this hot water supply system, a supercritical heat pump cycle C is used as a heating means for the heat storage fluid W. In this supercritical heat pump cycle C, a high pressure (the discharge pressure of the compressor 9) depends on the temperature of the heat storage fluid W. Therefore, as the temperature of the heat storage fluid W decreases, the high pressure decreases and the operation can be performed in a region where the cycle efficiency is good. Therefore, the temperature of the heat storage fluid W stored in the lower part of the tank 2 is lowered to the vicinity of the temperature of the hot water supply water by the flow rate control described above, and the heat storage fluid W is introduced from the lower part of the tank 2 to By heating and returning to the upper part in the tank 2, the cycle efficiency of the heat pump cycle C is improved, and a power saving operation can be performed.
[0061]
The water supply temperature may be directly detected by the first temperature sensor 51, or may be obtained indirectly by estimating the water temperature from other parameters related to the water temperature. For example, since the outside air temperature and the water temperature are related, the water temperature may be estimated from the outside air temperature, the change in the average water temperature over the course of one year is memorized, and the water supply temperature should be regarded as a calendar function. The water temperature may be calculated.
Moreover, since the heat storage fluid W is heated so that the temperature of the heat storage fluid W becomes a predetermined target temperature on the heat pump cycle C side, the temperature of the heat storage fluid W can be obtained from the heat pump cycle C side. Is possible.
[0062]
If the target temperature is set in advance throughout the year as the temperature of the heat storage fluid W, the set target temperature may be used as the temperature of the heat storage fluid W.
The flow rate sensor 54 may be installed upstream of the branch point between the water supply pipe 4 and the branch pipe 28 or downstream of the mixing valve 29 to detect the entire hot water supply flow rate. In this case, from the values of the temperature sensors 51, 52, and 53, the flow rates of the hot water supply heat exchanger 6 and the branch pipe 28 can be estimated by calorie calculation.
[0063]
(Modification)
The tank 2 shown in each embodiment does not necessarily need to use a resin material, and may be formed of a metal material. Moreover, the shape of the tank 2 may not be a rectangular parallelepiped shape but may be a cylindrical shape, for example.
In the hot water supply heat exchanger 6 described in the first embodiment, the secondary side passage 6b is provided inside the primary side passage 6a, but conversely, the secondary side passage 6b is provided outside the primary side passage 6a. May be. Moreover, the material used for the inner tube 6B and the outer tube 6A described above is an example. For example, the inner tube 6B can use aluminum having high thermal conductivity, and the outer tube 6A can be made of metal. Furthermore, you may cover the outer peripheral surface of the heat exchanger 6 for hot water supply with the heat insulating material 35 (refer FIG. 2).
[0064]
Further, the hot water supply heat exchanger 6 shown in each embodiment is not limited to the double tube structure including the inner tube 6B and the outer tube 6A, and may be a multi-hole tube structure as shown in FIG. 12, for example. This is configured by adhering a primary side plate 36 in which a plurality of primary side passages 6a are formed and a secondary side plate 37 in which a plurality of secondary side passages 6b are similarly formed with an adhesive or the like. Each of the plates 36 and 37 can be made of copper, aluminum, or the like having high thermal conductivity, and the periphery of the two plates 36 and 37 that are bonded together may be covered with a heat insulating material 38.
The electric pump 3 and the turbine shown in each embodiment may be arranged in the tank 2. In this case, since the heated heat storage fluid W is not taken out of the tank 2, the heat loss can be further reduced as compared with the case where only the hot water supply heat exchanger 6 is disposed in the tank 2.
[Brief description of the drawings]
FIG. 1 is an overall view showing a configuration of a hot water supply apparatus (first embodiment).
FIG. 2 is a cross-sectional view of an outer tube and an inner tube that constitute a heat exchanger for hot water supply.
FIG. 3 is an overall view showing the configuration of a hot water supply apparatus (second embodiment).
FIG. 4 is a configuration diagram showing a flow rate control mechanism for a heat storage fluid (third embodiment).
FIG. 5 is a configuration diagram showing a flow rate control mechanism for a heat storage fluid (fourth embodiment).
FIG. 6 is an overall view showing a configuration of a hot water supply apparatus (fifth embodiment).
FIG. 7 is an overall view showing the configuration of a hot water supply apparatus (sixth embodiment).
FIG. 8 is an overall view showing the configuration of a hot water supply apparatus (seventh embodiment).
FIG. 9 is an overall view showing the configuration of a hot water supply apparatus (eighth embodiment).
FIG. 10 is an overall view showing a configuration of a hot water supply apparatus (9th embodiment).
FIG. 11 is an overall view showing the configuration of a hot water supply apparatus (a tenth embodiment).
FIG. 12 is a cross-sectional view of a heat exchanger for hot water supply (modified example).
FIG. 13 is a cross-sectional view of a conventional hot water supply apparatus.
[Explanation of symbols]
1 Water heater
2 tanks
3 Electric pump (pump means)
4 Water supply pipe (pipe for hot water supply)
5 Hot water supply pipe (Pipe for hot water supply)
6 Heat exchanger for hot water supply (opposite flow heat exchanger)
6A Outer pipe (first pipe)
6B Inner pipe (second pipe)
7 Pump controller (flow rate control means)
14 Inflow pipe (fluid heating passage)
15 Outflow pipe (fluid heating passage)
17 Suction pipe (circulation passage)
18 Discharge pipe (circulation passage)
20 Water temperature sensor (hot water temperature control means)
22 First impeller (pump means)
23 Second impeller (pump means)
26 Electric flow control valve (flow control valve)
27 Temperature detection flow control valve (flow control valve)
28 Branch piping (hot water temperature control means)
29 Mixing valve (hot water temperature control means)
35 Insulation
51 1st temperature sensor (1st temperature detection means)
52 2nd temperature sensor (2nd temperature detection means)
54 Flow rate sensor (flow rate detection means)
C heat pump cycle (heating means)
W Heat storage fluid

Claims (10)

  1. A tank for storing heat storage fluid;
    Heating means for heating the heat storage fluid in the tank;
    A first pipe through which the heat storage fluid circulates and a second pipe through which hot water supply water flows are provided adjacent to each other, and the heat storage fluid and hot water supply water are opposed to each other. A counter-flow heat exchanger that performs heat exchange;
    A hot water supply pipe connected to the second pipe and leading hot water supply water to the terminal;
    A circulation path for taking out the heat storage fluid heated from the upper part in the tank, passing the first pipe, and returning it to the lower part in the tank;
    Pump means for circulating the heat storage fluid in the circulation passage;
    Flow rate control means for controlling the flow rate of the heat storage fluid flowing through the first pipe through the circulation passage;
    A fluid heating passage for taking out the heat storage fluid from the lower part in the tank and supplying it to the heating means, and returning the heat storage fluid heated by the heating means to the upper part in the tank;
    Heat exchange with the heat storage fluid flowing through the first pipe, and mixing means for mixing the hot water and the unheated hot water flowing out of the second pipe,
    The flow rate control means is
    First temperature detecting means for detecting the temperature of hot water for water flowing into the second pipe;
    Flow rate detecting means for detecting the flow rate of hot water for water passing through the second pipe,
    Based on the target temperature of hot water supplied from the hot water pipe, the temperature of hot water detected by the first temperature detecting means, and the flow rate of hot water detected by the flow rate detecting means , Adjusting the flow rate of the heat storage fluid flowing through the first pipe so that the temperature difference between the temperature of the heat storage fluid and the temperature of the hot water supply water flowing into the second pipe falls within a predetermined range ;
    The target temperature is set to a temperature that is higher by a predetermined temperature than the temperature at which hot water is actually supplied, and hot water heated up to the target temperature is mixed with unheated hot water by the mixing means, so that the temperature of the hot water is increased. The hot water supply device is characterized in that the temperature is lowered to a temperature at which the hot water should be supplied.
  2. 2. The hot water supply according to claim 1, wherein the heating means is a supercritical heat pump cycle in which a pressure of the refrigerant is equal to or higher than a critical pressure, and the heat storage fluid is heated by the refrigerant whose pressure is increased to the critical pressure or higher. apparatus.
  3. The flow rate control means includes second temperature detection means for detecting the temperature of hot water for water flowing out from the second pipe,
    As the temperature of the water for hot water supply to be detected by the second temperature detecting means becomes the target temperature, according to claim 1, characterized in that to correct the flow rate of the heat storage fluid flowing through the first pipe Water heater.
  4. The hot water supply apparatus according to any one of claims 1 to 3, wherein the target temperature is set to a constant temperature higher than a normally used hot water temperature .
  5. Hot water supply temperature adjustment means for adjusting the temperature of hot water for hot water supply by mixing the water heated by the heat exchanger with the hot water heated by the heat exchanger,
    The hot water supply apparatus according to any one of claims 1 to 4, wherein the heat exchanger is disposed in the tank .
  6. The hot water supply apparatus according to claim 5, wherein the circulation passage and the pump means are provided in the tank .
  7. The hot water supply apparatus according to claim 5 or 6, wherein the heat exchanger is covered with a heat insulating material .
  8. The pump means is provided with a first impeller that rotates in response to the energy of hot water flowing through the hot water supply pipe, and a second impeller that is provided in the circulation passage and is rotated by transmission of rotation of the first impeller. The hot water supply device according to any one of claims 5 to 7, further comprising an impeller, wherein the heat storage fluid is circulated through the circulation passage by the rotation of the second impeller .
  9. The hot water supply apparatus according to any one of claims 1 to 8, wherein the tank is open to an atmospheric pressure .
  10. The hot water supply temperature adjusting means includes:
    A mixing valve provided downstream of the heat exchanger in the hot water supply pipe;
    A branch pipe branched from the hot water supply pipe upstream of the heat exchanger and connected to the mixing valve;
    A water temperature sensor that detects the temperature of the hot water supply downstream from the mixing valve;
    6. The hot water supply apparatus according to claim 5 , wherein a mixing ratio of hot water and water in the mixing valve is adjusted based on a temperature detected by the water temperature sensor .
JP33975099A 1999-11-30 1999-11-30 Water heater Expired - Fee Related JP4104261B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP33975099A JP4104261B2 (en) 1999-11-30 1999-11-30 Water heater

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP33975099A JP4104261B2 (en) 1999-11-30 1999-11-30 Water heater
DE2000159134 DE10059134B4 (en) 1999-11-30 2000-11-29 Water heater

Publications (2)

Publication Number Publication Date
JP2001153458A JP2001153458A (en) 2001-06-08
JP4104261B2 true JP4104261B2 (en) 2008-06-18

Family

ID=18330465

Family Applications (1)

Application Number Title Priority Date Filing Date
JP33975099A Expired - Fee Related JP4104261B2 (en) 1999-11-30 1999-11-30 Water heater

Country Status (1)

Country Link
JP (1) JP4104261B2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101631503B1 (en) 2014-07-07 2016-06-22 원철호 Heating and cooling and hot water supplying apparatus using geothermy

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4485406B2 (en) * 2005-04-25 2010-06-23 東京電力株式会社 Hot water storage water heater
JP2006322644A (en) * 2005-05-18 2006-11-30 Matsushita Electric Ind Co Ltd Heat exchanger
JP4926620B2 (en) * 2006-03-31 2012-05-09 大阪瓦斯株式会社 Open air storage tank
JP5325281B2 (en) * 2006-03-31 2013-10-23 大阪瓦斯株式会社 Open air storage tank
JP2008082664A (en) * 2006-09-28 2008-04-10 Daikin Ind Ltd Hot water circulating heating system
JP2008138991A (en) * 2006-12-05 2008-06-19 Sanyo Electric Co Ltd Heating tank and hot water storage tank
JP4787284B2 (en) * 2007-03-27 2011-10-05 ダイキン工業株式会社 Heat pump type water heater
JP2008275302A (en) * 2007-03-30 2008-11-13 Daikin Ind Ltd Heating hot water supply apparatus
JP2009074750A (en) * 2007-09-21 2009-04-09 Kandenko Co Ltd Hot water supply system
JP4539777B2 (en) * 2008-02-01 2010-09-08 ダイキン工業株式会社 Hot water storage water heater and hot water heater
JP2009250542A (en) * 2008-04-08 2009-10-29 Hitachi Appliances Inc Water heater
JP4746078B2 (en) * 2008-07-31 2011-08-10 三菱電機株式会社 Heat pump water heater

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101631503B1 (en) 2014-07-07 2016-06-22 원철호 Heating and cooling and hot water supplying apparatus using geothermy

Also Published As

Publication number Publication date
JP2001153458A (en) 2001-06-08

Similar Documents

Publication Publication Date Title
US7603872B2 (en) Heat-pump hot water supply apparatus
EP2241829B1 (en) Heat pump type hot water supply system
KR101329509B1 (en) Hot water circulation system associated with heat pump and method for controlling the same
JP5642207B2 (en) Refrigeration cycle apparatus and refrigeration cycle control method
CN102425872B (en) Refrigeration cycle device
US6964820B2 (en) Water recirculation in fuel cell power plant
JP3297657B2 (en) Heat pump water heater
KR100859245B1 (en) Heat pump hot water supply floor heating apparatus
JP3915770B2 (en) Heat pump water heater
JP4059616B2 (en) Heat pump water heater
ES2379167T3 (en) Hot water supply system with storage tank
JP5238001B2 (en) Refrigeration cycle equipment
KR100524578B1 (en) Heat pump type hot water supply heater
JP2007003162A (en) Storage type heat pump hot water supply device
US8657207B2 (en) Hot water circulation system associated with heat pump and method for controlling the same
JP4058696B2 (en) Heat pump hot water supply system
JPWO2003048652A1 (en) Waste heat recovery system
JP2010007953A (en) Hot water supply system
CN203396150U (en) Refrigerating cycle device
JP2002364925A (en) Hybrid water-heater
JP3737414B2 (en) Water heater
JP2002206805A (en) Hot water supply apparatus
JP3632645B2 (en) Heat pump water heater
JP5071434B2 (en) Heat pump water heater
KR101222331B1 (en) Heat-pump hot water apparatus

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20060516

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20070823

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20070827

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20071026

A02 Decision of refusal

Free format text: JAPANESE INTERMEDIATE CODE: A02

Effective date: 20071225

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20080225

A911 Transfer of reconsideration by examiner before appeal (zenchi)

Free format text: JAPANESE INTERMEDIATE CODE: A911

Effective date: 20080229

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20080325

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20080325

R150 Certificate of patent or registration of utility model

Ref document number: 4104261

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150

Free format text: JAPANESE INTERMEDIATE CODE: R150

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20110404

Year of fee payment: 3

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130404

Year of fee payment: 5

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130404

Year of fee payment: 5

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20140404

Year of fee payment: 6

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

S533 Written request for registration of change of name

Free format text: JAPANESE INTERMEDIATE CODE: R313533

R350 Written notification of registration of transfer

Free format text: JAPANESE INTERMEDIATE CODE: R350

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

LAPS Cancellation because of no payment of annual fees