EP2770278B1 - Chauffe-eau - Google Patents

Chauffe-eau Download PDF

Info

Publication number
EP2770278B1
EP2770278B1 EP14155464.2A EP14155464A EP2770278B1 EP 2770278 B1 EP2770278 B1 EP 2770278B1 EP 14155464 A EP14155464 A EP 14155464A EP 2770278 B1 EP2770278 B1 EP 2770278B1
Authority
EP
European Patent Office
Prior art keywords
heat medium
hot water
refrigerant
heat
water tank
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.)
Active
Application number
EP14155464.2A
Other languages
German (de)
English (en)
Other versions
EP2770278A1 (fr
Inventor
Shigeo Aoyama
Teruo Yamamoto
Kazuhito Nakatani
Yoshitsugu Nishiyama
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Corp
Original Assignee
Panasonic Corp
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 Panasonic Corp filed Critical Panasonic Corp
Publication of EP2770278A1 publication Critical patent/EP2770278A1/fr
Application granted granted Critical
Publication of EP2770278B1 publication Critical patent/EP2770278B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers

Definitions

  • the present invention relates to a water heater for producing high temperature water by a heat pump heat source.
  • a conventional water heater of this kind water is heated by a heat pump heat source which uses carbon dioxide refrigerant, and the water heater produces warm water having higher temperature than a heat pump heat source which uses CFC-based refrigerant.
  • the produced high temperature water is stored in a hot water tank, and the high temperature water is supplied (see patent document 1 for example).
  • Fig. 8 shows a water heater described in patent document 1.
  • this water heater includes a heat pump unit 52 having a gas cooler (hot water-supply heat exchanger) 51, and a hot water storing unit 54 having a hot water tank 53. Hot water boiled by the gas cooler 51 is stored in the hot water tank 53.
  • a heat pump unit 52 having a gas cooler (hot water-supply heat exchanger) 51
  • a hot water storing unit 54 having a hot water tank 53. Hot water boiled by the gas cooler 51 is stored in the hot water tank 53.
  • the heat pump unit 52 includes a refrigerant circuit formed by annularly connecting a compressor 55, the gas cooler 51, an expansion valve (decompressor) 56 and an evaporator 57 to one another through a refrigerant pipes. Carbon dioxide (CO2) refrigerant circulates through the refrigerant circuit as refrigerant.
  • the hot water storing unit 54 includes a circulation pump 58 through which hot water circulates, the hot water tank 53, a water supply pipe 60 through which water is supplied from a water pipe to the hot water tank 53, and a hot water supply pipe 59 through which high temperature water stored in the hot water tank 53 is supplied.
  • the circulation pump 58, the hot water tank 53 and the gas cooler 51 are annularly connected to one another through a water supply pipe, thereby configuring a water circuit.
  • Water stored in a lower portion of the hot water tank 53 is conveyed to the gas cooler 51 by the circulation pump 58, the conveyed water and high temperature and high pressure gas refrigerant compressed by the compressor 55 exchange heat in the gas cooler 51, and high temperature water (e.g., 85°C) is produced.
  • the produced high temperature water is conveyed to the hot water tank 53 through the water circuit and is stored therein, the high temperature water is made to flow out from the hot water supply pipe 59 as need arises and the high temperature water is supplied. If carbon dioxide is used as refrigerant, it is possible to produce higher temperature water as compared with CFC-based refrigerant.
  • a heat-transfer pipe is wound around an outer wall surface of a hot water tank, and a vapor compression type refrigeration cycle is used as a heat source.
  • High temperature and high pressure refrigerant discharged from a compressor is made to flow into a heat-transfer pipe which is wound around a hot water tank, and water in the hot water tank is heated (see patent document 2 for example).
  • Fig. 9 shows a water heater described in patent document 2.
  • the water heater 100 includes a refrigerant circuit 90 through which refrigerant circulates, and a hot water tank 110 in which warm water is stored.
  • the refrigerant circuit 90 is configured by annularly connecting a compressor 101, a hot water storing-side heat exchanger 116, an expansion device 104 and an air-side heat exchanger 106 to one another through refrigerant pipes.
  • a heat-transfer pipe is disposed in a hot water tank 110 as a hot water storing-side heat exchanger 116 such that the heat-transfer pipe is in contact with an outer wall surface of the hot water tank 110. Water is supplied to the hot water tank 110 through a water supply pipe 119.
  • refrigerant flows through the refrigerant circuit 90 in directions of solid arrows in Fig. 9 .
  • Gas phase high temperature and high pressure refrigerant discharged from the compressor 101 flows into the hot water storing-side heat exchanger 116, releases heat to water in the hot water tank 110 through a partition thereof, and condenses.
  • the refrigerant in the supercooled liquid state which is liquefied and condensed in the hot water storing-side heat exchanger 116 is decompressed by the expansion device 104, and is brought into a low pressure gas/liquid two phase state, and the refrigerant flows into the air-side heat exchanger 106 (evaporator).
  • the refrigerant absorbs heat from outside air sucked by an outdoor fan 105 in the air-side heat exchanger 106 (evaporator).
  • the refrigerant absorbs heat from outside air sucked by an outdoor fan 105 in the air-side heat exchanger 106 (evaporator) and evaporates, and the refrigerant phase-changes from the gas/liquid two phase state to a superheated state. Then, the refrigerant flows into the compressor 101 and is again compressed, and is brought into a high temperature and high pressure gas phase state.
  • hot water in the hot water tank 110 is heated, and high temperature water can be stored.
  • EP2362164A2 discloses a heat pump system, the operation of which is controlled using a temperature difference between a water inlet and a water outlet of a heat exchanger, exchanging heat between a refrigerant and water, and a control method thereof.
  • the heat pump system includes temperature sensors installed on a water circulation pipe unit at water inlet and outlet sides of a heat exchanger, and heats a load to a set temperature by controlling a compressor or an expander according to a difference between temperatures sensed by the temperature sensors.
  • a temperature of water transmitted to the load is set to be greater than a target load temperature by a reference value, and if the temperature difference is smaller than a designated value, the operation of the heat pump system is stopped.
  • the present invention has been accomplished to solve the conventional problems, and it is an object of the invention to provide a water heater capable of efficiently producing high temperature water while suppressing precipitation of scale.
  • the present invention provides a water heater according to claim 1.
  • the precipitation of scale is prone to be generated especially when water having much hardness component is heated to high temperature and this high temperature water flows through a pipe having a small diameter like an outlet of a heat medium of a gas cooler.
  • the heat medium circuit and a hot water supply circuit are separated from each other, it is possible to effectively suppress the precipitate of scale.
  • a first aspect of the present invention provides a water heater including: a refrigerant circuit configured by annularly connecting, to one another through refrigerant pipes, a compressor for compressing refrigerant, a first radiator for exchanging heat between the refrigerant and heat medium, an expansion device for expanding the refrigerant, and an evaporator for evaporating the refrigerant, and the refrigerant circulating through the refrigerant circuit; a hot water tank in which water is stored; and a heat medium circuit configured by annularly connecting, to one another through heat medium pipes, the first radiator, a second radiator for exchanging heat between the heat medium and the water, and a circulation device, and the heat medium circulating through the heat medium circuit, wherein the refrigerant circulating through the refrigerant circuit is carbon dioxide, and in the second radiator, the heat medium pipe is wound around an outer surface of the hot water tank, and the heat medium releases heat to water in the hot water tank.
  • the precipitation of scale is prone to be generated especially when water having much hardness component is heated to high temperature and this high temperature water flows through a pipe having a small diameter like an outlet of a heat medium of a gas cooler.
  • the heat medium circuit and a hot water supply circuit are separated from each other, it is possible to effectively suppress the precipitate of scale. That is, the heat medium circuit which is under such a temperature condition that high temperature fluid circulates and scale is prone to be precipitated is closed. Hence, fluid having much hardness component does not flow any time, and it is possible to effectively suppress the precipitate of scale.
  • the heat medium releases heat to water in the hot water tank in the second radiator, and temperature of the heat medium is sufficiently lowered. Thereafter, the heat medium flows out from the second radiator and flows into the first radiator. That is, since the temperature of the heat medium flowing into the first radiator is lowered, excessive pressure rise on the high pressure side in the refrigerant circuit is suppressed. Since a circulation water amount of heat medium which flows through the heat medium pipe is reduced, it is possible to increase the length of the heat medium pipe of the second radiator, and to reduce a diameter of the heat medium pipe while suppressing the increase in the pressure loss in the heat medium pipe.
  • L/S (m/mm 2 ) is 2.8 or more and 5.3 or less.
  • the heat medium flows from an upper portion to a lower portion of the second radiator.
  • water in the hot water tank is heated in order from above at the time of hot water storing operation, temperature of upper side water in the hot water tank is maintained high, and temperature of lower side water is maintained low. That is, temperature stratification is formed in the hot water tank while suppressing natural convection of hot water in the hot water tank.
  • a temperature difference between the heat medium and water in the hot water tank can appropriately be maintained. It is possible to efficiently heat water while suppressing temperature rise of heat medium which flows into the first radiator. Therefore, it is possible to enhance energy saving as a water heater.
  • Fig. 1 is a schematic diagram of a water heater in an embodiment of the present invention.
  • the water heater of the embodiment includes a heat source unit 1 for heating heat medium, and a tank unit 2 having a hot water tank 21 in which warm water produced by the heated heat medium is stored.
  • the water heater of the embodiment includes a refrigerant circuit 3 as a heat pump unit, i.e., a heat source, through which refrigerant circulates, a heat medium circuit 4 through which heat medium circulates, and a hot water supply circuit 5 which supplies water into the hot water tank and supplies heated warm water.
  • a refrigerant circuit 3 as a heat pump unit, i.e., a heat source, through which refrigerant circulates
  • a heat medium circuit 4 through which heat medium circulates
  • a hot water supply circuit 5 which supplies water into the hot water tank and supplies heated warm water.
  • CO2 carbon dioxide
  • water is used as heat medium which circulates through the heat medium circuit 4.
  • the refrigerant circuit 3 is configured by annularly connecting a compressor 11, a refrigerant/heat medium heat exchanger 12, an expansion valve (expansion device) 13 which expands refrigerant, and a refrigerant/air heat exchanger 14 to one another through refrigerant pipes.
  • the refrigerant/heat medium heat exchanger 12 functions as a first radiator, and exchanges heat between refrigerant and heat medium.
  • the refrigerant/heat medium heat exchanger 12 includes a refrigerant flow path through which refrigerant flows, and a heat medium flow path through which heat medium flows. Refrigerant and heat medium exchange heat through partitions forming the respective flow paths, thereby producing high temperature heat medium.
  • the refrigerant/air heat exchanger 14 is a fin tube heat exchanger, functions as an evaporator, and exchanges heat between refrigerant and air.
  • a blower 16 disposed adjacent to the refrigerant/air heat exchanger 14 sends air to the heat exchanger 14, and the sent air and refrigerant exchange heat.
  • the heat medium circuit 4 is configured by annularly connecting, to one another through heat medium pipes, the refrigerant/heat medium heat exchanger 12, an expansion tank 24 corresponding to expansion of warm water, a hot water-storing heat exchanger 22 which functions as a second radiator, and a circulation pump (circulation device) 23.
  • the hot water-storing heat exchanger 22 is spirally wound around an outer periphery of the hot water tank 21 such that the heat medium pipe comes into contact with an outer surface of the hot water tank 21. That is, high temperature heat medium produced in the refrigerant/heat medium heat exchanger 12 flows into the hot water-storing heat exchanger 22, exchanges heat with water in the hot water tank 21, and heats water in the hot water tank 21. After the heat medium exchanges heat with water in the hot water tank 21, the heat medium flows out from the hot water-storing heat exchanger 22. At this time, to reduce thermal resistance between the heat medium pipe configuring the hot water-storing heat exchanger 22 and the outer surface of the hot water tank 21, adhesive 25 for facilitating adhesion and thermal conductivity is applied to the outer surface of the hot water tank 21.
  • L/S (m/mm 2 ) L/S (m/mm 2 ) is 2.8 or more and 5.3 or less.
  • the hot water supply circuit 5 includes the hot water tank 21, a water supply pipe 5b connected to a lower portion of the hot water tank 21 and supplies water to the hot water tank 21, and a hot water supply pipe 5a connected to an upper portion of the hot water tank 21 and supplies warm water to a user.
  • a hot water storing operation for heating water in the hot water tank 21 to produce high temperature water high temperature heat medium heated in the refrigerant/heat medium heat exchanger 12 flows into the hot water-storing heat exchanger 22, this high temperature heat medium and water stored in the hot water tank 21 exchange heat through the heat medium pipe of the hot water-storing heat exchanger 22 and the hot water tank 21.
  • High temperature water stored in the hot water tank 21 is supplied to a user through the hot water supply pipe 5a. According to this, if an amount of hot water in the hot water tank 21 is reduced, water is supplied from the water supply pipe 5b to the hot water tank 21
  • the hot water tank 21 is composed of a cylindrical central portion 21a, an upper member 21b and a lower member 21c. One end of each of the upper member 21b and the lower member 21c opens and the other end is formed into a dome shape.
  • the central portion 21a, the upper member 21b and the lower member 21c are welded and bonded to one another through bonded portions 21d.
  • the heat medium pipe forming the hot water-storing heat exchanger 22 is disposed around the outer periphery of the hot water tank 21. This heat medium pipe comes into contact with the outer surface of the hot water tank 21 at an inlet portion 4a, the heat medium pipe is spirally wound up to a lower portion of the hot water tank 21, and separates from the outer periphery of the hot water tank 21 at an outlet portion 4b of the lower member 21c. As shown in Fig. 2 , the upper member 21b is provided with the inlet portion 4a, and the lower member 21c is provided with the outlet portion 4b.
  • a portion of the heat medium pipe from the inlet portion 4a to the outlet portion 4b is in contact with the outer surface of the hot water tank 21, and the hot water-storing heat exchanger 22 is formed. Since the heat medium pipe is spirally wound from the upper member 21b to the lower member 21c, it is possible to form the hot water-storing heat exchanger 22 over the entire hot water tank 21. Therefore, it is possible to heat entire water in the hot water tank 21 to high temperature.
  • Water is supplied from the water supply pipe 5b connected to a lower connected portion 5d of the lower member 21c to the hot water tank 21, high temperature water heated in the hot water-storing heat exchanger 22 flows out from the hot water supply pipe 5a connected to an upper connected portion 5c of the upper member 21b, and the high temperature water is supplied to a user.
  • water is supplied from the water supply pipe 5b to the hot water tank 21 at a location higher than the outlet portion 4b. That is, the lower connected portion 5d is disposed at a location higher than the outlet portion 4b in the vertical direction of the hot water tank 21. According to this, at least a portion of the heat medium pipe which forms the hot water-storing heat exchanger 22 is disposed at a location lower than the lower connected portion 5d. Therefore, it is possible to efficiently heat low temperature water which is prone to stay in the lower portion of the hot water tank 21 by natural convection, and to produce high temperature water in the entire interior of the hot water tank 21.
  • hot water is supplied from the hot water supply pipe 5a to a user at a location higher than the inlet portion 4a. That is, the upper connected portion 5c is disposed at a location higher than the inlet portion 4a in the vertical direction of the hot water tank 21. According to this, high temperature water which is heated by the hot water-storing heat exchanger 22 and which is stored in the upper portion in the hot water tank 21 by the natural convection can efficiently be used for hot water supply.
  • a connection relation between the hot water supply pipe 5a and the hot water tank 21, a connection relation between the water supply pipe 5b and the hot water tank 21, a positional relation between the inlet portion 4a and the upper connected portion 5c, and a positional relation between the outlet portion 4b and the lower connected portion 5d can selectively be applied.
  • Fig. 3 is a P-h diagram (Mollier diagram) showing a relation between refrigerant pressure P of the refrigerant circuit and refrigerant enthalpy h
  • Fig. 4 is a schematic diagram showing water temperature variation in the hot water tank 21.
  • CO2 refrigerant circulates through the refrigerant circuit 3 in directions of solid arrows in Fig. 1 . Then, CO2 refrigerant in a saturated or superheated state is sucked by the compressor 11 (point a in Fig. 3 ), the CO2 refrigerant is compressed up to supercritical pressure by the compressor 11, and the CO2 refrigerant is brought into a high temperature and high pressure gas state (point b in Fig. 3 ). The CO2 refrigerant in the high temperature and high pressure gas state is sent to the refrigerant/heat medium heat exchanger 12, the CO2 refrigerant exchanges heat with heat medium, and high temperature heat medium is produced.
  • the CO2 refrigerant is cooled in the refrigerant/heat medium heat exchanger 12, the CO2 refrigerant flows out from the refrigerant/heat medium heat exchanger 12 and then flows into the expansion valve 13 (point c in Fig. 3 ). Thereafter, the CO2 refrigerant is decompressed and expanded by the expansion valve 13, and is brought into a liquid state (points c to d in Fig. 3 ), and the CO2 refrigerant flows into the refrigerant/air heat exchanger 14.
  • the CO2 refrigerant absorbs heat from air which is sent by the blower 16 in the refrigerant/air heat exchanger 14 and evaporates and is brought into a saturated gas state or superheated gas state and again flows into the compressor 11 (point a in Fig. 3 ).
  • high temperature heat medium produced in the refrigerant/heat medium heat exchanger 12 flows in directions of dotted line arrows in Fig. 1 .
  • the heat medium flows from an upper portion of the hot water tank 21 into the hot water-storing heat exchanger 22 through the expansion tank 24 existing on the inlet side of the hot water tank 21.
  • Heat energy possessed by the high temperature heat medium is transmitted to water in the hot water tank 21 through the heat medium pipe of the hot water-storing heat exchanger 22 and the hot water tank 21, and high temperature water is produced.
  • the operation efficiency of the heat pump is enhanced.
  • a contact area is increased.
  • a heat passage rate is increased.
  • Fig. 5 shows a relation between L/S and a ratio (called "operation efficiency ratio", hereinafter) of average operation efficiency when the conditions are changed. That is, Fig. 5 shows a case where heating temperature of water in the hot water tank 21 is 55°C using the conventional CFC-based refrigerant and a case where the heating temperature of water in the hot water tank 21 is 85°C using carbon dioxide refrigerant.
  • Fig. 6 shows a relation between L/S and a pressure loss dP in the heat medium pipe of the hot water-storing heat exchanger 22 under the same conditions as those shown in Fig. 5 .
  • Fig. 7 is a schematic diagram for determining a contact length between the hot water tank 21 and the heat medium pipe forming the hot water-storing heat exchanger 22.
  • a vertical axis in Fig. 5 shows an operation efficiency ratio.
  • the operation efficiency ratio shows a relative ratio in which a peak value ⁇ o of operation efficiency ⁇ when heating temperature of water in the hot water tank 21 is set to 55°C is defined as 100%.
  • a horizontal axis in Fig. 5 shows L/S. If a length L of one heat medium pipe configuring the hot water-storing heat exchanger 22 is increased or the inner diameter di of the heat medium pipe is reduced, L/S is increased, and if the length L is reduced or the inner diameter di is increased, L/S is reduced.
  • the hot water-storing heat exchanger 22 when the length of one heat medium pipe configuring the hot water-storing heat exchanger 22 is defined as L (m) and an in-pipe cross-sectional area of the heat medium pipe is defined as S (mm 2 ), the hot water-storing heat exchanger 22 is configured such that L/S (m/mm 2 ) becomes 2.8 or more and 5.3 or less. According to this configuration, it is possible to maximize the operation efficiency ⁇ while taking a performance error of constituent parts of the compressor and other refrigerant circuit into consideration.
  • the peak value ⁇ o of the operation efficiency ⁇ is varied depending upon L/S due to the following phenomenon: That is, as L/S is gradually increased from zero, i.e., as the length L of the heat medium pipe of the hot water-storing heat exchanger 22 is increased, a surface area of the hot water-storing heat exchanger 22 is increased. Therefore, there is a tendency that the operation efficiency ⁇ is gradually increased. If the L/S is increased, this means that the length L of the heat medium pipe is increased or the in-pipe pipe di of the heat medium pipe is reduced.
  • the operation efficiency ⁇ has such characteristics that the operation efficiency ⁇ is increased together with increase of L/S, and after the operation efficiency ⁇ reaches the peak value ⁇ o, the operation efficiency is gradually deteriorated. If heating temperature of water in the hot water tank 21 is set to 85°C, it is necessary to further increase a compression ratio in the compressor 11 as compared with a case where the heating temperature is 55°C. Therefore, if the compressor power is increased, the operation efficiency ⁇ is lowered as compared with the case where the heating temperature is 55°C.
  • heat medium is produced using CO2 refrigerant and water in the hot water tank 21 is heated to high temperature, i.e., 85°C, it is possible to increase the temperature difference between the water in the hot water tank 21 and the heat medium as compared with a case where the heating temperature is 55°C. According to this, since the flow rate of circulating heat medium can be reduced under such a condition that average heating abilities are equal to each other, a pressure loss in the heat medium pipe which configures the hot water-storing heat exchanger 22 has such characteristics that the pressure loss is reduced as compared with the case where the heating temperature is 55°C as shown in Fig. 6 .
  • the operation efficiency ⁇ reaches the peak value ⁇ o under such a condition that L/S (m/mm 2 ) is between 1.2 or more and 1.8 or less.
  • the heat medium pipe is configured such that the L/S (m/mm 2 ) falls within a range of 2.8 or more and 5.3 or less. According to this, it is possible to maximize the average operation efficiency while taking the performance error (3%) of constituent parts of the compressor and other refrigerant circuit into consideration.
  • water is used as heat medium which circulates through the heat medium circuit 4 in the embodiment, the invention is not limited to this, and antifreeze liquid may be used for example.
  • the heat medium circuit 4 is provided with the expansion tank 24 in the embodiment, if a circulation amount of heat medium is small and an expansion amount of heat medium is small, the heat medium circuit 4 may be not provided with the expansion tank 24.
  • the water heater of the present invention can efficiently produce high temperature water while suppressing precipitation of scale, the invention can be applied to domestic or professional use water heaters.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Claims (1)

  1. Chauffe-eau comprenant: un circuit de réfrigérant (3) configuré par raccordement annulaire, l'un à l'autre par des tuyaux de réfrigérant, un compresseur (11) pour comprimer un réfrigérant, un premier radiateur pour échanger de la chaleur entre le réfrigérant et un milieu thermique, un dispositif d'expansion (13) pour dilater le réfrigérant, et un évaporateur (14) pour évaporer le réfrigérant, et le réfrigérant circulant à travers le circuit de réfrigérant (3);
    un réservoir d'eau chaude (21) dans lequel de l'eau est stockée; et
    un circuit de milieu thermique (4) configuré par raccordement annulaire, l'un à l'autre par des tuyaux de milieu thermique, le premier radiateur (12), un second radiateur (22) pour échanger de la chaleur entre le milieu thermique et l'eau, et un dispositif de circulation (23), et le milieu thermique circulant à travers le circuit de milieu thermique (4), dans lequel
    le réfrigérant circulant à travers le circuit de réfrigérant (3) est le dioxyde de carbone,
    dans le second radiateur (22), le tuyau de milieu thermique est enroulé autour d'une surface externe du réservoir d'eau chaude (21), et le milieu thermique libère de la chaleur vers l'eau dans le réservoir d'eau chaude (21),
    dans lequel, lorsqu'une longueur entière du tuyau de milieu thermique configurant le second radiateur (22) est définie comme étant L et une aire de section transversale de l'intérieure du tuyau de milieu thermique est définie comme étant S, lorsqu'une capacité de chauffage moyenne est supérieure ou égale à 2,0 kW et inférieure ou égale à 2,5 kW dans des conditions telles que L est supérieure ou égale à 25 m et inférieure ou égale à 45 m, un diamètre interne du tuyau de transfert de chaleur est supérieur ou égal à 3 mm et inférieur ou égal à 28 mm et un volume interne du réservoir d'eau chaude (21) est supérieur ou égal à 150 l et inférieur ou égal à 300 l, L/S est supérieur ou égal à 2,8 m/mm2 et inférieur ou égal à 5,3 m/mm2;
    dans lequel le milieu thermique s'écoule d'une partie supérieure à une partie inférieure du second radiateur (22).
EP14155464.2A 2013-02-25 2014-02-17 Chauffe-eau Active EP2770278B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2013034189A JP2014163566A (ja) 2013-02-25 2013-02-25 給湯装置

Publications (2)

Publication Number Publication Date
EP2770278A1 EP2770278A1 (fr) 2014-08-27
EP2770278B1 true EP2770278B1 (fr) 2019-07-31

Family

ID=50112822

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14155464.2A Active EP2770278B1 (fr) 2013-02-25 2014-02-17 Chauffe-eau

Country Status (3)

Country Link
EP (1) EP2770278B1 (fr)
JP (1) JP2014163566A (fr)
CN (1) CN104006534A (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104864599A (zh) * 2015-04-10 2015-08-26 广东美的暖通设备有限公司 一种高效率换热水箱
GB2543086B (en) 2015-10-08 2018-05-02 Isentra Ltd Water-cooled carbon dioxide refrigeration system
CN106940087A (zh) * 2016-01-04 2017-07-11 艾欧史密斯(中国)热水器有限公司 热泵热水器及水箱
JP2017166761A (ja) * 2016-03-17 2017-09-21 パナソニックＩｐマネジメント株式会社 ヒートポンプ給湯機
CN106196600B (zh) * 2016-08-22 2022-03-29 艾欧史密斯(中国)热水器有限公司 热泵热水器及其组装方法
ES2737673A1 (es) * 2018-07-13 2020-01-15 Robert Art En Pedra S L Sistema para el control de la temperatura de al menos un módulo de almacenamiento energético y método asociado

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5897461U (ja) * 1981-12-23 1983-07-02 株式会社　ト−タルシステム タンクと弓形チユ−ブによる熱交換器
JPS6259337A (ja) 1985-09-09 1987-03-16 Matsushita Electric Ind Co Ltd 給湯装置
US5558273A (en) * 1994-11-10 1996-09-24 Advanced Mechanical Technology, Inc. Two-pipe system for refrigerant isolation
MY125381A (en) * 2000-03-10 2006-07-31 Sanyo Electric Co Refrigerating device utilizing carbon dioxide as a refrigerant.
WO2009057303A1 (fr) * 2007-11-02 2009-05-07 Panasonic Corporation Système d'alimentation en eau chaude
KR101042533B1 (ko) * 2009-08-04 2011-06-17 경희대학교 산학협력단 강제 순환식 태양열 온수 가열기 및 그 제조 방법
JP5308977B2 (ja) 2009-09-28 2013-10-09 サンデン株式会社 給湯システム
KR20110097203A (ko) * 2010-02-25 2011-08-31 삼성전자주식회사 히트 펌프 시스템 및 그 제어방법
JP2012242020A (ja) * 2011-05-20 2012-12-10 Denso Corp ヒートポンプ装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
JP2014163566A (ja) 2014-09-08
EP2770278A1 (fr) 2014-08-27
CN104006534A (zh) 2014-08-27

Similar Documents

Publication Publication Date Title
EP2770278B1 (fr) Chauffe-eau
EP2770277B1 (fr) Chauffe-eau
JP6161005B2 (ja) 冷凍サイクル装置およびそれを備えた温水生成装置
JP5411643B2 (ja) 冷凍サイクル装置および温水暖房装置
KR100758902B1 (ko) 멀티 공기조화 시스템 및 그 제어방법
JP2009133547A (ja) 冷凍サイクル装置
JP2009236403A (ja) 地熱利用ヒートポンプ装置
CN103836790B (zh) 热泵式热水供给装置
JP2017161115A (ja) 空調給湯システム
EP2918921B1 (fr) Générateur d'eau chaude
JP2005077042A (ja) 冷却システム、及び、冷却システムの施工方法
JP6051401B2 (ja) ヒートポンプ式冷暖房給湯装置
JP2013083439A5 (fr)
JP2009092258A (ja) 冷凍サイクル装置
JP4033788B2 (ja) ヒートポンプ装置
JP2009162403A (ja) 空気調和機
JP4661908B2 (ja) ヒートポンプユニット及びヒートポンプ給湯装置
JP2009281631A (ja) ヒートポンプユニット
JP2015224845A (ja) 冷凍サイクル装置
CN107178823A (zh) 空调供热水系统
JP5413594B2 (ja) ヒートポンプ式給湯装置
KR101286699B1 (ko) 히트펌프를 이용한 냉,난방장치
JP5997057B2 (ja) ヒートポンプ式加熱装置
JP5793715B2 (ja) 空気調和装置
JP2014202365A (ja) 温水生成装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20140217

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

R17P Request for examination filed (corrected)

Effective date: 20150227

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20180208

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20180921

GRAJ Information related to disapproval of communication of intention to grant by the applicant or resumption of examination proceedings by the epo deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTC Intention to grant announced (deleted)
INTG Intention to grant announced

Effective date: 20190305

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1161314

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190815

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602014050747

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20190731

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1161314

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191031

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191031

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191202

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191101

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191130

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200224

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602014050747

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG2D Information on lapse in contracting state deleted

Ref country code: IS

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191030

26N No opposition filed

Effective date: 20200603

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20200217

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20200229

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200217

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200229

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200229

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200217

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200217

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200229

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190731

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20220421

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20240219

Year of fee payment: 11