WO2013108130A2 - Dispositif chauffe-eau à récupération d'eau et de chaleur - Google Patents

Dispositif chauffe-eau à récupération d'eau et de chaleur Download PDF

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Publication number
WO2013108130A2
WO2013108130A2 PCT/IB2013/000481 IB2013000481W WO2013108130A2 WO 2013108130 A2 WO2013108130 A2 WO 2013108130A2 IB 2013000481 W IB2013000481 W IB 2013000481W WO 2013108130 A2 WO2013108130 A2 WO 2013108130A2
Authority
WO
WIPO (PCT)
Prior art keywords
water
fluid
temperature
steam
hot water
Prior art date
Application number
PCT/IB2013/000481
Other languages
English (en)
Other versions
WO2013108130A3 (fr
Inventor
Shaun Mccarthy
Michael Daly
Maxime Sorin
Alan Simpson
Neil DWYER
Original Assignee
Steorn Limited
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 Steorn Limited filed Critical Steorn Limited
Publication of WO2013108130A2 publication Critical patent/WO2013108130A2/fr
Publication of WO2013108130A3 publication Critical patent/WO2013108130A3/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/08—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being steam
    • F22B1/14—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being steam coming in direct contact with water in bulk or in sprays
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H7/00—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release
    • F24H7/02—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release the released heat being conveyed to a transfer fluid
    • F24H7/04—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release the released heat being conveyed to a transfer fluid with forced circulation of the transfer fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/0027—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters using fluid fuel

Definitions

  • the present invention is in the field of fluid heating, more particularly a system designed for instantaneous water heating across a range of temperatures and at variable flow rates.
  • Hot water has myriad uses such as domestic heating, washing and food preparation.
  • greywater where used water from sources such as showers, baths and hand basins is recycled, often close to the original point of use, e.g. in a household.
  • greywater is usually utilised for flushing toilets or soil irrigation.
  • the invention disclosed herein provides a water heater system designed to deliver hot
  • a heat and water recovery component designed to capture the waste hot water after its initial application (for example, a domestic shower) and reuse both the water itself and the heat energy contained therein, feeding both back into the main system, thus reducing 5 overall water and energy usage.
  • the system is composed of a thermal store used as a heat exchanger and a cold water- to-steam mixer element.
  • a cold water supply is heated as it enters the heat exchanger within the thermal store. Since the thermal store operates at high temperatures, this flow of water is turned into steam as it goes through it. The steam is then mixed with cold water.
  • the recovery component of the system incorporates an inlet feed to take the used water. This water will need purification and reheating before it can be reused and this is achieved by passing the water through the thermal store.
  • the amount of heat energy that can be reused is dependent on a number of factors, including the desired output temperature and
  • the thermal store operates typically between 450 - 900 degrees Celsius. Due to this high operating temperature and the consequent amount of thermal energy held, large volumes of hot water can be provided while reducing the size of the thermal store compared to traditional, tank-based stores. Another benefit of this implementation is that operating at over 450 - 900 degrees Celsius. Due to this high operating temperature and the consequent amount of thermal energy held, large volumes of hot water can be provided while reducing the size of the thermal store compared to traditional, tank-based stores. Another benefit of this implementation is that operating at over
  • the high temperature serves to purify the waste water being fed back into the system to ensure its suitability for re-use.
  • the heat contained within this recycled water reduces the overall energy needed for the thermal store to provide hot water at the required temperature.
  • the thermal store is a metallic item heated up to a high temperature.
  • the upper limit 30 of the temperature is dependent on the material used.
  • the volumetric heat capacity of the material used will define the overall volume of the system.
  • High thermal conductivity is a desirable feature of the material used for the thermal store to optimize the heat transfer from the store to the water. Very favorable results are achieved with a material that has a high volumetric heat capacity and a high thermal conductivity such as iron and steel.
  • the thermal store can also include any phase change of the material that will give even more energy stored for the same volume such as molten metals or salts. If this method is used, the material to which the phase change occurs will be encapsulated in a high thermal conductivity metallic casing.
  • the thermal store has holes through which water can enter and be turned into steam before exiting the heat exchanger.
  • the space between the holes is defined by the thermal conductivity of the material used. The higher the thermal conductivity of the material, the larger the space between the holes.
  • the volumetric size of the thermal store is defined by the type of material used such
  • the metallic thermal store can be heated to its selected operating temperature in a number of different ways.
  • the most common way is to use resistive elements such as
  • the water output of the heater is non-pressurized where input and output water pressures are required to remain the same or pressurized in a containment vessel where a controlled output water pressure is required.
  • the steam is mixed with cold water. This can be done in different ways; for example using a sparger, injecting the steam into a tank of cold water, using a heat exchanger or with a mixing valve.
  • system material requirements and weight are significantly less than a tanked system delivering comparable
  • the surface area of the thermal store relative to that of a tank necessary to store water at a desired temperature is substantially lower leading to greatly reduced thermal losses. Further, the energy in the thermal store rapidly heats the cold water input thus reducing waiting time for uses requiring large volumes of hot water delivered over a short timeframe, and the high operating temperature of the system means that lime scale cannot
  • Figure 1 is a perspective view of a heat exchanger core of a system according to the disclosure, partially in phantom, with attached manifold plates and associated pipework;
  • Figure 2 is a cutaway drawing of the steel core of the heat exchanger
  • Figure 3 is a perspective view of the manifold plates of the heat exchanger
  • Figure 4 is a view of the heat exchanger fitted with cartridge heaters and thermocouple
  • Figure 5 is a schematic diagram of the system
  • Figure 6 is an assembly view of the system
  • Figure 7 is a view of the sparger used in mixing the steam and cold water.
  • a heat exchanger 10 is provided. As described, the embodiment is illustrative and the dimensions indicated are approximate and may differ in alternative embodiments. At its
  • the 20 center is a steel core 100.
  • the steel core is, for example, of medium carbon steel EN8 and is 135mm wide, 135mm deep and 100mm tall.
  • Within the steel core are a number of cylindrical holes as illustrated in Figure 2.
  • the horizontal holes are
  • the upper row has the hole centers 27.5mm from the core's top and at 22.5mm, 52.5mm, 82.5mm and 112.5mm on the side face.
  • the lower row has the hole centers 72.5mm from the core's top and the same as the upper row with respect to the side face.
  • a hole 105 Positioned adjacent to one of the horizontal holes is a hole 105 which is 1.5mm in
  • thermocouple 110 30 diameter and 60mm deep, with its hole center at 82.5mm from the side and 35.6mm from the top intended to hold a thermocouple 110.
  • the thermocouple may be a K-Type, model XQ- 182-RS supplied by Radionics Limited, part of Electrocomponents pic of Oxford, United Kingdom.
  • the three columns of vertical holes in the core are arranged as follows: Columns 1 and 3 each comprise three holes with their centers at 32.5mm, 67.5mm and 102.5mm from
  • Column 2 has two holes, with their centers at 50mm and 85mm from the side face. All holes are 13mm in diameter.
  • manifold plates 101, 102 Welded to the top and bottom of the core are two manifold plates 101, 102. These plates are centered on the top and bottom of the steel core, thus substantially completely 5 covering the eight vertical holes 104 running through the core.
  • the plates as illustrated in Figure 3, are of stainless steel grade 304 and are 97mm in width and depth and 20mm tall. There is a recess 115 inside the plates which is 80mm square and 18mm deep, leaving a border 120 of 5mm around the edge. It is this border which is welded to the steel core. At the center of each manifold plate is a hole 125 of 15mm diameter.
  • each manifold plate Welded to the hole in each manifold plate is a grade 304 stainless steel pipe 130, 135 which act as the water inlet (on the bottom of the steel core) and steam outlet (on the top of the steel core). They are 15mm in diameter, 2mm thick and 60mm in length.
  • the end of each pipe is equipped with a threaded boss 140, 145 for connection to inlet and outlet pipework.
  • each of the eight horizontal holes in the steel core is fitted with a cartridge heater 150.
  • cartridge heater 150 are, for example, supplied by Watlow, of St. Louis, Missouri, USA, model HT Firerod, which have a maximum operating temperature of 982 degrees Celsius.
  • Each of the cartridge heaters is connected to a controller 155.
  • a 20 Series 122 Bare Board controller from Zytron Control Products of Trenton, New Jersey, USA is utilised to manage the operating temperature of the system. Power for the system is fed through the controller, in this case a typical 240V mains supply.
  • This board is also connected to the thermocouple 110 located within the steel core as part of the control mechanism.
  • a schematic diagram of the system is provided in Figure 5.
  • the output water temperature of the system is dictated by the ratio of steam to cold water.
  • two proportional flow gate valves 160, 165 as shown in Figures 5 and 6 are used to manage this ratio. These are manually controlled but could equally be electronic and linked to a user-controlled output temperature setting to
  • a source of cold water for example a main water supply.
  • This water supply is subsequently split into two paths 170, 175 as shown in Figures 5 and 6.
  • a first flow 170 is directed into the heat exchanger 10. It flows into the manifold plate 102 and up through the eight vertical channels 104 in the heat exchanger.
  • the 850 degree temperature of the heat exchanger converts the water to steam which passes out of
  • the mixer essentially consists of a mixing junction for steam from the heat exchanger
  • the sparger is illustrated in Figure 7. In this illustrative embodiment it is 71mm long and cylindrical in shape over 51mm of its length with a diameter of 6mm, with a shoulder over its remaining 20mm. The shoulder has a threaded end to allow it to be connected inside the mixer in conjunction with a reducer
  • the resulting hot water flows into a reservoir tank 210 through a 1 ⁇ 2 inch copper pipe.
  • the tank is constructed from 304 gauge stainless steel and is 205mm high, 100mm wide and 50mm deep. It is provided with fittings to take the output from the mixer, installation of an air bleed valve 163 and an output through the 5 second solenoid valve 162.
  • the tank may not be incorporated and the hot water may be drawn off directly from the mixer.
  • the heat exchanger 10, exposed pipework and the tank 210 are all covered in high- performance insulation, in this embodiment Promalight 320 by Promat UK of Bracknell, United Kingdom.
  • Standard mixing valves and aperture control allow for the user to select the desired pressure at the delivery point, the upper limit bounded by choice of materials and consequent operating parameters.
  • all water-contacting surfaces may be made from copper or stainless steel, for example.
  • the temperature range available to the user and the volume of hot water supplied by the system may be varied.
  • the power source used to heat the thermal store is not limited to any one type. Further, while a metallic thermal store is described, those skilled in the art should appreciate that other materials that withstand extreme temperature

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Domestic Hot-Water Supply Systems And Details Of Heating Systems (AREA)

Abstract

L'invention concerne un système conçu pour chauffer l'eau rapidement et efficacement, à composant de récupération d'eau et de chaleur. À l'aide d'un accumulateur thermique se présentant sous la forme d'un échangeur de chaleur, le système mélange de la vapeur et de l'eau froide pour délivrer de l'eau chaude à une température contrôlée par l'utilisateur. La température de fonctionnement élevée de l'accumulateur thermique et son efficacité thermique permettent d'obtenir un moyen compact très efficace de distribution d'eau chaude. La consommation d'eau et d'énergie est encore réduite grâce à un moyen de recyclage de l'eau chaude dans le système en cours de fonctionnement.
PCT/IB2013/000481 2012-01-18 2013-01-18 Dispositif chauffe-eau à récupération d'eau et de chaleur WO2013108130A2 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
US201261587692P 2012-01-18 2012-01-18
US61/587,692 2012-01-18
US201261639128P 2012-04-27 2012-04-27
US61/639,128 2012-04-27
US13/745,239 2013-01-18
US13/745,239 US20140026823A1 (en) 2012-01-18 2013-01-18 Water heater device with heat and water recovery

Publications (2)

Publication Number Publication Date
WO2013108130A2 true WO2013108130A2 (fr) 2013-07-25
WO2013108130A3 WO2013108130A3 (fr) 2013-10-31

Family

ID=48182938

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IB2013/000481 WO2013108130A2 (fr) 2012-01-18 2013-01-18 Dispositif chauffe-eau à récupération d'eau et de chaleur

Country Status (2)

Country Link
US (1) US20140026823A1 (fr)
WO (1) WO2013108130A2 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USD990642S1 (en) * 2021-10-14 2023-06-27 Yu Xie Water heater

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2713994A (en) * 1950-05-03 1955-07-26 Henry W Angelery Heat exchanger
DE1299393B (de) * 1965-03-24 1969-07-17 Rhein Westfael Elect Werk Ag Warmwassererzeuger, insbesondere Heizwassererzeuger
SE335604B (fr) * 1966-07-16 1971-06-01 Rhein Westfael Elect Werk Ag
GB1296992A (fr) * 1969-03-20 1972-11-22
US4732712A (en) * 1987-05-28 1988-03-22 Leslie Controls, Inc. Steam injection water heater
JP5273378B2 (ja) * 2009-03-25 2013-08-28 三浦工業株式会社 蒸気ボイラ装置およびその運転方法
US20140144626A1 (en) * 2012-11-29 2014-05-29 Conocophillips Company Superheated steam water treatment process

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
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Also Published As

Publication number Publication date
WO2013108130A3 (fr) 2013-10-31
US20140026823A1 (en) 2014-01-30

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