WO2012099476A1 - Échangeur de chaleur giratoire horizontal - Google Patents

Échangeur de chaleur giratoire horizontal Download PDF

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Publication number
WO2012099476A1
WO2012099476A1 PCT/NZ2011/000003 NZ2011000003W WO2012099476A1 WO 2012099476 A1 WO2012099476 A1 WO 2012099476A1 NZ 2011000003 W NZ2011000003 W NZ 2011000003W WO 2012099476 A1 WO2012099476 A1 WO 2012099476A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
spillage
heat
flow
medium
Prior art date
Application number
PCT/NZ2011/000003
Other languages
English (en)
Inventor
Joseph VAN LIEMPT
Original Assignee
Van Liempt Joseph
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 Van Liempt Joseph filed Critical Van Liempt Joseph
Priority to PCT/NZ2011/000003 priority Critical patent/WO2012099476A1/fr
Publication of WO2012099476A1 publication Critical patent/WO2012099476A1/fr

Links

Classifications

    • E—FIXED CONSTRUCTIONS
    • E03—WATER SUPPLY; SEWERAGE
    • E03C—DOMESTIC PLUMBING INSTALLATIONS FOR FRESH WATER OR WASTE WATER; SINKS
    • E03C1/00—Domestic plumbing installations for fresh water or waste water; Sinks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/04—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being spirally coiled
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • E—FIXED CONSTRUCTIONS
    • E03—WATER SUPPLY; SEWERAGE
    • E03C—DOMESTIC PLUMBING INSTALLATIONS FOR FRESH WATER OR WASTE WATER; SINKS
    • E03C1/00—Domestic plumbing installations for fresh water or waste water; Sinks
    • E03C2001/005—Installations allowing recovery of heat from waste water for warming up fresh water
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0012—Recuperative heat exchangers the heat being recuperated from waste water or from condensates
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/56—Heat recovery units

Definitions

  • the invention relates to waste heat recycling using a horizontal exchanger method for the recovery of heat from waste water discharged from households and commercial businesses, such as from showers, basins, baths, dishwashing machines, kitchen sinks, laundry washing machines, etc.
  • heated waste water is typically disposed down a drain, with a resultant waste of its energy.
  • one heat recovery system is manufactured and sold by Water Cycles Energy Recovery, based in the Canadian province of Saskatchewan.
  • the Water cycles heat-recovery system recovers energy from water flushing down drains in residential and commercial applications. It uses no energy itself, and there are no moving parts.
  • the Water Cycle has a copper coil system and forms part of the wastewater pipe to extracts heat from wastewater. This heat is then conveyed to incoming fresh water before it reaches the water tank, thus pre-heating the supply.
  • Commercial applications are typically multiple shower installations in fitness centres and swimming pools, and dishwashers in commercial kitchens.
  • Ah under-bath model measuring 600 x 300 x 100mm, is stated as recovering 40% of energy.
  • the invention aims to provide a system for the recovering of heat from sanitation run-off systems, especially for short burst use such as hand washing and showering to overcome weaknesses of the known art or at least provide the public with a useful choice.
  • This spec uses a moulded routing system (T), a shallow rigid close wound spiral conduit (C), ' snug fit in a moulded circular outer shell.
  • the shell (HE) wall has a curved shape and is equipped with an internal spout (6) to impart extra flow momentum and uses variable guide means (7) and transposable connections (9-1 1) to manipulate the flows to suit the domestic application range.
  • variable guide means (7) and transposable connections (9-1 1) to manipulate the flows to suit the domestic application range.
  • the developed product referred to in the descriptive spec paragraph No 1 ( ⁇ 1) comprises
  • a single module assembly consisting of:
  • a shell base B housing the conduit C for the heat transfer medium Fig.3
  • ⁇ Number is as claim number (Item Numbers) and Capital letters refer to corresponding markings in the drawings Fig. # indicators are referring to drawing # in appendix Category Number, (Cat. #) refers to Attributes see Page 7
  • the method offers solutions where others have not.
  • the device is shaped and sized to return peak thermal power at 9 litres per minute, halfway the recommended or mandatory capacity range of 5 to 13 litres per minute processing.
  • the cut-away section of the 40mm diameter drainpipe the shell intersects with ⁇ 280mm.
  • the diameter of the processing platform 210mm and the processing volume (Fig.3-HE), of 1.9 litres more or less.
  • the heat exchanger (HE Fig.1 -3), as described in claim 1, is preferably housed in a shallow walled containment designed (See Cat. ]) to intersect a substantially horizontal in-floor section of a drainpipe, which containment assembly includes a shallow walled moulded top T and a shallow walled moulded base B containing a close wound platform C for heat transfer, both joined by sealing flanges and include; the top T having integrated an upstream extension, outwardly projected (Fig.2) socket, connectible to the drainpipe for taking control of run-off angle (Cat.3) and turbulence and ensuring a flow steadying zone prior to receiving the spillage (1 ) and from which the downstream moulded penetration (Cat.4), extends inwardly as an internal re-routing (Cat.5), and spout (Cat.6), system, (See Cat.2 to 6), taking behavioural control of the flow and angled to direct and spout (6) spillage at intensified flow momentum, for delivery to the base
  • a conduit (ii) C (Cat.9-11) to transport the heat transfer medium fabricated in a rigid close-wound coil to assume the snug fit of all of the said main floor (ii) of B, thereby providing a maximum gravitation processing platform, circular for inviting gyration of the spillage and optioned with variable guide means (7) (Cat.7) for regulating a thermal power band without increasing the medium's internal contact area for heat transfer relative to the proportional constraint attribute (iv) (Cat. 1), whereby the tubular conduit C receives the medium cool (9 or 10 or 1 1), while expelling pre-warmed supply (1 1 and 10, or 9) to the cold inlet of a hot water end-use fixture; iv.
  • HE a singular sealed outer shell
  • a heat exchanger as described in ⁇ 1 including any derived method of providing for two or more substantially horizontal and circular pathways for heat transferring exposure by clockwise or anticlockwise gyrated motion inside a drain vessel, wherein waste heat carrying liquids are processed in varying state, viscosity, density and flow momentum using a direct or indirect medium in varying state such as refrigerants, which method defines the space, shape (Cat.l) and routing (Cat.2-6), interpolated or extrapolated as defined from a critical radius to best gyrate that liquid into substantially horizontal and predominantly parallel flows with the medium, for prolonged and, and/or repeated contact for heat transfer, wherein some or all attributes (Cat.1-12) are employed and wherefore suspension means include a gimballed suspension and applications may span from single and zone shared or reticulated sanitation, to storm water, motor cooling or industrial run-off systems.
  • the heat exchanger system design achieves miniaturisation, by having a configuration composed of up to 12 internal and external dependent variable attributes, a formula devised to re-produce competitive returns for wider applications, which attributes are categorised as;
  • Category 1 Prelim inary input from application purpose to determine the parameters for processing spillage and medium conduit capacity
  • the shell preferably has the following spec
  • Receiving spillage via a >300 mm external steadying zone at 3° design run-off and matching the size of the external feeder pipe at 40mm nominal diameter begins routing of the flow using a 64° design radius left Fig.3, (or right if the process is mirrored), curve aside for smooth redirection and 15° design mn-off to intensify momentum and delivers the flow at the acute angle of >0 and ⁇ 10° Fig.2 to the internal wall of the process shell, to the conduit outer surface. (Cat. 2 to 6)
  • the heat exchanger medium conduit C comprises a close wound, dished, rigid fabricated spiral , taking up all of the dished and circular shape of the lower part of the shell, both inviting an unpressurized whirlpool like motion from the turbulent spillage as it spreads and circles onward from the spillage spout control (using Attribute Cat. 2 to 6), over the conduit and, with the additional control of guide means, (using Attribute Cat. 7 & 8), for assisted and quality assured parallel flow, co-inviting with the spout control, marginal upstream cross flow for high velocity spillage, or downstream for lower loads before expulsion via the central spillage exit.
  • Cat. 7 Guide means (7) of a size, in ratio of vertical protrusion to spillage demand flow; i.e. 4mm high for 9 litres per minute, if water, over a ⁇ 210mm rotating pathway, or 6mm high for 6L/min. flow, or 2mm high for 12L/min. flow.
  • the shell also integrates this attribute for manipulation of the spillage flow, and, if water and in the first aspect, by having at 352° (fig.2) from the spout (6) tip, one sector of the curved wall of the outer shell interrupted to outwardly feature an isosceles triangular pocket with a raised platform that prevents undesirable flow stagnation and stratification. (Cat. 8)
  • Cat. 9 Re-feed (9) connection ofjhe medium, as determined by (Cat.1) + low line pressure, Inlet connection or re-feed Fig.3 is an optional connection for the heat transfer medium that enables control to match the medium to spillage velocities for effective heat transfer, increased temperature differential and reduced pressure drop.
  • inlet connection (9) allows for connection to a smaller diameter tube for use in wider range of flow demand.
  • Cat. 10 User input as required to determine the conduit size, and internal contact area, containing 4.22 m coil length to 210mm heat transfer platform or 0.1043 - 0.1056m 2 internal contact area : 0.210m' diameter.
  • the heat exchanger medium conduit C as in the first aspect scenario, having the conduit fabricated using a high velocity, pipe size of 10mm, EN 1057 Type B and small winding radius, for exploiting the highest feasible drag for optimal heat transfer.
  • the smallish tube thus allows a more compact processing platform ' that e.g. fits between existing floor joists. It also allows for a larger contact area proportional to fluid displacement and produces better turbulence for higher heat transfer.
  • Cat. 11 Shell process Fig.3 volume for flow rotations relative to its momentum at 40 : 210 (with Cat.2);
  • the heat exchanger medium conduit C wherein the achievable shortest process cycle of the heat transfer conduit ensuing from Cat. 10, enables further shortening of that heat transfer conduit, reducing cycle time and pressure drop, so that the said outer shell interior meets the volumetric design target of ⁇ 1.9 litres more or less, (Cat. 1 1 )
  • Cat. 12 In-service access, for maintaining the performance peak.
  • the heat exchanger in-service access (Fig. 3), wherein the capping and shaft ( 12) representing the in-service access for inspection, flushing and retrievals, is preferably an optional made to measure shaft, stench free capped and sealed to withstand stresses to ⁇ 85kPa, which shaft is connectible from the top of the shell to an access facility above, to any other practical level. (Cat. 11)
  • the heat exchanger medium conduit body with which optimum transference is enabled, is externally co-promoted by; '
  • the waste water heat recovery system when factoring-in for purpose design may encompass as many as 5 flow rate categories within NZS4305 at 5 group levels of supply line pressures in 4 different service configurations.
  • Installation of the waste water heat recovery system essentially involves interrupting services and. inserting the unit(s) into the fixture's waste pipe and the water supply connected to feed either the hot water source facility or fixture mixer, or both. It may be placed anywhere from 300mm or more, horizontally down line from the waste trap. It is to be carefully levelled, secured and maintenance access provided. Coil connections must be of the flexible braided type to absorb water line hammer and follow the client's purpose designed configuration. On commissioning, a visual inspection guides a levelling fine tuning operation in which the waste flow should cover >95% of the spiral at 5L/m. A floor inspection hatch access is recommended. If used with a strainer for larger particles, maintenance frequency will not be different from that of a strainer as explained in a user guide.
  • Figure 1 shows the preferred whirlpool motion, a simplified representation of the principle motion produced by the waste water heat recovery system in accordance with the embodiment of the invention.
  • 1 is the spillage, 6 spout, 15 drain, between 10 and 11 is the medium conduit C, which forms the processing platform.
  • Figure 2 shows a perspective of the exchanger HE as prototype IV Mark 5 for simulated tests on domestic showering. (Refer 'Substantiation')
  • Top T It depicts the, Top T, coil C and Base B.
  • the base shows the sealed flange arrangement.
  • FIG. 3 shows a vertical, cross sectional view of the exchanger HE, shown in accordance to a preferred embodiment of the invention.
  • the spout is 6, the close wound conduit C, spillage processing platform C and guide means is 7.
  • the task set was to find the 'fix' plotted between heat transference and resistance to transfer for demand flow rates in a practical application.
  • Table 2.1 shown above lists variations for showering solutions with relevant parameters and performance data collated from simulated tests and shows 10 extracted test result from Table 1 (Not included) for thermal power work out.
  • Table 2.2 Shows three graphs extracted from 2.1 . Test protocol, conditions and meaning are below. Definitions
  • Savings mean: Saving of energy to be replenished to perform the same task.
  • A Area for heat transfer, here given as inner contact area in m 2
  • T T Temperature differential of spillage and medium in °C
  • the peak performance range is selected to match NZS4305 domestic flow rates intentions of 6 to 12L/m. for shower use.
  • the mean actual rate, reported in BRANZ HEEP 2010 appears 10.5 L/min. At 12L/min., savings are at 37%.
  • a performance value is used for easier comparison before and after. I.e. the U value - 81-87% of the copper HT Coefficient in physics. The value accounts for the inner contact area only. Therefore, the comparison is externally biased, as the full effect of tests involving the outer transfer area with the guides was unavailable at the time of print. This awaits Mark 6.
  • Projection is 4% by outer HT contact area.
  • ⁇ 16 A derivative heat exchanger system direct or indirect application method, preferably as specified in claim 1 and 16, being a method for use in wider applications, is included for best mode R&D. Benchmarking these modes seem harder as densities vary.
  • ⁇ 13 A heat exchanger system design as described above, having the HT conduit fabricated in single or double wall, using a high velocity, code compliant, lowest mass and small winding radius pipe or channel composite, for exploiting the highest contextually feasible drag for heat transfer. (Cat. 10)
  • the design brief has centred on the size of application restrictions to encourage engagement in reducing wastage.
  • One of the embodiments of the invention includes the Heat Exchanger is applied with Domestic Hot Water as depicted in Fig. 1 & 3 and is described below;
  • a tandem arrangement prevents the relatively steep curve fall implied above, and produces a 60 : 42 or 143% best return.
  • the exchanger is housed in an outer shell, preferably having a design volume of 1.9 litres more or less, with capacity for 5 to 13 litres per minute spillage processing in critical proportion to processing platform
  • Tolerances for guide protrusion are set by field testing outcomes diameter of 210mm and a 30 litres per minute, all inclusive capacity for flushing the fixture and platform, without overflowing the spillage nor trapping air.
  • the exchanger preferably having its peak thermal power at mean usage demand flows at selectively 7, 9 and 10.5 litres per minute over a processing range between 5 and 13 litres per minute if the spillage is water. (Cat. 7)
  • the whirlpool solution uses the waste flow momentum to effect a multi-pass process of heat transfer for both the waste and the medium flows in a horizontal plane.
  • the compact horizontal process chamber containing the copper spiral exchanger, features the medium spiralled with, not around, the path of the waste flow.
  • the waste entry pipe At 100- 120mm before touch down of the waste flow, the waste entry pipe, at the plan view angles shown, is to incorporate a standard radius waste bend of 40 x ⁇ 22.5° enabling adjustment from a 3° waste pipe run off to a preset 15° momentum assisted fluid transfer while curving to the left into the process chamber. This to ensure waste flow disturbance is corrected to a stable repetitive pattern.
  • Heat recapture from hand washing, showering, hot water rinsing or steam cleaning are primarily focused on, especially by communities in temperate climate zones, who would stand to gain most.
  • Direct exchangers Simultaneous use and spill hot water fixtures such as shower cubicles, shower uses in bathtubs, laundry tubs, rinsing facilities, flushing fixtures in food processing spaces and milking sheds.
  • Indirect exchangers (Demand unexplored) All other non simultaneous fixtures and appliances that may be connected to secondary Heat Transfer coils, such as in conjunction with heat pumps or indirect solar heat collectors. In general, these devices are applicable to all entities and situations where there is a concern with energy usage, emissions and reduction of demand for potable and non potable water. Direct and indirect systems work with any known type of hot water systems.
  • tandem arrangements may provide extra capacity. Otherwise larger versions are needed ( ⁇ 16).
  • a second module may be installed.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Health & Medical Sciences (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Hydrology & Water Resources (AREA)
  • Public Health (AREA)
  • Water Supply & Treatment (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

La présente invention concerne un appareil compact utilisé pour la distribution à réaction rapide d'une chaleur d'échappement provenant d'un court rinçage par explosion, comme dans des applications domestiques dans lesquelles ledit appareil est monté entre des poutrelles de plancher et est composé d'un système d'acheminement moulé (T) qui amène le déversement accidentel à jaillir sur une spirale de cuivre étroitement enroulée rigide et mince (C), ce qui provoque des turbulences giratoires et des contacts répétés régulés par des guides pour accroître les transferts de chaleur et promouvoir le dépassement de la performance maximale.
PCT/NZ2011/000003 2011-01-21 2011-01-21 Échangeur de chaleur giratoire horizontal WO2012099476A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/NZ2011/000003 WO2012099476A1 (fr) 2011-01-21 2011-01-21 Échangeur de chaleur giratoire horizontal

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/NZ2011/000003 WO2012099476A1 (fr) 2011-01-21 2011-01-21 Échangeur de chaleur giratoire horizontal

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WO2012099476A1 true WO2012099476A1 (fr) 2012-07-26

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2952845A1 (fr) 2014-06-05 2015-12-09 Alfa Laval Corporate AB Ensemble de rinçage
CN105180688A (zh) * 2014-05-31 2015-12-23 吴文龙 浴室废热回收箱
JP7471709B1 (ja) 2023-10-31 2024-04-22 真 冨永 熱交換装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05131999A (ja) * 1991-10-25 1993-05-28 Natl Space Dev Agency Japan<Nasda> 噴霧冷却式除熱器
JP2005536706A (ja) * 2002-06-24 2005-12-02 アブ リサーチ リミテッド 熱交換器
JP2007519884A (ja) * 2004-01-28 2007-07-19 シエル・インターナシヨネイル・リサーチ・マーチヤツピイ・ベー・ウイ 発熱反応用の熱交換器

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05131999A (ja) * 1991-10-25 1993-05-28 Natl Space Dev Agency Japan<Nasda> 噴霧冷却式除熱器
JP2005536706A (ja) * 2002-06-24 2005-12-02 アブ リサーチ リミテッド 熱交換器
JP2007519884A (ja) * 2004-01-28 2007-07-19 シエル・インターナシヨネイル・リサーチ・マーチヤツピイ・ベー・ウイ 発熱反応用の熱交換器

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105180688A (zh) * 2014-05-31 2015-12-23 吴文龙 浴室废热回收箱
EP2952845A1 (fr) 2014-06-05 2015-12-09 Alfa Laval Corporate AB Ensemble de rinçage
WO2015185257A1 (fr) 2014-06-05 2015-12-10 Alfa Laval Corporate Ab Ensemble de chasse
JP2017516973A (ja) * 2014-06-05 2017-06-22 アルファ−ラヴァル・コーポレート・アーベー 洗浄組立体
US9970183B2 (en) 2014-06-05 2018-05-15 Alfa Laval Corporate Ab Flushing assembly
JP7471709B1 (ja) 2023-10-31 2024-04-22 真 冨永 熱交換装置

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