WO2012155258A1 - Commande pour un système de chauffage géothermique - Google Patents

Commande pour un système de chauffage géothermique Download PDF

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Publication number
WO2012155258A1
WO2012155258A1 PCT/CA2012/050096 CA2012050096W WO2012155258A1 WO 2012155258 A1 WO2012155258 A1 WO 2012155258A1 CA 2012050096 W CA2012050096 W CA 2012050096W WO 2012155258 A1 WO2012155258 A1 WO 2012155258A1
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WO
WIPO (PCT)
Prior art keywords
loop
flow
fluid
pumps
loops
Prior art date
Application number
PCT/CA2012/050096
Other languages
English (en)
Inventor
Lorne R. HEISE
Fraser F. NEWTON
David S. LAMB
Original Assignee
Heat-Line Corporation
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 Heat-Line Corporation filed Critical Heat-Line Corporation
Priority to CA2827295A priority Critical patent/CA2827295A1/fr
Publication of WO2012155258A1 publication Critical patent/WO2012155258A1/fr

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Classifications

    • 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
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/0034—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using liquid heat storage material
    • 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
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage
    • 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
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E70/00—Other energy conversion or management systems reducing GHG emissions
    • Y02E70/30—Systems combining energy storage with energy generation of non-fossil origin

Definitions

  • the present invention relates to geothermal energy transfer systems.
  • is well known to use a heat pump to transfer energy between a consumer of energy, such as a building, and a source of energy such as the surrounding environment.
  • the heat pump uses a closed cycle that passes a refrigerant through an expansion phase, that requires the absorption of external energy, and a compression phase, which rejects energy to the building.
  • the rejected heat is transferred in to the heating system of that location and the energy required to effect the expansion of the refrigerant is absorbed from an external source.
  • the location acts as a source and supplies the energy for the expansion of the refrigerant and the heat generated during compression is rejected to the surrounding environment thai acts as a consumer.
  • a preferred external source has a substantially constant temperature and the ground or large body of water are typically used, [t is therefore known to provide a heat exchange loop between the heat pump and such a source so that heat may be absorbed in to the loop to supply energy to the heat pump or may be rejected from the loop to remove energy from the heat pump.
  • the loops are typically an extensive run of pipe containing a saline, glycol or ethyl alcohol based heat exchange lluid.
  • the pipe is buried in a trench between one or two meters below 7 the normal surface, At that depth, the earth is at a substantially constant temperature and provides an energy source to either provide energy to or absorb energy from the heat transfer iluid because of the temperature differential between the heat exchange fluid and the surrounding.
  • the heat transfer loop is placed in the water and heat transfer iluid circulated through the loop.
  • the heat exchange loop is typically closed to isolate the heat transfer fluid from the environment.
  • a flow centre is placed in the heat exchange loop to subdivide the heat exchange loop i n to a heat transfer loop and a heat absorption loop.
  • the flow centre acts as a reservoir for heat transfer fluid, !n a pressurized system, a dedicated reservoi r i s not provided as the system is typically charged with air after fil l ing.
  • the flow center i s usually placed between the loop that passes fluid through the heat pump (the heat transfer loop) and the loop that passes fl uid through the ground or water loop (the heat absorption loop).
  • a pump circulates the heat transfer fl uid through the heat transfer loop and returns it to a manifol d from which the heat absorption loop is supplied.
  • Tt is therefore an object of the present invention to obviate or mitigate the above disadvantages.
  • an energy transfer system includes a first loop to circulate fluid through a heat pump and a second loop to circulate fluid through a geothermal energy source.
  • Each of the loops is connected to a flow center to provi de a reservoir of fluid for circulation.
  • a respective pump is connected in each of said loops to establish respective flow rates of fluid in each of said loops, with balance flow being provided by the flow center.
  • Figure 1 is a schematic representation of an energy transfer system
  • FIG. 1 is a perspecti ve view of a flow center
  • Fi gure 3 is a schematic representation of flo through the flo center of Figure 2;
  • 0015[ Fi gure 4 is a view, similar to Figure 2 of an alternative flow center:
  • FIG. 5 is a schematic representation of flow through the flo center of Figure 4:
  • Figure 6 is a further embodiment of the energy transfer system;
  • Figure 7 i s a side elevati on of a further embodiment of flo centre:
  • Figure S is a section on the line VIII - VIII of Figure 7:
  • FIG. 1 0 is a How chart showing a first control strategy for operation of the heating system of figure 1 ,
  • Figure 1 1 is flow chart showing a second control strategy for operation of the heating system of figure 1 in a heating mode
  • Figure 1 is a flow chart showing the second control strategy for operation of the heating system of figure 1 in a cooling mode.
  • a bui lding 1 0 has a heating and cooling system 12 to distribute heat through the building or to remove heat from the building.
  • the heat distribution system may be an air circulating system, or a water ci rculating system that transfers heat between di fferent areas of the building and a heat source.
  • the heating and cool ing system 1 2 includes a heat exchanger 1 4 that cooperates with a heat exchanger 16 to transfer iieat between a heat pump 1 8 and the bui lding 1 0.
  • the heat pump 1 8 is of conventional construction and includes a heat exchanger 20 connected in a refrigerant loop 1 to the heat exchanger 16 through a throttle valve 22 and a compressor 24. Expansion of a refrigerant through the throttle valve 22 causes heat to be absorbed in to the refrigerant and compression of the refrigerant through the pump 24 causes heat to be rejected .
  • the heat exchangers 1 6 and 20 absorb or reject the heat depending upon the mode of the operation of the refrigerant cycle.
  • a reversing valve 23 reverses the How direction to allow the heat pump 18 to function in a heating mode to supply heat to the bui lding, or a cooling mode in wh ich heat i s extracted from the building 1 0.
  • a thermostat 27 and controller 25 is i ncorporated in to the system 12 to control operation and mai ntain the required temperature in the building 1 0,
  • the heat exchanger 20 cooperates with a further heat exchanger 26 to transfer heat between the refrigerant loop 19 and a heat transfer loop indicated at 28.
  • the heat transfer loop 28 includes a pump 30 that circulates a heat transfer fl uid, typically a saline, glycol or ethyl alcohol based mixture, through a return pipe 32 and a supply pipe 34.
  • 0028 ⁇ The pi pes 32. 34 arc connected in series with a pair of header pipes 36, 38, one of which, 36 acts as a supply and the other. 38 acts as a return.
  • the header pipes 36, 38 that are connected to opposite sides of a heat transfer unit 40 to provide a heat absorption loop 41 .
  • the heat transfer unit 40 may be a loop or multiple loops connected in paral lel, to the header pipes 36. 38.
  • the loop is buried in the ground or under water, or. preferably, is a self contained heat transfer unit of the type more fully described in United States Patent
  • the loops may also include loops to auxiliary heat consumers, such as a poo] or spa, if required and as shown in figure 6, with a suffix "b" for clarity.
  • a pump 42 is connected in the header pipe 36 to circulate fluid through the heat absorption loop 41 defined by the pipes 36,38 and the heat transfer unit 40.
  • a How center 44 is connected in parallel with the pipes 36, 38 and 32. 34 through stub pipes 46.
  • the flow center 44 is seen more fully in Figure 2 and, in its simplest form, comprises a cy l indrical housing 50 sealed at its lower end.
  • a cap 52 with a vent valve 54 is fitted to the housing 50 to provide venting to accommodate expansion and contraction of fluid i n the fluid circulation loops 28, 4 ] ,
  • the stub pi pes 46 are connected on diametrically opposite sides of the housing 50.
  • the vent valve 54 is replaced with an air valve allowing the system to be pressurized.
  • the Cap 52 is instal led as to seal the system.
  • the heat transfer loop 28 and the heat absorption loop 41 are filled with fluid through filling the housing 50.
  • the vent 54 allows for venti ng of air from the system and a cap 52 for adding/replenishing fluid duri ng/after initial installation.
  • the pumps 30 and 42 operate to circulate fluid through the heat exchanger 26 and through the heat exchanger 40.
  • the pump 30 is sized to provide a turbulent flow through the heat transfer loop 28 at a rate that maximizes heal transfer between the heat exchangers 26 and 20.
  • the rate required to attain optimum heat transfer wil l vary in different design conditions but for a supply of fluid at a particular temperature an optimum rate can be determined, from operating characteristics of the heat pump 18.
  • the pump 42 is sized to provide a circulation through the heat absorption loop at a rate that optimizes the transfer of energy between the heat exchanger 40 and the surroundings. Again this will depend upon the particular design conditions but an optimum flow rate can be attained, taking into account the temperature of the heat source, the thermodynamic properties of the fluid and the heat transfer characteristics of the heat transfer unit 40.
  • the heat absorption rate from the surroundings through the heat exchanger 40 may require a different How rate through the heat absorption loop 41 to that in the heat transfer loop, 28.
  • the pumps 30, 42 can then be sized to provide those respective flow rates.
  • each of the pumps 30, 42 arc variable flow rate pumps that can be adjusted to increase or decrease the flo rate to suit particular control strategies.
  • one of the pumps 30, 42 may be a fixed capacity and the other variable to permit adj stment of the respective How rates. If a steady condition is anticipated then both pumps may be of fixed How rating for the anticipated conditions in the respective loop. However, as will be explained more fully below; the ability to adj ust the How rates may be used advantageously in the operation and control of the heating and cooling system 12.
  • the flow center 44 operates as a reservoir to recei e excess fluid from the heat absorption loop 41 and supply a balancing fluid back into that loop through respective ones of the stub pipes 46.
  • the flow rate through the heat absorption loop 41 is greater than that required in the heat transfer loop and so the flow center 44 receives fluid from, and delivers fluid to. the heat absorption loop 41.
  • the Ho required through the heal transfer loop 28 is denoted by Y and the flow rate required in the heat absorption loop 4 ] is X + Y.
  • the flow center 44 thus receives X gallons per minute from the heat absorption loop 41 through one of the stub pipes 46 acting as an inlet and similarly delivers X gallons per minute to that loop 41 from the other stub pipes 56 acting as an outlet to supply the pump 42,
  • a flow rate through the heat absorption loop 41 in the order of 23 gallons per minute is optimum with a flow rate through the heat transfer loop 28 of 16 gallons per minute.
  • Fluid circulation in the heat absorption loop 41 may also enable a selective precooling or preheating of the fluid in the flow center 44.
  • the fluid can be preheated in the flow center 44 from fluid circul tion in the heat absorption loop 41 and when cooling a dwelling, the fluid can be prccooled in the flow center from fluid circulation in the heat absorption loop 41 ,
  • FIG. 4 ⁇ further embodiment of ilow center is shown in Figures 4 and 5 i which like components will be denoted w ith like reference numerals with the suffix a added for clarity.
  • the How center 44a includes a pair of cylindrical housings 50a I 50a? Each of the housings has a cap 52a and vent valve 54a.
  • a balancing tube 60 interconnects the upper end of the housings 50a to allow for fluid to flow between the housing.
  • receives fluid returned from the heat absorption loop 41 a through the pi e 38a and supplies fluid to the heat transfer loop 28a.
  • the housing 50a? receives the return through pipe 38a from the heat transfer loop 28a and supplies fluid through the pipe 34, 36a to the heat absorption loop 41 a.
  • FIG. 7 through 9 A further embodiment of flow centre is shown in Figures 7 through 9 in which like reference numerals will be used for like components w ith a suffix "c" added for clarity.
  • Flow centre 44c can be used interchangeably with the How centres 44. 44a, 44b shown in the previous embodiments.
  • the flow centre 44c has a cylindrical housing 50c which is encompassed in an insulating foam 70 and encased in an outer casing 72.
  • a cap 52c is secured to the housing 50c and has an upstanding square boss 76.
  • a retaining bracket 78 is fitted over the cap and has a square hole 80 that fits around the boss 76.
  • the bracket 78 is 1 secured to the casing 72 by bolts 82 and thereby tamper proofs the cap by preventing
  • the bracket 78 may also be used, alter release of the bolts 82 and
  • a pair of cross lubes 90. 92 extend diametrically through the housing 50c and are
  • Hach of the cross tubes 90, 92 has an array of holes 94 at
  • holes 94 may be provided depending upon the I particular circumstances, The aggregated cross section of the holes 94 is the same as or 2 slightly greater than the cross section of the corresponding tube 90. 92.
  • a sight glass 96 is provided on the exterior of the flow 4 centre 44c to provide an indication of the level of fluid contained within the flow centre 44c. 5 Conveniently, a spectrum indicating different colors of fluid corresponding to the
  • the tube 90 is connected between the return pipe 38c of the heat absorption loop 41 c and the supply pipe 34c of the heat transfer loop 28c so that one end acts as an inlet from0 loop 41 c and the other as an outlet to loop 28.
  • the tube 92 is similarly connected between 1 the return pipe 32c of heat transfer loop 28c and the supply pipe 36c of the heat absorption2 loop 41 c to provide respective inlets and outlets.
  • fluid from the heat absorption loop 41 c is delivered by the pump 42c4 to the tube 90 w here it flow s from the return pipe 38c to the supply pipe 34c.
  • How5 in the heat transfer loop 28c from the pump 30c is delivered to the tube 92 from the return6 pipe 32c to the supply pipe 36c of the heat absorption loop 41 c.
  • the pumps 30c. 42c have a7 differential How rate so that typically the How delivered to (he tube 90 from the absorption8 loop 41 c is greater than the flow rate extracted from the tube 90 by the transfer loop 28c. The9 balance of the How is discharged through the holes 94 in to the reservoir provided by the0 interior of the housing 50c.
  • the flow required from the tube 92 to supp!y the absorption loop 41 c is2 greater than that delivered by the return pipe 32c of the transfer loop 28c and therefore makeup fluid is provided through the holes 94 in the tube 92 from the housing 50c,
  • the holes 94 therefore provide for a cross flow between the heat transfer loop and absorption loop to maintain the desired flow rates as determined by the respective pumps.
  • the effect of the delivery of the fluid in the return pipe 38c to the tube 90 is to supply it directly to the inlet to the pump 30c, effectively supercharging the inlet to pump 30c to a positive pressure, to ensure that it is operating under optimum conditions.
  • the pump 30c is not required to operate at a reduced inlet suction pressure, but at the same time ensures that the required flow rates between the two loops is maintained to provide optimum efficiencies.
  • the controller 25 is used to control operation of the heating system 10 and may be a simple thermostat interacting with the heat pump 18 to switch pumps 30, 42 on or off. However, as explained in greater detail below, the controller 25 may also be used to modulate operation of the pumps 30, 42.
  • the pumps 30, 42 may be fixed flow rate pumps, or one pump may be variable and the other fixed.
  • each of the pumps 30, 42 is a variable flow pump to provide differing flow rates in the respective loops 28, 41 .
  • An example of such a pump and a suitable controller is a Dan oss VLT micro drive - FC51.
  • the controller 25 provides a variable reference frequency to the motor of the pump which adjusts the rotational speed of the motor to match the reference frequency.
  • Variable flow rates may also be provided by using a pair of pumps connected in series and selectively switching one of (he pumps on or off.
  • the controller 25 in a preferred embodiment, is a programmable controller having outputs, namely Y
  • the output (> controls reversing valve 23 to switch between heating mode and cooling mode.
  • is used to provide a reference frequency that sets the pump 30 at an intermediate flow rate, to match the required flow rate through the loop 28 when the compressor 24 has an intermediate load, and to maintain the pump 42 at a corresponding predetermined flow rate in excess of pump 32.
  • the output of each pump 30. 42 is correspondingly increased to match the ilow rates to the full load operating condition of the system.
  • 0051 j The ilow centre 44c of Figure 9 facilitates initial setup of the relative flow rates in the heating and cooling system 12, which, in turn, enhances control of the system 12 after the initial setup.
  • the pump 30c is set to an initial intermediate ilow rate, typically that specified by the manufacturer of the heat pump 18,
  • the flow rate is determined by measuring the pressure drop across the heat exchanger 26c, after applying a correction factor to accommodate for varying temperatures of the fluid in the loop 28c.
  • a first set point i of the reference frequency is established for the required flow rate of pump 30c, With the flow rate in loop 28c established, the flow rate of the pump 42c is adjusted to match that of the pump 30c. This is facilitated in the ilow centre 44c by reducing the level of fluid through the drain port provided on the sight glass, so that the fluid is level with the upper cross tube 90. At this level, the relative flow rates in the loops 28c, 41c, can be observed from the flow through the cross ports 94. When the flows are equal, there is no net flow across the ports 94 and the flow rates are balanced.
  • the pump 42c Upon attaining a balanced Ilow, the pump 42c is adjusted to increase the flow in the loop 41 c to achieve a nominally increased flow rate. It has been found that an increased flow rate of 5% - 10% is satisfactory for typical installations. A first set point zi of the reference frequency is established for the pump 42c.
  • ⁇ ' is established for the increased flow rate required from pump 30c, either empirically or by measuring the pressure drop across the heat exchanger 26c as specified for a lull load, and a corresponding set point z: established for the pump 42c. This may be done by observing net flows in the flo centre 44 or by extrapolation from the previous settings,
  • the outputs of controller 25 are used to adjust the flo rates from the pumps 30c. 42c. in the required ratio, to meet the demands of the system 12,
  • the output O determines the mode, heating or cooling, and upon the thermostat cal l ing for an increase in temperature ⁇ in the healing mode), or a reduction of temperature (in
  • is applied to the compressor 24 and each of the pumps 30, 42.
  • the compressor 24 operates at the intermediate load (e.g. 67%) and the pumps 30. 42 circulate fluid at the rates determ ined by the set points xi . z t respectively.
  • the controller 25 provides outputs Y: to the com pressor 24 and each of the pumps 30c, 42c.
  • the compressor 24 increases to ful l load and the output of pumps 30c, 42c, is increased to set points x 2 . z; respectively.
  • the system 12 operates at these conditions until the required temperature is reached, or a further time limit is reached and the auxiliary heat is switched on by output W.
  • the controller 25 Upon attainment of the required temperature, the controller 25 removes the outputs Y i . Yj and W, and the system returns to an at rest condition, with the compressor and the pumps 30c, 42c switched off.
  • control ler 25 may be utilized to further optimize the operation of the system 1 2.
  • 1 4 can elevate the fluid temperature by 2°C. su fficient to mitigate the surface freezing.
  • the control strategy therefore, operates the pump 42c to over supply the loop 28c 3 during heating mode to permit admixture, whereas in cooling mode the admixture i s
  • the variabil ity of the flow rates may also be used to 6 advantage and coordinated with the operation of the heat pum p 1 8. as al so shown i n the 7 schematics of Figures 1 1 and 1 2.
  • a control signal Y] is sent to the pump 30c to initiate flow in the loop 28c at the rate determined by the set point xi .
  • the control signal ⁇ is applied to the pump 42 to operate it at its maximum flow rate, i.e. at set point zi and the pump 30 is maintained operating at the intermediate speed xi .
  • the increased flow rate is accommodated in the flow centre 41 and is maintained for an initial purge period, typically a period sufficient to provide a complete circulation of fluid in the loop 41 , in the order of 300 seconds.
  • a flow ramp up period of 30 seconds is provided to avoid sudden changes. If preferred, a higher flow rate than the set point Z;> may be used for purging, but it is convenient to use the set point 22.
  • control signal to the pump 42 reverts to Yi and the output of the pump 42 will be ramped down over a period of 30 seconds, to set point Z] _
  • the pump 30 is switched on at set point X ] , as the heating mode is selected, the set point z i provides an over capacity providing admixture with fluid returning from loop 28.
  • control signal Yi is removed.
  • the controller 25 asserts an output Y : to the pump 42 for a shut down period, typically 300 seconds, to maintain circulation in the heat transfer loop 1 . Thereafter, the flow rate is ramped down and the pump 42 switched off.
  • the independent operation of the two pumps 32. 42 may therefore be used to establish optimum flow rales in each loop for steady slate and transient conditions, without impacting on the design conditions for the heat pump 1 8.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

Le système de transfert d'énergie géothermique selon l'invention présente une boucle de transfert thermique associée à une pompe à chaleur et une boucle d'absorption de chaleur pour faire circuler du fluide à travers une source d'énergie telle que le sol ou une nappe d'eau. Les boucles sont reliées par le biais d'un réservoir et chaque boucle présente une pompe de circulation pour faire circuler du fluide à travers les boucles respectives. Les débits des pompes sont choisis de manière à optimiser le transfert d'énergie dans chaque boucle et les différences de débits sont absorbées dans le réservoir.
PCT/CA2012/050096 2011-02-18 2012-02-17 Commande pour un système de chauffage géothermique WO2012155258A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CA2827295A CA2827295A1 (fr) 2011-02-18 2012-02-17 Commande pour un systeme de chauffage geothermique

Applications Claiming Priority (6)

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US201161444580P 2011-02-18 2011-02-18
US61/444,580 2011-02-18
US201161523698P 2011-08-15 2011-08-15
US61/523,698 2011-08-15
US201161535467P 2011-09-16 2011-09-16
US61/535,467 2011-09-16

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