EP0128808A1 - Verfahren zum Ausgleichen einer Zwei-Rohr-Zentralheizungsanlage und Anlage zum Durchführen dieses Verfahrens - Google Patents

Verfahren zum Ausgleichen einer Zwei-Rohr-Zentralheizungsanlage und Anlage zum Durchführen dieses Verfahrens Download PDF

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Publication number
EP0128808A1
EP0128808A1 EP84401100A EP84401100A EP0128808A1 EP 0128808 A1 EP0128808 A1 EP 0128808A1 EP 84401100 A EP84401100 A EP 84401100A EP 84401100 A EP84401100 A EP 84401100A EP 0128808 A1 EP0128808 A1 EP 0128808A1
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EP
European Patent Office
Prior art keywords
radiator
valve
flow
hot water
installation
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.)
Withdrawn
Application number
EP84401100A
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English (en)
French (fr)
Inventor
Marc Gillant
Alain Percebois
Rolland Vallet
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.)
Saunier Duval Eau Chaude Chauffage SDECC SA
Original Assignee
Saunier Duval Eau Chaude Chauffage SDECC SA
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Application filed by Saunier Duval Eau Chaude Chauffage SDECC SA filed Critical Saunier Duval Eau Chaude Chauffage SDECC SA
Publication of EP0128808A1 publication Critical patent/EP0128808A1/de
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
    • F24D19/1009—Arrangement or mounting of control or safety devices for water heating systems for central heating
    • F24D19/1015—Arrangement or mounting of control or safety devices for water heating systems for central heating using a valve or valves
    • F24D19/1021—Arrangement or mounting of control or safety devices for water heating systems for central heating using a valve or valves a by pass valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D3/00—Hot-water central heating systems
    • F24D3/02—Hot-water central heating systems with forced circulation, e.g. by pumps

Definitions

  • the present invention relates to a method of balancing a central heating installation comprising a hot fluid generator and radiators, this installation being of the twin-tube type, that is to say comprising a fluid supply line hot (hot water) between the generator (a boiler) and the radiators, and a return line of cooled fluid between the radiators and the generator.
  • radiators are mounted in parallel between the hot fluid supply pipe leaving the boiler and the return pipe of cooled fluid to the boiler.
  • a hot fluid circulation pump is mounted on the hot fluid supply pipe between the generator (or boiler) and the first supply circuit of a radiator.
  • Each radiator which can also be a convector, and which can be designated by the more general term of heating body, is characterized by a heat emitting power at full flow of hot fluid, which depends in particular on its size and the hot fluid temperature.
  • each heating body mounted in parallel on a circuit one end of which is taken from the hot fluid supply line and the other end is connected to the cooled fluid return line, is controlled by a controlled tap either manually, either using a thermostatic head, or using any other control system, for example electric.
  • the water preferably flows dan 's particular radiator at the expense of one or another heater.
  • Some radiators are never crossed by their nominal hot water flow rate for which they are likely to give their nominal heating power. The temperature they should give is not reached. There is then a lack of comfort.
  • thermostatic valves operate by all or nothing when the ambient temperature of the room varies significantly: according to a phenomenon known as "pumping", the valves open and close alternately, unstable and oscillating instead of keeping a certain stable opening position which would be a function of the temperature prevailing in the room.
  • the present invention relates to a hydraulic and automatic balancing process of a central heating installation of the twin-tube type which solves the aforementioned difficult problem.
  • the method of the invention applied to a two-pipe central heating installation where hot water is supplied to a certain number of heating bodies or radiators fitted with taps and where the cooled water is brought back to the generator or the boiler, is characterized in that the hot water is passed both through each radiator and in parallel with each radiator, in two parallel streams which meet at the inlet of the tap and at the outlet of each radiator, and a flow control is carried out downstream of each radiator and the confluence of the two rivers so as to adjust the sum of the flows of the two rivers combined to a constant value specific to each radiator so that a crossing of each radiator is guaranteed by its nominal flow when the lift of the valve flap of each radiator is nominal.
  • a partially constant pressure drop is maintained between the inlet of the tap and the outlet of each radiator so as to obtain a linear function between the flow rate of each radiator and the lifting of the tap valve. of each radiator.
  • a curved function is established between the flow rate of each radiator and the lifting of the valve flap of each radiator whose curvature with concavity upwards is opposite to that of the curved function with concavity down the heating power of each radiator with respect to the flow rate of each radiator, so as to obtain a practically linear function between the heating power of each radiator and the lifting of the valve flap of each radiator, said linear function being the result of the two aforementioned curved functions of inverse curvatures.
  • the invention also relates to an installation for the implementation of this process, this twin-tube type installation comprising a hot fluid generator (hot water) or boiler, a hot water supply pipe starting from the boiler and comprising a circulation pump, a return line of cooled water to the boiler after passing through a certain number of radiators or heating bodies connected in parallel on the two aforementioned pipes, each radiator being equipped at its inlet with a tap control of the flow of hot water before passing through it, this installation being characterized in that each radiator is doubled by a bypass or bypass pipe constituting a parallel watercourse joining the inlet of the tap and the outlet of each radiator, and in that downstream of the confluence-of the bypass pipe and the outlet of each radiator, but upstream of the connection to the cooled water return pipe of the boiler, there is mounted a water flow regulator set to a constant flow value for each radiator considered, this flow value being fbnction of the characteristics of each radiator and specific to each radiator.
  • a hot fluid generator hot water
  • boiler hot water supply pipe starting from the boiler and comprising
  • the valve controlling the flow rate of supply of the radiator at its inlet is adjusted so as to reduce the flow rate (reduction in the degree of opening of its valve or the lifting of the valve relative to its seat)
  • the flow passing through the bypass circuit increases in proportion to the reduction in that which passes through the radiator, thus compensating for this reduction so as to give a constant total flow imposed by the flow regulator.
  • the water flow rate passing through the radiator increases, the water flow rate passing through the py-pass duct decreases correspondingly.
  • the central heating installation is therefore automatically balanced in this way.
  • the bypass pipe is equipped with a calibrated relief valve so as to open only for a pressure given hot water.
  • This embodiment of the invention is advantageous when one simply wants to modify or improve an existing installation.
  • central heating whose two-way valves are for example valves with head or thermostatic control.
  • the tap which controls the flow of hot water entering the radiator is a three-way tap, the first of which is the upstream route of hot water coming from the boiler, the second is a downstream channel for entering hot water into the radiator and the third channel is a downstream bypass or bypass channel connecting with a bypass or bypass pipe which constitutes the stream parallel to the radiator, the valve seat to the downstream bypass path having a cross section greater than that of the valve seat to the downstream radiator supply path.
  • This second embodiment is interesting when it is desired to modify the equipment at the tap of each radiator.
  • One can for example, but not exclusively, equip each three-way valve with a thermostatic head. But it can also be fitted with an electric or other actuator.
  • This second embodiment which makes it possible to obtain a flow-lift curve function, of inverse curvature of the power / flow curve function of each radiator.
  • the invention makes it possible to obtain an almost linear or linear variation in the thermal power supplied by each radiator as a function of the lift of the valve of its valve.
  • a central heating system of known prior type comprises a boiler supplying hot water at a constant temperature, a hot water supply pipe 2 starting from the boiler 1, a pipe 3 for returning water cooled to the boiler 1 after having circulated through radiators, hence the name of central heating "two-pipe".
  • a circulation pump 4 On the pipe 2 is mounted a circulation pump 4.
  • radiators 5 In parallel between the pipes 2 and 3 are mounted a number of radiators 5 or other heating bodies which could for example be convectors. The number of radiators 5 depends on the number of rooms to be heated and the volume of these rooms. Here, only two radiators and their respective supply circuits are shown, for the purpose of simplification.
  • Each radiator 5 equipped with its adjusting tee (at the outlet) is mounted on a branch with two pipes 6 for entry into the radiator 5 and 7 for the outlet from the radiator 5.
  • the pipe 6 is a branch of the pipe 2 hot water supply and the pipe 7 is connected to the pipe 3 for return of cooled water.
  • the lines 6 and 7 constitute a watercourse crossing the radiator 5.
  • On the line 6 entering the radiator 5 is mounted a valve 8 for adjusting the flow of hot water entering the radiator 5.
  • the valve 8 to two channels of known type with flat valve can be manually controlled or can be controlled or thermostatic head TH shown in broken lines due to the optional nature of said thermostatic control.
  • each radiator 5 thus diffuses an amount of heat which depends on the flow of hot water which the tap 8 passes and which also depends on its own dimensions, that is to say the number of elements capable of being 'traversed by hot water and diffusing heat and which of course depends on the fixed adjustment of each adjusting tee.
  • Each radiator 5 thus has its own calorific power used and its own maximum calorific power at maximum opening of its valve 8. As known, if the valve 8 is closed, the water does not circulate in the branch 6-7. After each radiator 5 or part of the radiators 5 have passed through if other radiators in the installation are closed, the cooled water, since it has given up its heat, returns to the boiler 1 via line 3.
  • This operation can be expressed by curves according to FIGS. 2, 3 and 4 which qualitatively illustrate the operating mode of any radiator 5 forming part of the installation.
  • Fig. 2 illustrates the variation in the heating power of the radiator 5 considered as a function of the flow of hot water Q which passes through it. It can be seen that from a zero flow rate, the heating power increases rapidly but that, from a certain flow rate, a further increase in flow rate hardly increases the heating power any more.
  • the nominal power Pn corresponding to a nominal flow Qn of the radiator 5 is that which corresponds to the nominal opening ln of the valve 8. Overall, the heating power of the radiator 5 is not proportional to the flow.
  • the curve of FIG. 3 illustrates the variation of the flow rate as a function of the "lifting" of the valve flap 8 relative to its seat, that is to say as a function of the opening of the valve 8.
  • the curve of FIG. 3 shows that it is only at the start of opening of the valve 8 that the flow rate increases rapidly and that, from a certain opening of the valve 8, the flow of hot water entering the radiator 5 hardly increases any more .
  • a valve opening 8 or nominal lift In corresponds to a nominal flow Qn of hot water passing through the radiator 5. If the tap is subjected to too low a pressure drop, the nominal lift In is greater than the maximum lift of the valve valve 8, which prevents reaching the nominal flow Qn, therefore the nominal power Pn of the radiator 8.
  • the curve of FIG. 4 is the synthesis of curves 2 and 3: it illustrates the variation in the heating power P of the radiator 5 considered as a function of the opening 1 of its valve 8. Given the above, it will be understood that the heating power P of the radiator 5 increases rapidly at the start of the opening of the valve 8 and that, from a certain opening of the valve 8, the heating power P hardly increases any more if the valve 8 is continued to be opened further, that is to say if the lift 1 increases to the maximum.
  • This flow regulator 9 On the outlet pipe 7, and upstream of the connection of the pipe 7 on the pipe 3 for returning cooled water to the boiler 1, a flow regulator 9 is mounted.
  • This flow regulator 9, of the type known for example by the first addition 74 260 to French patent 1 204 375, comprises a tubular body 10 of axis XX and a moving element of the same axis (Fig. 6).
  • the body 10 is open at its ends on the duct 7 to which it is connected for example by flanges 11.
  • the ring 14 is a screen.
  • the screen ring 14 is mounted downstream of the perforated ring 12 with respect to the direction of flow in the conduit 7.
  • a movable element passing through the internal rings 12 and 14.
  • This element comprises a rod 16 sliding in the central hub 13 which guides it and carrying at one of its ends, on the side of the screen 14, a head 17 in the form of a carrot or warhead of progressively reduced section from upstream to the 'downstream, that is to say from its maximum section of connection with the rod 16.
  • Said circular maximum section has a diameter less than the diameter of the calibrated cylindrical opening 15 of the screen 14 so as to be able to spare with opening 15 an annular passage calibrated for water.
  • the rod 16 carries a base 18 which is for example screwed onto the rod 16 and which serves as a support for a helical spring 19 compressed between the central hub and the base 18.
  • This moving assembly is capable of occupying two extreme positions, one (in solid lines) in which the largest section of the head 17 is at the entrance to the calibrated opening 15 and in which the spring 19 is compressed, the other (in broken lines) in which the apex, that is to say the most tapered part of the head 17 is at the entrance to the calibrated opening 15, and the maximum section of the head 17 in abutment against the central hub 13 of the inner ring 12, the spring 19 then being relaxed.
  • each radiator '5 the flow D defined by each flow regulator 9 is as follows: If this radiator 5 is oversized after thermal improvement of the installation, for example after thermal insulation work of the premises, a part only (P'n) of its heating power is sufficient to ensure comfort. In other words, the useful nominal value Pn is reduced to a nominal value P'n less than Pn. The new heating power P'n corresponds to a nominal flow Q'n lower than the nominal flow Qn which corresponded to the nominal power Pn (Fig. 7).
  • the flow D of the flow regulator 9 is chosen equal to or slightly greater than the flow Q'n.
  • the values D or Q'n are therefore different from each other when the corresponding radiators 5 have different dimensions.
  • each bypass conduit 20 is connected at its origin to a conduit 6 and is connected at its end to a conduit 7.
  • a relief valve 21 coaxial with the conduit 20 along an axis YY.
  • the central heating installation comprises as many branches 6-7, by-pass conduits 20 and relief valves 21 as there are radiators 5.
  • the relief valve '21 comprises a tubular body 22 ensuring the continuity of the by-pass conduit 20 and connecting to it by flanges 23.
  • a ring 24 with calibrated opening forming a seat for a valve. 25 capable of closing said opening.
  • an internal support ring 26 with central opening. Between the support ring 26 and the valve 25 is compressed a calibrated helical spring 27.
  • the support ring 26 is located downstream of the seat ring 24 relative to the direction of flow on the conduit 20, starting from line 6 and ending at line 7.
  • each radiator 5 is actuated by a tap 8 with a thermostatic head.
  • the valve 8 is preferably with a flat seat and valve, this flat shape being capable of providing a linear variation in the flow rate as a function of the lift of the valve relative to the seat, under constant pressure drop.
  • the valve 25 In the working position of the valve 21, the valve 25 is moved away from its seat 24. Hot water passes through the radiator 5 and through the by-pass duct 20.
  • the valve 8 reduces its lift under the action of the thermostatic head so that the flow of hot water in the branch 6-5-7 decreases, while it increases in the bypass duct 20, the sum of these two flows remaining equal to the setpoint D of the flow regulator 9. If this overheating is significant, the flow is canceled through branch 6-5-7 therefore through the radiator 5, and all the water passes through the by-pass duct 20 forcing the opening of the relief valve 21 (the resso rt 27 is compressed).
  • the flow regulator 9 therefore avoids underflows in the branches 6-7 furthest from the circulation pump 4 as a result of overflows in the branches 6-7 which are closest to the pump 4. Thus the installation is balanced.
  • the by-pass conduits 20 corresponding to the closed radiators 5 are traversed by a flow of hot water which is regulated by each flow regulator 9, without disturbing the supply flows of the other radiators 5 which remain in operation.
  • the flow regulator 9 must have a nominal flow D equal to or slightly higher than the nominal flow Q'n of the radiator 5.
  • the valve 21 is also a differential pressure regulator establishing a constant pressure drop across the branch 6-5-7, that is to say between the upstream of the valve 8 and the downstream of the radiator 5.
  • the pressure drop in the radiator 5 is negligible in general in front of that of valve 8, it is subjected to an almost constant pressure drop, which, on a valve 8 with a flat valve, makes it possible to obtain a law of variation of the flow rate Q as a function of the almost linear lift 1 , as shown in Fig. 8.
  • the nominal flow rate of the valve 8 under 1 bar pressure drop or unit flow rate for a given lift is expressed by the following relation in function of the flow D of the flow regulator 9 and of the differential pressure or pressure drop AP obtained by the valve 21:
  • the valve 8 must therefore be chosen as a function of the unit flow D of the regulator 9 and of the pressure drop aP of the valve 21.
  • the role of the relief valve 21 which operates the valve 8 and the radiator 5 at constant pressure drop across the branch 6-7 is to ensure the linearity of the flow function Q - lift 1 as shown in Fig. 8. If one did not realize a constant pressure drop across the terminals of branch 6-7, one would have a flow rate function Q-lift 1 which would be curved therefore non-linear, as in FIG. 3. The resulting thermal law heating power P-lift 1 would therefore also not be linear (see Fig.4). On the contrary, thanks to the linearity obtained by the valve 21 and expressed in FIG. 8, the result of the thermal law of variation of the heating power P as a function of the flow rate Q (Fig. 7) is combined in its part shown in solid lines (see the comments below) with the linear hydraulic law of the Fig. 8 to give as a result the thermal law of the heating power P as a function of lift 1 illustrated in FIG. 9 which is a law if not of perfect linearity, at least of quasi-linearity or of satisfactory or sufficient linearity.
  • FIG. 9 illustrating the law of heating power of each radiator as a function of the lifting of the corresponding tap 8 which shows that one can have a significant modulation of this power by operating the tap 8, that is to say a precise adjustment of the heating power which one wishes to obtain, contrary to what one obtained according to FIG. 4 of the known prior art.
  • the role of the relief valve 21 is therefore to ensure a constant differential pressure between the inlet and the outlet of the branch 6-5-7, that is to say between the ends of the bypass duct 20 , and to ensure a linear law of variation of the flow rate passing through each radiator 5 as a function of the lifting or of the degree of opening of the flat valve of the valve 8 of each radiator 5 (FIG. 8).
  • a new central heating installation comprises, as in the first embodiment, a bypass duct 20 shorting each radiator 5.
  • the installation also includes a flow regulator 9 mounted on the outlet duct 7 of each radiator 5 downstream of the confluence of the bypass duct 20 and the duct 7.
  • the flow regulator 9 is identical to that of FIG. 6.
  • each two-way valve 8 is replaced by a three-way valve 27 to control the intake hot water to each radiator 5 using a mobile assembly.
  • the three ways of tap 27 are connected to conduits 6 and 20.
  • the three-way tap 27 comprises a tubular body 28 of axis ZZ to which three tubes corresponding to three channels are connected, namely two tubes which are radial with respect to the axis ZZ, one upstream 29 (conduit side 6), the other 30 downstream (bypass side 20), and a third 31, in the ZZ axis, also downstream (radiator side 5).
  • the expressions upstream and downstream are used with respect to the direction of flow on the conduit 6 (arrows f).
  • the pipes 29-30 and 31 are connected by flanges respectively to the pipe 6, connecting to the pipe 2 for supplying hot water, to the bypass pipe 20, and, again to the pipe 6 for entry into a radiator 5 since the tap 27 is placed on the path of the conduit 6 interrupted for this purpose.
  • the valve 27 is divided by two internal calibrated partitions 34 and 35 forming two flat seats for two flat valves 36 and 37.
  • the lower partition 34 marking one end of the tubing 31 and communicating with the radiator 5 through a section of duct 6 has a calibrated opening substantially smaller than that of the upper partition 35 which marks one end of the tubular body 28 and which communicates with the bypass duct 20 by the tubing 30.
  • the passage offered by the seat 35 to the bypass duct 20 has a cross section greater than the passage offered by the seat 34 to the corresponding radiator 5.
  • the two valves 36 and 37 form a one-piece stepped body of axis ZZ forming part of a movable assembly of the same axis ZZ inside the tubular body 28.
  • the valve 36 corresponds to the partition 34 on the radiator side and at a diameter substantially smaller than that of the valve 37 which corresponds to the partition 35 on the bypass side 20.
  • the one-piece body with two valves 36 and 37 moves along the axis ZZ between the partitions 34 and 35.
  • it is integral with a rod 38 of axis ZZ which passes through the cylindrical opening of the partition 35 and extends over the entire length of the tubular body 28.
  • An additional partition 32 parallel to the partitions 34 and 35 is traversed with a simple clearance guide by the rod 38.
  • the upper partition 32 marks a separation between the valve 27 proper and a control head 41 which can be manual electric, thermostatic or of another type.
  • This control head 41 not shown is intended to actuate by pushing the upper end of the rod 38.
  • on the rod 38 is fixed, for example by screwing, and locked, for example between two circlips , a support base 39, well above the upper partition 32.
  • a helical spring 40 of axis ZZ consequently bearing on the fixed upper partition 32.
  • valve 27 and of this control head 41 is schematic in FIG. 11, it is understood that the control head 41 which can be seen secured to the tubular body 28 can be attached thereto, for example by screwing.
  • the control head 41 automatically ensures that it is thermostatic or manually, if it is manual, that the moving equipment moves 36-37-38 towards the seat 35 leaving the spring 40 to relax.
  • the valve 37 approaches the seat 35 and the valve 36 moves away from the seat 34.
  • the flow of hot water to the radiator 5 increases and the flow to the by-pass -pass 20 decreases.
  • the sum of these two water flows remains constant thanks to the flow regulator 9.
  • the head 41 In the event of overheating of the room where the radiator 5 is located, the head 41 automatically or manually ensures a thrust of the movable assembly 36-37-38 compressing the spring 40 and moving the shutter 37 away from its seat 35, while bringing the the shutter 36 from its seat 34 without closing it.
  • the flow of hot water supplying the radiator 5 is then reduced in favor of the flow passing through the bypass duct 20.
  • the greater the overheating the more the flow in the bypass duct 20 increases at the rate of the flow passing through the radiator 5, the sum of the two flows through the radiator 5 and through the conduit 20 remaining constant thanks to the flow regulator 9.
  • the head 41 pushes the moving assembly 36-37-38 in the direction of completely closing the seat 34 by the shutter 36.
  • the radiator 5 is thus closed. If one or two radiators 5 are closed throughout the installation, where other radiators 5 still operate, the bypass conduits 20 The corresponding to the closed radiators 5 are traversed by a flow of hot water which is regulated by each flow regulator 9, without disturbing the supply flows of the other radiators 5 which remain in operation.
  • the seat 35 for admitting hot water to the bypass duct 20 has an opening of section substantially greater than that of the seat 34 for admitting hot water to the radiator 5. This is intended and the effect of obtaining that in a range of low liftings of the valve 36 relative to the seat 34, the increases in liftings have for corollary only small increases in the flow of hot water passing through the radiator 5 since it is the flow of hot water passing through the bypass duct 20 which is favored. It is necessary to wait for a large range of lifts of the shutter 36 relative to the seat 34 so that increases in lifts correspond to significant increases in flow rates.
  • Fig. 12 is the characteristic of the function of the heating power of each radiator as a function of the flow of hot water passing through each radiator 5. It is a curved function, with downward concavity. For the nominal flow Qn obtained by means of the flow regulator 9, the nominal heating power Pn is obtained.
  • Fig. 13 is the characteristic of the hot water flow function Q of each radiator 5 with respect to the lifting 1 of the valve 27, that is to say of the valve 36 with respect to the seat 34.
  • Fig. 14 is the characteristic of the heating power function of each radiator 5 relative to the lift 1 of each tap 27.
  • Fig. 14 is the result of FIGS. 12 and 13.
  • the flow law Q as a function of lift 1 illustrated in FIG. 13 is obtained by virtue of the passage section through the seat 34 towards each radiator 5 substantially smaller than the passage section through the seat 35 towards the bypass duct 20. This is the role of these section diameters passing through the seats 34 and 35 to obtain such an operating curve whose curvature with upward concavity is opposite to that of FIG. 12 which represents the law of variation of heating power P as a function of the flow rate Q of each radiator 5.
  • FIG. 14 is a quasi-linear law of the heating power P of each radiator 5 as a function of the lift 1 of the corresponding tap 27.
  • the abscissas are the liftings 1 of zero value up to a nominal liftout 1n of the valve 36 of each three-way valve 27 relative to the seat 34.
  • the ordinates represent the water flows passing through the valve at three-way 27 the flows are expressed in terms of Kv designating a unit flow for a given lifting of the crew 36-37-38 relative to one of the seats 34,35, at constant pressure drop.
  • the intrinsic operating characteristic of a valve channel is generally defined by a flow at constant pressure drop (1 bar), called Kv.
  • Kv constant pressure drop
  • a flat-seat valve system gives a flow rate law Kv proportional to the valve lift up to a value that can reach 0.25 times the diameter of the seat.
  • the flow rate is substantially proportional to the section of the seat, for a comparable valve-seat overlap.
  • a certain number of valve and seat profiles also provide a Kv / linear lift rate law and therefore also meet the need of the invention.
  • the following description is limited to the illustrated example of the flat valve.
  • the ratio of the maximum values of these two Kv is substantially proportional to the sections of their respective seats 34 and 35.
  • the flow through the radiator 5 has a value KvRi proportional to the ordinate da, and the total unit flow KvT has a value KvTi proportional to the ordinate dc.
  • the flow QR from channel 31 to the radiator 5 therefore has a value proportional to the total flow D of the flow regulator 9 in the ratio of the abovementioned ordinate segments da / dc, which is expressed by l 'equation:
  • This QR value is reported at a point a 'in FIG. 13 for the same lift li (point d) of FIG. 13.
  • the role of the flow regulator 9 is to ensure the hydraulic and automatic balancing of the central heating installation. Thanks to this regulator 9, it is guaranteed to obtain from each radiator 5 its nominal power because it has its nominal flow.
  • this heating power is modulated with the best possible precision by virtue of a quasi-linear (Fig. 9) or practically linear (Fig. 14) law of the heating power of each radiator 5 depending on the lift 1 of the valve 8 or 27 of each radiator 5 using two means: the relief valve 21 for existing installations where the valves 8 are kept with two original channels, and the valve 27 three-way (with wider passage section to bypass 20) for new or old installations very redesigned.
  • the TD information from the SD probe (flow temperature signals) is transmitted to an electronic control unit 42 by a connection cable 43.
  • the information TR from each probe SR (return temperature signals) is transmitted to a transmission box 44 which, in turn, transmits it to the counting center 42 by a transmission cable 45.
  • the invention allows better management of energy sources, that is to say devices used to supply hot water in central heating installations (boilers for example).
  • the invention allows an improvement in the efficiency of the hot water generator (of the boiler). Indeed, a nominal power of the boiler makes it possible to obtain the nominal efficiency of the boiler.
  • a nominal power of the boiler makes it possible to obtain the nominal efficiency of the boiler.
  • the invention also has the advantage of allowing the circulation pump 4 to work at a constant flow rate thanks to the flow regulators 9. Thanks to these, the heating bodies (radiators or convectors) are properly irrigated and the problems of heat build-up and noises due to this heat build-up are therefore eliminated, especially in wall-hung boilers.
  • the flat seat 34 of the three-way valve 27 makes it possible to obtain a curved flow / lift law under variable pressure loss at the terminals of the valve (Fig. 13) while retaining a low nominal lift In that can be achieved by the thermostatic heads. 41 existing.
  • a form of valve with a concave bottom can be used, applied by a circular peripheral edge on the flat seat.
  • the first embodiment of the invention (FIGS. 5 to 9) can also be used for new installations, although it is suitable for existing installations.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
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  • Steam Or Hot-Water Central Heating Systems (AREA)
EP84401100A 1983-06-09 1984-05-29 Verfahren zum Ausgleichen einer Zwei-Rohr-Zentralheizungsanlage und Anlage zum Durchführen dieses Verfahrens Withdrawn EP0128808A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8309720A FR2547396B1 (fr) 1983-06-09 1983-06-09 Procede d'equilibrage d'une installation de chauffage central de type bitube et installation pour la mise en oeuvre de ce procede
FR8309720 1983-06-09

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EP0128808A1 true EP0128808A1 (de) 1984-12-19

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EP84401100A Withdrawn EP0128808A1 (de) 1983-06-09 1984-05-29 Verfahren zum Ausgleichen einer Zwei-Rohr-Zentralheizungsanlage und Anlage zum Durchführen dieses Verfahrens

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EP (1) EP0128808A1 (de)
FR (1) FR2547396B1 (de)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2724160A1 (fr) * 1994-09-07 1996-03-08 Comap Installation de distribution d'un fluide circulant en circuit ferme, a regulation, et procede de reglage de cette installation
FR2740544A1 (fr) * 1996-02-07 1997-04-30 Martin Jean Antoine Emetteurs thermiques auto-equilibres
EP0795724A1 (de) * 1996-03-14 1997-09-17 Comap Ausgleichsverfahren eines Netzes für eine nicht-komprimierbare Flüssigkeit
FR2746713A1 (fr) * 1996-03-28 1997-10-03 Valeo Climatisation Dispositif pour regler independamment le chauffage des deux cotes de l'habitacle d'un vehicule
US6035932A (en) * 1995-07-31 2000-03-14 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Process and apparatus for heating a gas delivered to a membrane gas separator
WO2011029971A3 (es) * 2009-09-14 2011-07-14 Xial Domotecnologia, S.L. Unidad hidráulica distribuidora para agua sanitaria y de calefacción en viviendas comunitarias
US8109289B2 (en) 2008-12-16 2012-02-07 Honeywell International Inc. System and method for decentralized balancing of hydronic networks
WO2012013941A3 (en) * 2010-07-30 2013-06-27 Gregory Hall Central heating system
CN107003014A (zh) * 2014-12-03 2017-08-01 格兰富控股联合股份公司 用于平衡供暖系统的方法和系统

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111396986B (zh) * 2020-03-26 2021-04-27 河南理工大学 基于阻抗的集中供热管网静态水力平衡人工调节方法

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR74260E (fr) * 1958-10-08 1960-11-07 Cie De Pont A Mousson Régulateur de débit et de pression
GB2062216A (en) * 1979-10-25 1981-05-20 Bosch Gmbh Robert A central heating system having a circulating heating medium

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR74260E (fr) * 1958-10-08 1960-11-07 Cie De Pont A Mousson Régulateur de débit et de pression
GB2062216A (en) * 1979-10-25 1981-05-20 Bosch Gmbh Robert A central heating system having a circulating heating medium

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
CHAUD-FROID-PLOMBERIE, volume 32, no. 382, mai 1978; F. ROSSIGNOL: "Tour d'horizon sur le comptage individuel", pages 71-77 *

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2724160A1 (fr) * 1994-09-07 1996-03-08 Comap Installation de distribution d'un fluide circulant en circuit ferme, a regulation, et procede de reglage de cette installation
US6035932A (en) * 1995-07-31 2000-03-14 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Process and apparatus for heating a gas delivered to a membrane gas separator
FR2740544A1 (fr) * 1996-02-07 1997-04-30 Martin Jean Antoine Emetteurs thermiques auto-equilibres
EP0795724A1 (de) * 1996-03-14 1997-09-17 Comap Ausgleichsverfahren eines Netzes für eine nicht-komprimierbare Flüssigkeit
FR2746168A1 (fr) * 1996-03-14 1997-09-19 Comap Procede d'equilibrage d'un reseau de distribution de fluide non compressible a deux tubes, a plusieurs branches ou colonnes derivees
FR2746713A1 (fr) * 1996-03-28 1997-10-03 Valeo Climatisation Dispositif pour regler independamment le chauffage des deux cotes de l'habitacle d'un vehicule
US5884697A (en) * 1996-03-28 1999-03-23 Valeo Climatisation Apparatus for independently regulating the heating on the two sides of the cabin of a vehicle
US8109289B2 (en) 2008-12-16 2012-02-07 Honeywell International Inc. System and method for decentralized balancing of hydronic networks
WO2011029971A3 (es) * 2009-09-14 2011-07-14 Xial Domotecnologia, S.L. Unidad hidráulica distribuidora para agua sanitaria y de calefacción en viviendas comunitarias
WO2012013941A3 (en) * 2010-07-30 2013-06-27 Gregory Hall Central heating system
CN107003014A (zh) * 2014-12-03 2017-08-01 格兰富控股联合股份公司 用于平衡供暖系统的方法和系统
CN107003014B (zh) * 2014-12-03 2020-07-24 格兰富控股联合股份公司 用于平衡供暖系统的方法和系统

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FR2547396A1 (fr) 1984-12-14
FR2547396B1 (fr) 1985-07-12

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