EP2388529A1 - Vorrichtung und Verfahren zur Steuerung von Wärmesystemen, und zwar Strahlersystemen - Google Patents

Vorrichtung und Verfahren zur Steuerung von Wärmesystemen, und zwar Strahlersystemen Download PDF

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Publication number
EP2388529A1
EP2388529A1 EP11003006A EP11003006A EP2388529A1 EP 2388529 A1 EP2388529 A1 EP 2388529A1 EP 11003006 A EP11003006 A EP 11003006A EP 11003006 A EP11003006 A EP 11003006A EP 2388529 A1 EP2388529 A1 EP 2388529A1
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EP
European Patent Office
Prior art keywords
temperature
feed
heat transfer
transfer fluid
manifold
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Withdrawn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
EP11003006A
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English (en)
French (fr)
Inventor
Claudio BORTOLASO
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Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP2388529A1 publication Critical patent/EP2388529A1/de
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F24D3/10—Feed-line arrangements, e.g. providing for heat-accumulator tanks, expansion tanks ; Hydraulic components of a central heating system
    • F24D3/1058—Feed-line arrangements, e.g. providing for heat-accumulator tanks, expansion tanks ; Hydraulic components of a central heating system disposition of pipes and pipe connections
    • F24D3/1066—Distributors for heating liquids
    • F24D3/1075—Built up from modules
    • 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
    • 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
    • F24D19/1024—Arrangement or mounting of control or safety devices for water heating systems for central heating using a valve or valves a multiple way valve
    • F24D19/1033—Arrangement or mounting of control or safety devices for water heating systems for central heating using a valve or valves a multiple way valve motor operated

Definitions

  • the present invention relates to an apparatus and a method for controlling thermal systems, namely radiant heating systems.
  • a warm heat transfer fluid circulates at low temperature, generally between 30°C and 40°C, through the various structural components of the thermal system.
  • the temperature of the heat transfer fluid is adjusted as a function of the external temperature, by means of a mixing valve and of an adapted electronic apparatus for temperature control.
  • a circulating pump feeds the fluid at the same temperature to all the circuits connected to the mixing valve.
  • the circuits are generally constituted by one or more distribution manifolds,
  • the feed temperature Is preset at a fixed value by using a thermostatic valve or an electronic regulator that operates a motorized valve.
  • the feed temperature is the same for all the circuits connected to the system; however, it is possible to adjust the temperature of each room independently by using thermostats which close the corresponding circuit when a desired ambient temperature is reached.
  • the same thermal system can be used to cool the rooms.
  • the feed temperature is the same for all the circuits connected to the system and its value must be such as to prevent condensation on the surfaces.
  • the humidity may be reduced by means of adapted air treatment machines, which can operate purely by dehumidification, with post-heating batteries, or also by cooling.
  • the temperature of the feed fluid of the air treatment machines is normally lower than the temperature of the fluid that flows in the circuits in order to have a better performance.
  • the feed temperature of the heat transfer fluid is the same for all circuits and is set to the value required to meet the least favoured room.
  • the radiating bodies are also sized as a function of this temperature.
  • a room thermostat is generally installed, setting the feed temperature of the heat transfer fluid to a value that is certainly higher than necessary, if the system is operating in heating mode, and lower than necessary, if the system is in the cooling mode.
  • the adjustment is entrusted to local thermostats, which close the corresponding circuit when the desired temperature is reached in the room; however, such temperature is subject to continuous variations.
  • high-temperature heating bodies such as radiators or heated towel rails
  • low-temperature heating bodies such as floor panels, wall panels or ceiling panels
  • two distinct temperature controls one for the low temperature and one for the high temperature.
  • a heating system with one feed temperature entails a further problem: in rooms that require a lower heat emission per unit surface, the pipes must be spaced further apart, however, excessively wide spacing of the pipes may lead to an increase in the time required by the system to reach the steady state.
  • a further problem of the conventional temperature control systems is that they are difficult to calibrate efficiently.
  • a 25°C variation of the outside temperature generally corresponds to a 20°C variation of the feed temperature of the system, which means that a 1°C variation of the outside temperature leads to a variation of the feed temperature of 0.8°C.
  • the thermal emission at the surface that covers the piping proximate to the feed of the heat transfer fluid is higher than the thermal emission at the surface that covers the piping at the end of the user circuit; because of this, the standards prescribe that average thermal emission must be considered as the design thermal emission but that the temperature measured at the point at the highest temperature must be considered as the maximum surface temperature.
  • the feed temperature is 40°C and the return temperature is 30°C
  • a temperature of 35°C is considered for the heat transfer fluid for thermal emission, but the temperature obtained above the piping, in which the heat transfer fluid temperature is 40°C, is considered as the maximum surface temperature.
  • the temperature difference that usually occurs between the return temperature and the feed temperature, should be cancelled out or limited.
  • the aim of the invention is therefore to solve the problems described above, providing an apparatus and a method for controlling thermal systems, namely radiant systems, that allow to maximize the thermal performance, by reducing the difference between the feed temperature and the return temperature.
  • a particular object of the invention is to provide an apparatus and a method that allow to obtain a substantially constant thermal flow along all the piping that forms a user circuit.
  • Another object of the invention is to provide an apparatus and a method that facilitate the adjustment of the room temperature by making it independent from the precision of the feed temperature of the system.
  • a further object of the invention is to provide an apparatus and a method that can be used for regulating the temperature of radiant systems, regardless of whether they are preset for heating or for cooling.
  • a further important object of the invention is to provide an apparatus and a method that allow to reduce the speed of the heat transfer fluid in user circuits, also reducing the electric power of the circulation pump assigned to the operation of the system.
  • an apparatus for controlling thermal systems namely radiant systems, comprising at least one feed manifold and at least one return manifold; in an active condition, said first feed manifold distributes heat transfer fluid to a plurality of user circuits, at feed temperature, and said return manifold collects heat transfer fluid from said user circuits, at return temperature; said apparatus is characterized in that it comprises a temperature equalizing means associated with said first feed manifold; in said active condition, said temperature equalizing means distributes the thermal emission homogeneously along each individual user circuit.
  • an apparatus for controlling thermal systems namely radiant systems, is generally designated by the reference numeral 1.
  • the apparatus 1 comprises a first feed manifold 10 and a return manifold 30, which control and distribute a heat transfer fluid to the user circuits 40 of a thermal system 1000.
  • the user circuits 40 may be constituted by coils of radiating panels, by radiators, by other heating accessories or by any other heating body.
  • the first feed manifold 10 is constituted by a first tubular body 11, which is provided, at one end, with a first inlet 12 for the heat transfer fluid at feed temperature that arrives from a heating and refrigeration source.
  • a first threaded coupling 13, at the opposite end, allows the connection of other substantially equivalent feed manifolds.
  • the flow through the first inlet 12 is adjusted by a first ball valve 14, while the first threaded coupling 13 is closed by a first plug 15, when the first feed manifold 10 is capable of autonomously meeting the requirements of the thermal system 1000.
  • Feed branches 16 are provided on the side wall of the first tubular body 11. In an active condition such feed branches 16 distribute the heat transfer fluid at feed temperature to the user circuits 40.
  • the return manifold 30 includes a third tubular body 31, which is provided at one end with an outlet 32 for the heat transfer fluid at return temperature to be conveyed toward the heating and refrigeration source. At the opposite end, the return manifold 30 also includes a third threaded coupling 33, which allows the connection of other substantially equivalent return manifolds.
  • the third threaded coupling 33 is closed by an overpressure valve 34.
  • Return branches 35 are provided on the side wall of the third tubular body 31. In the active condition, the return branches 35 collect the heat transfer fluid at return temperature that arrives from the user circuits 40.
  • the thermal system 1000 is preset for winter heating and the heating and refrigeration source is preferably constituted by the secondary circuit of a heat exchanger 1001, the primary circuit of which interacts with a boiler, which is not shown in the figures.
  • the heat exchanger 1001 is connected to the first inlet 12 and to the outlet 32 of the apparatus 1 and Interacts with a circulation pump 50 which is preferably arranged at the same outlet 32.
  • the heat exchanger 1001 separates the boiler circuit from the circuit related to the heating bodies and prevents the flow rates between the primary and secondary circuits from affecting each other.
  • the thermal system 1000 also comprises an automatic air vent valve 1002, which is arranged substantially at the first inlet 12.
  • the apparatus 1 comprises a temperature equalizing means 100, which is associated with the first feed manifold 10 in order to uniformly distribute the thermal emission along each user circuit 40,
  • the temperature equalizing means 100 is substantially constituted by a second feed manifold 120, which is associated with the first feed manifold 10, and a series of switching units 130 which interact with the two feed manifolds.
  • the second feed manifold 120 mainly has the function of distributing the heat transfer fluid, at return temperature, to the user circuits 40.
  • the switching units 130 alternate the heat transfer fluid at feed temperature, distributed by the first feed manifold 10, with the heat transfer fluid at return temperature, distributed by the second feed manifold 120, substantially at the feed of each user circuit 40.
  • the second feed manifold 120 comprises a second tubular body 121, which is provided at one end with a second inlet 122 for the heat transfer fluid at return temperature that arrives from the user circuits 40.
  • a second ball valve 124 adjusts the flow in the second inlet 122.
  • the second inlet valve 122 is connected to the outlet 32 of the return manifold 30, directly or by means of the interposed circulation pump 50.
  • a second threaded coupling 123 is provided at the free end of the second tubular body 121 and allows to connect other substantially equivalent feed manifolds or to apply a second plug 125.
  • Branches 126 are formed on the side wall of the first tubular body 11 and are connected to the switching units 130.
  • Each switching unit 130 includes a three-way valve 131 which is controlled automatically and is provided with a first inlet 132a.
  • the first inlet 132a is connected to a feed branch 16 of the first feed unit 10.
  • the three-way valve 131 is also provided with a second inlet 132b, which is connected to the corresponding branch 126 of the second feed unit 120, and with an outlet 133.
  • the outlet 133 is connected to a user circuit 40.
  • the three-way valve 131 connects the outlet 133 alternately to the first inlet 132a and to the second inlet 132b.
  • the apparatus 1 also comprises a balancing valve 140, which is arranged at the second inlet 122 in order to adjust the pressure difference between the first feed manifold 10 and the second feed manifold 120, in a fixed or variable manner.
  • the heat transfer fluid at feed temperature arrives from a heating and refrigeration source and gathers in the first feed manifold 10
  • the heat transfer fluid at return temperature arrives from the user circuits 40 and gathers in the second feed manifold 120.
  • one user circuit 40 among the ones connected to the thermal system 1000, in the active condition the outlet 133 of the corresponding three-way valve 131 is connected to the first inlet 132a.
  • the heat transfer fluid at feed temperature flows initially in the user circuit 40.
  • the flow of heat transfer fluid at feed temperature is throttled and the outlet 133 of the three-way valve 131 is connected to the second inlet 132b, causing heat transfer fluid at return temperature to flow in the user circuit 40.
  • the flow of heat transfer fluid at return temperature also is throttled and the outlet 133 of the three-way valve 131 is again connected to the first inlet 132a, repeating the entire cycle.
  • the alternation between heat transfer fluid at feed temperature and heat transfer fluid at return temperature allows the apparatus 1 to utilize the thermal capacity of the piping in which the fluid flows, as explained hereinafter with an example.
  • the duration of the two distribution periods determines the average heating power of the user circuit 40.
  • the outlet 133 of the three-way valve 131 is constantly connected to the second inlet 132b, the user circuit 40 is crossed by heat transfer fluid at return temperature and, accordingly, the heat exchange between the piping of the user circuit 40 and the environment is substantially nil.
  • thermal system 1000 requires different feed temperatures in order to supply not only floor panels, wall panels or ceiling panels but also heating bodies such as radiators and/or heated towel rails, if it operates in heating mode, or air treatment machines, if it is operating in cooling mode.
  • the heat transfer fluid gathers in the return manifold 30 and, propelled by the circulation pump 50, returns to the heating and refrigeration source.
  • the heat transfer fluid at feed temperature that arrives from the heat exchanger 1001 is heat transfer fluid at high-temperature
  • the heat transfer fluid at return temperature that arrives from the user circuits 40, in which heat transfer has occurred is heat transfer fluid at a low-temperature
  • the first distribution period begins and the piping that forms the user circuit 40 increases its temperature as a function of the thermal gradient between the heat transfer fluid and the piping and accumulates heat, which it partly transmits externally.
  • the outlet 133 of the three-way valve 131 is connected to the second inlet 132b and the second distribution period begins, during which part of the heat accumulated in the piping is transferred to the low-temperature heat transfer fluid that flows through the user circuit 40.
  • the heat that at a certain point of the piping reaches the surface of the floor and is transferred to the environment is therefore determined by the difference between the heat transferred by the high-temperature heat transfer fluid and the heat absorbed by the low-temperature heat transfer fluid.
  • the heat transfer fluid at feed temperature that arrives from the heat exchanger 1001 is heat transfer fluid at low-temperature, while the heat transfer fluid at return temperature that arrives from the user circuits 40, in which heat absorption has occurred is heat transfer fluid at high-temperature.
  • the alternation between the heat transfer fluid at feed temperature and the heat transfer fluid at return temperature allows to utilize the thermal capacity of the piping by means of processes that are substantially equivalent to the ones that have already been described.
  • the present invention also relates to a method for controlling thermal systems, namely radiant systems, which can be used advantageously with temperature control systems that are substantially equivalent to the apparatus 1 described earlier,
  • the method according to the invention substantially comprises supplying a user circuit of a thermal system with heat transfer fluid at feed temperature alternated with heat transfer fluid at return temperature.
  • heat transfer fluid at feed temperature is introduced in the user circuit; subsequently, during a second distribution period that immediately follows the first distribution period, heat transfer fluid at return temperature is introduced in the user circuit.
  • the two distribution periods which have adjustable durations, are alternated cyclically.
  • the heat transfer fluid at return temperature is preferably constituted by part of the fluid that arrives from the user circuits.
  • the apparatus and the method for controlling thermal systems namely radiant systems, according to the invention fully achieve the intended aim, allowing a substantially constant heat flow along the entire piping of a user circuit, with a thermal performance that is higher than that of the conventional systems, which operate with a difference In temperature between the feed and the return of approximately 5°C.
  • the apparatus and the method according to the invention facilitate the adjustment of the room temperature because such temperature is no longer linked to the precision of the feed temperature but rather to the number of high-temperature cycles that are activated through the day.
  • the speed of the heat transfer fluid in the circuits must be rather high, in order to have a low thermal gradient, in the apparatus and the method according to the invention the speed of the fluid can be considerably reduced and, accordingly, the electric power of the circulation pump assigned to the operation of the system is also reduced.
  • the adjustment of the frequency and duration of the various distribution periods allows to achieve high stability of the ambient temperature regardless of whether the thermal system is preset for winter heating or for summer cooling.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Steam Or Hot-Water Central Heating Systems (AREA)
  • Cultivation Of Plants (AREA)
EP11003006A 2010-04-16 2011-04-11 Vorrichtung und Verfahren zur Steuerung von Wärmesystemen, und zwar Strahlersystemen Withdrawn EP2388529A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ITVI2010A000106A IT1400008B1 (it) 2010-04-16 2010-04-16 Apparato e metodo per il controllo degli impianti termici, in particolare per gli impianti radianti.

Publications (1)

Publication Number Publication Date
EP2388529A1 true EP2388529A1 (de) 2011-11-23

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Application Number Title Priority Date Filing Date
EP11003006A Withdrawn EP2388529A1 (de) 2010-04-16 2011-04-11 Vorrichtung und Verfahren zur Steuerung von Wärmesystemen, und zwar Strahlersystemen

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EP (1) EP2388529A1 (de)
IT (1) IT1400008B1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103471159A (zh) * 2013-09-09 2013-12-25 陈意军 一种新型水系统供暖供冷节能装置
EP4227583A3 (de) * 2022-02-14 2023-10-18 Purmo Group Plc Verfahren zum kühlen oder heizen von räumen

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5707007A (en) * 1995-11-22 1998-01-13 Fiedrich; Joachim Hydronic heating with continuous circulation supplying multi-temperature heating loops
EP1065447A2 (de) * 1999-06-30 2001-01-03 R.B.M. S.p.A. Verteiler für thermisches System mit Zwangsumlauf
WO2008056162A1 (en) * 2006-11-10 2008-05-15 Microgen Energy Limited A linear free piston stirling machine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5707007A (en) * 1995-11-22 1998-01-13 Fiedrich; Joachim Hydronic heating with continuous circulation supplying multi-temperature heating loops
EP1065447A2 (de) * 1999-06-30 2001-01-03 R.B.M. S.p.A. Verteiler für thermisches System mit Zwangsumlauf
WO2008056162A1 (en) * 2006-11-10 2008-05-15 Microgen Energy Limited A linear free piston stirling machine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103471159A (zh) * 2013-09-09 2013-12-25 陈意军 一种新型水系统供暖供冷节能装置
EP4227583A3 (de) * 2022-02-14 2023-10-18 Purmo Group Plc Verfahren zum kühlen oder heizen von räumen

Also Published As

Publication number Publication date
ITVI20100106A1 (it) 2011-10-17
IT1400008B1 (it) 2013-05-09

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