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
• • 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
  • F24D11/00—Central heating systems using heat accumulated in storage masses
  • F24D11/002—Central heating systems using heat accumulated in storage masses water heating system

Definitions

• the present invention relates to a hydraulic supply device for installation in a closed circuit.
• the present invention also relates to such an installation.
• the installations targeted by the invention are in particular heating and / or cooling installations in which a heat transfer fluid flows along a closed circuit to pass successively through equipment for producing heat or cold, a use , a pump, a buffer tank, a filter, etc.
• It may be a heating or cooling installation, or an installation which can operate either in heating or in cooling, the thermal source being for example then constituted by a reversible refrigerating machine, that is to say capable to operate either by heating means or by cooling means.
• the object of the present invention is to rationalize installations of the aforementioned kind as regards their components other than the uses.
• the hydraulic supply device for installation using a heat transfer fluid in a closed circuit, this device comprising for the heat transfer fluid the following components: - a tank having a return orifice and a departure orifice,
• an expansion tank is characterized in that it further comprises an enclosure containing at least in part the aforementioned components by joining them together to form a hydraulic block.
• the enclosure is substantially sealed. This avoids the substantial entry of water vapor into the enclosure and therefore the problems of condensation on the outside of the tank wall.
• the enclosure carries on its inner face a thermal insulation lining.
• a thermal insulation lining is much easier to produce than exterior linings on components having a complex shape such as a tank, pump, and pipes connecting them.
• the enclosure being thus insulated internally makes it possible to dispense with thermal insulation on the components enclosed in one enclosure.
• the thermal insulation lining can be made of intrinsically non-waterproof material, such as rock wool.
• a material is inexpensive and easy to apply. Thanks to the tightness of the enclosure, there is no risk of waterlogging.
• the filter is mounted inside the tank in the manner of a permeable partition dividing the interior of the tank into a return chamber connected to the return orifice and a departure chamber. connected to the starting port.
• This arrangement has multiple advantages. It eliminates the need to provide a location and a mounting for the filter in the circuit outside the tank.
• the filter has a large diameter and thus offers a negligible pressure drop.
• a filter of such a size proves capable of stopping the initial impurities then continuing to allow normal operation. without needing to be cleaned. If the return chamber is in the lower position under the flow chamber, the impurities tend to fall to the bottom of the return chamber instead of remaining suspended on the underside of the filter.
• One of the important optional features of the present invention is to mount some of the components through the wall of the enclosure.
• the pump (s) are preferably mounted so that their motor is outside the enclosure.
• the motor is better ventilated and the heat released by the motor is prevented from heating the interior of the enclosure, which is undesirable when the installation has the function of cooling the uses.
• Such a compartment can take the form of a cabinet in which the electrical box is also installed. If the tank return and outlet ports are oriented approximately 90 ° from each other, the path of departure, making a 90 ° turn due to the usual geometry of pumps such as centrifugal, can exit on the same side of the enclosure as that through which enters the return journey. This is favorable for a rational connection with the rest of the installation.
• the heating and / or cooling installation comprising, along a closed circuit of heat transfer fluid:
• a hydraulic supply device - at least one thermal source
• At least one use is characterized in that the supply device conforms to the first aspect.
• FIG. 1 and 2 are two diagrams relating to two variant installations according to the invention
• FIG. 3 is an elevational view of the supply device according to the invention, with vertical section of the enclosure and cutaway of the tank;
• FIG. 4 is a top view of the supply device of Figure 3, with horizontal section of one enclosure;
• FIG. 5 is a view of a detail of Figure 3, on a larger scale
• - Figure 6 is a view similar to Figure 2, but relating to another embodiment
• - Figure 7 is a view similar to Figure 3, but relating to a possible embodiment for the supply device of Figure 6;
• the thermal conditioning installation comprises a device for supplying heat transfer fluid 1, an equipment 2 forming a thermal source, and uses 3. These elements 1, 2, 3 are linked between- them by a pipe 4 going from the source 2 to a return pipe 6 of the supply device 1, a pipe 7 connecting a starting path 8 of the feed device 1 with the uses 3, and a pipe 9 going from the uses 3 at input 11 in the heat source 2.
• the installation therefore forms a closed circuit for the heat transfer fluid going from the supply device 1 to the uses 3 then to the thermal source 2 from which the fluid returns to the supply device 1.
• the uses 3 are mounted in parallel between the conduits 7 and 9 which serve them.
• each use 3 is illustrated in the form of an exchanger 12 with ambient air 13.
• Each use 3 tends to vary the temperature of the heat transfer fluid in the opposite direction to the temperature variation produced by the thermal source 2.
• the heat source 2 is illustrated in the form of a refrigeration machine, one of the thermally active components 16 of which is in heat exchange relation with the closed circuit of heat transfer fluid.
• the starting path 8 of the supply device 1 is connected by a pipe 17 to the inlet 11 of the heat source 2 and the return path 6 of the supply device 1 is connected by a pipe 14 to the output of the uses 3.
• a pipe 19 connects the output 18 of the thermal source 2 with the input of the uses 3.
• the supply device 1 comprises a reservoir 21 of generally cylindrical shape arranged along a vertical axis in the example shown.
• the reservoir 21 has a return port 22 which communicates with the return path 6 and a start port 23 which communicates with the start path 8.
• the tank 21 is part of the closed circuit for the heat transfer fluid.
• the return path 6 and the start path 8 communicate with each other only through the reservoir 21 which in service is filled with heat transfer liquid.
• the reservoir 21 carries an automatic vent valve 24 for the automatic elimination of any gas pockets.
• the reservoir 21 has a thermal accumulator function preventing sudden temperature variations in the heat transfer fluid, when the heat source is started or stopped manually or automatically and when the consumption of the uses 3 varies abruptly.
• the supply device 1 further comprises an expansion vessel 31 comprising a liquid chamber communicating with the interior of the reservoir 21 by a conduit 32.
• the vessel 21 contains a movable wall (not shown) separating the liquid chamber of a gas chamber whose pressure can be adjusted by an access 33.
• the pressure of the liquid in the reservoir 21 is thus adjusted independently of the variations in volume of the liquid enclosed in the closed circuit of the 'installation.
• the starting path 8 comprises pumping means produced in the example shown in the form of two centrifugal pumps 41 mounted in parallel.
• the use of two pumps 41 is intended to avoid the risk of breakdown of the entire installation in the event of the breakdown of one of the pumps.
• Each pump 41 has an axial inlet 42 communicating with a respective starting port 23 of the reservoir 21.
• Each pump 41 also has a radial delivery port 43 connected to a common delivery pipe 44. In a manner not shown, there is between each delivery opening 43 and the delivery pipe discharge 44 a non-return valve preventing a pump 41 in operation from discharging into another pump 41 stopped.
• the discharge conduit 44 is equipped with a valve 51 for adjusting the flow rate for the heat transfer liquid discharged by the pumps 41.
• the reservoir 21 is installed in an enclosure 61 of generally parallelepiped shape supported by a base 62 on which a base 26 of the reservoir rests.
• the enclosure 61 comprises an outer shell 63, for example made of sheet metal.
• a thermally insulating lining 64 which completely covers it along the four side walls, under the upper wall as well as above the frame 62.
• a complement of lining 66 is produced on the inside of the base 26.
• An air gap 67 is provided between the inside of the lining 64 and the entire outside of the tank 21.
• One of the side walls of the enclosure 61 includes an opening 67 for a hatch inspection 68 which is also thermally insulating.
• the enclosure is made substantially sealed so as to avoid as much as possible the entry of atmospheric water vapor and consequently the formation of a large amount of condensation water on the surface of the reservoir 21 and of the other cold parts situated inside the enclosure.
• a filter 81 is installed inside the tank 21 in the manner of a partition permeable to the coolant, dividing the inside of the tank 21 into a return chamber 27 communicating with the return orifice 22 and a flow chamber 28 communicating with the starting orifices 23.
• the filter 81 is for example produced in the form of a grid of generally circular planar shape or preferably curved to resist by a vault effect the pressure difference between the chambers 27 and 28
• the filter 81 is welded by its entire periphery to the inner face of the peripheral wall of the reservoir 21.
• the filter 81 is arranged in a horizontal plane.
• the wall of the reservoir 21 is still crossed by two openings 29 located one just below and the other just above the filter 81. As shown in FIG.
• these openings 29 allow the mounting of heating resistors 82 each in the form of a bar which plunges radially into the interior of the tank 21 and are fixed against the outside face of the wall of the tank 21 by a flange 83 extended outwards by an electrical connection device 84.
• Such resistors are intended for serve as an additional heating source in addition to the thermal source 2 if the latter is insufficient when it is operating as a heat source, or alternatively to replace the thermal source 2 when the latter consists for example of a machine that is not reversible in a heat pump, so that the installation can still operate in heating installation for example during the winter period.
• the orifices 29 are oriented towards the inspection hatch 68.
• an electric heating mat 86 is fixed against the external face of the wall of the tank 21 in the vicinity of the starting orifices 23 because this zone comprising numerous walls separating the heat transfer fluid from the gas space 67 inside the enclosure 63 is more exposed to the risk of freezing.
• the pumps 41, the expansion tank 31, and the valve 51 are installed in leaktight manner in appropriate openings of the enclosure 61, through the same wall 71 of this enclosure at the same time forming the bottom of a compartment 87 configured in a technical cabinet also containing the electrical box 88.
• the power cable 89 (FIG. 4) of the heating mat 86 passes through the wall 71 of the enclosure in leaktight manner to be connected to the electrical box 88.
• the power supply cable of each resistor 82 can connect the connection device 84 with the electrical box 88 via a cable which is, for example, grouped with the cable 89 for crossing the wall 71.
• the assembly is such that the pump bodies 46 of each of the pumps 41 are inside the enclosure 61 while the motors 47 of the pumps 41 are projecting in the compartment 87.
• the delivery path of the pumps 41 from discharge orifices 43 and passing through the body 52 of the valve 51 extends in a plane parallel to the wall 71 traversed by the components 31, 41 and 51, all against the interior lining of this wall 71.
• the member 53 of the valve 51 protrudes into the compartment 87 to be accessible and allow the adjustment of the valve 51 from this compartment.
• the expansion tank 31 is installed so that the cover 33 giving access to the adjustment means is located in the compartment 87 to allow the pressure of the reservoir 21 to be adjusted from the compartment 87.
• the wall 73 is adjacent to the wall 71 through which components 31, 41, 51 are mounted, and opposite the wall 74 fitted with the hatch 68.
• the return duct 6 is a short tube oriented radially with respect to the reservoir 21 and leading directly to the return orifice 22 located just behind the wall 73.
• the starting path 8 forms, seen from above (FIG. 4), a 90 ° bend inside the pump bodies 46.
• the starting orifices 23 are oriented towards the wall 71, substantially 90 ° of the return orifice 22 around the vertical axis of the reservoir 21, so that after the 90 ° turn in the pumps the starting path 8 ends at the same wall 73 as the return path 6, as it has been said.
• the axis of the pumps 41 is horizontal and radial relative to the reservoir 21.
• the inlet conduits 42 of the pumps 41 are very short rectilinear tubes directed radially relative to the axis of the reservoir 21.
• the discharge conduit 44 is also rectilinear. If only one pump 41 was provided, all the conduits provided for the heat transfer fluid in the supply device 1 could be strictly straight. In the example shown, this very advantageous condition could not be completely achieved because of the necessary connection between the outlets of the two pumps 41.
• the wall 71 can, for the mounting of the components 31, 41, 51, have a large window 76 closed by a thermally insulating mask 77 through which the components 31 are mounted,
• the heat transfer liquid When at least one of the pumps 41 is in operation, the heat transfer liquid is sucked in through the return orifice 22, enters the reservoir 21 in the return chamber 27, passes through the filter 81 to be in the departure chamber 28 that it leaves through at least one of the starting orifices 23.
• the impurities stopped by the filter 81 tend to fall spontaneously at the bottom of the tank 21 where they are in no way annoying.
• the temperature inside the enclosure 61 is close to that of the heat transfer fluid, which is generally regulated as it passes in contact with the thermal source 2 (FIGS. 1 and 2). The heat given off by the motors 47 remains outside.
• the heating mat 86 can automatically start to prevent freezing at the intake of the pumps.
• Such a supply device can operate for years without requiring any maintenance inside the enclosure 61. If one wishes to clean the inside of the tank 21, the latter is emptied by a bottom tap not shown , the two resistors 82 are dismantled and a suction cannula is introduced through the corresponding openings 29 to clean the return chamber 27 and the departure chamber 28 respectively, including the two faces of the filter 81. This operation is facilitated by the fact that the openings 29 are opposite the hatch 68.
• the supply device is particularly economical to manufacture, very practical in use, minimizes maintenance as well as the pressure losses undergone by the heat transfer fluid.
• FIG. 6 will only be described for its differences from that of FIG. 1.
• a part 101 of the heat source 2 is an integral part of the hydraulic supply device 1 and is integrated inside the enclosure 61 and in particular inside the volume surrounded by the gasket. thermal insulation 64.
• the part 101 of the heat source 2 which is inside the enclosure 61 comprises the refrigeration compressor 103, a reservoir of refrigerant 106, a refrigerant expansion valve 107 and an apparatus 116 serving as an evaporator for the refrigerant and a cooling exchanger for the coolant.
• the line 17 is now entirely inside the enclosure 61 between the discharge of the pump 41 and the entry into the evaporator-exchanger 116.
• the outlet 118 of the evaporator-exchanger 116 is constituted by a line coming out of the enclosure 61 through the same face of the enclosure 61 as that where the return connection 6 is located inside the tank 21.
• the discharge 108 of the compressor 103 is constituted by a pipe which crosses the wall of the enclosure 61 to go to connect to the inlet of the condenser 104 which constitutes the essential element of the part 102 of the heat source 2 which is outside the enclosure 61.
• a pipe 109 for the outlet of the condenser 104 also passes through the enclosure 61 to go and connect to the refrigerant reservoir 106.
• the region 106 f of the reservoir 106 which is located below the liquid level in this tank is connected by the pressure reducer 107 with the inlet of the evaporator part of the evaporator-exchanger 116.
• the outlet of this evaporator part is connected by a pipe 111 with the compressor inlet 103.
• This embodiment has the advantage that the parts of the refrigerating machine and more generally of the thermal source which also need to be thermally insulated are grouped together inside the insulated enclosure 61.
• the problems of thermal insulation in the installation are greatly simplified, a large part of the technical components of the installation are grouped together in the same enclosure, there is no need for external insulation on elements such as the compressor or evaporator, which makes these elements more accessible for maintenance.
• the compressor although having the thermodynamic point of view to compress the refrigerant to a temperature which can be quite high, still constitutes in practice a cold part of the installation since it is usually kept at low temperature by a cooling system using the steam coming from the evaporator of the refrigeration circuit just before its admission into the compression chamber of the compressor.
• the possible regulating members of the refrigerating machine such as regulating the throttle produced by the regulator 107 for the refrigerating fluid which passes through it.
• FIG. 6 is also distinguished from that of FIG. 3 by the mounting inside the enclosure 61 of a different filter 181, of cylindrical shape having an annular edge 182 surrounding the return orifice 6 and, at the opposite end, an annular edge 183 surrounding a manhole orifice 184 formed in the wall of the reservoir 21, and normally closed by a closure plate.
• a different filter 181 of cylindrical shape having an annular edge 182 surrounding the return orifice 6 and, at the opposite end, an annular edge 183 surrounding a manhole orifice 184 formed in the wall of the reservoir 21, and normally closed by a closure plate.
• the cylindrical shape of the filter 181 has excellent resistance to the burst stress which results from this depression, especially when the filter is dirty.
• the production of a cylindrical filter is inexpensive.
• Manhole 184 conveniently allows the insertion of a heating resistor, or a suction cannula for cleaning, or even the replacement of filter 181.
• the condenser 104 instead of being physically separated from the enclosure 61 is fixed thereon, outside the thermally insulating lining 64.
• the particular embodiment of the refrigerating tank 106 in the form of an elongated bottle with a substantially vertical upper region 106g, intended to contain the gas phase and a lower region 106f intended to contain the liquid phase and which forms an obtuse angle of approximately 100 ° with the region 106g, so as to be almost horizontal.
• the region 106f is integral with supports 121 which are extended upward to also support the evaporator-exchanger 116 and the compressor 103.
• Another support 122 of the compressor 103 rests solely on the tank 106.
• FIG. 6 illustrates that the gaseous region 106g is connected to the discharge 108 of the compressor 103 by a connection pipe 123.
• the heat source 2 is no longer a refrigerating machine but a heat exchange system with the water 131 of a swimming pool 132 having a water treatment device 133.
• a treatment device draws water from the pool 132 and subjects it to cleaning, filtration, etc. treatments. The water is then returned to the swimming pool 132.
• the water passing through the treatment device 133 is diverted inside the enclosure 61 by an inlet duct 134 and then returns to the treatment device 133 by a return pipe 136.
• the pool water passes through a heat exchanger 141, the other path of which is crossed by the discharge 17 of the pump 41 upstream of the orifice 118 for the outlet of the heat transfer fluid from the enclosure 61.
• the heat transfer fluid can go directly to the uses or pass through a refrigerating machine intended to further lower its temperature.
• the heat transfer fluid has two separate circuits.
• a first circuit simply ensures the circulation of the heat transfer fluid from the reservoir 21 by the pump 41 to the uses and return by the inlet orifice 6 in the reservoir 21.
• the other circuit comprises a second pump 148 with a suction 149 in the tank 21, and a discharge 151 in the thermal source 2 which can, as shown, be at least partly located inside the enclosure 61. From the source 2, the heat transfer fluid returns directly to the tank 21 by a pipe 152.
• the device can with minor modifications be installed so that the axis of the reservoir 21 is horizontal.
• the filter 81 is then without drawback placed in a vertical plane.

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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)
• Structures Of Non-Positive Displacement Pumps (AREA)

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• 1998
  • 1998-08-21 FR FR9810638A patent/FR2782552B1/fr not_active Expired - Fee Related
• 1999
  • 1999-08-18 US US09/763,475 patent/US6427474B1/en not_active Expired - Fee Related
  • 1999-08-18 WO PCT/FR1999/001998 patent/WO2000011408A1/fr not_active Application Discontinuation
  • 1999-08-18 EP EP99936743A patent/EP1105685A1/de not_active Withdrawn

Non-Patent Citations (1)

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