Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F24—HEATING; RANGES; VENTILATING
  • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
  • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
  • F24F3/001—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems in which the air treatment in the central station takes place by means of a heat-pump or by means of a reversible cycle
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F24—HEATING; RANGES; VENTILATING
  • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
  • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
  • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
  • F24F1/14—Heat exchangers specially adapted for separate outdoor units
  • F24F1/16—Arrangement or mounting thereof
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B13/00—Compression machines, plants or systems, with reversible cycle
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
  • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F24—HEATING; RANGES; VENTILATING
  • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
  • F24F2221/00—Details or features not otherwise provided for
  • F24F2221/08—Installation or apparatus for use in sport halls, e.g. swimming pools, ice rings
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
  • F25B2313/003—Indoor unit with water as a heat sink or heat source
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
  • F25B2700/19—Pressures
  • F25B2700/193—Pressures of the compressor
  • F25B2700/1933—Suction pressures
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
  • F25B2700/21—Temperatures
  • F25B2700/2115—Temperatures of a compressor or the drive means therefor
  • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Definitions

• the present invention relates to a heat pump for the heating and/or cooling of fluids.
• Heat pumps are generally composed of a closed fluid-operated circuit, along which a refrigerant fluid circulates in a thermodynamic cycle and, therefore, following variations in pressure and/or temperature, is transformed from a liquid state to a gaseous state and vice versa.
• These machines comprise first heat exchange means in which the refrigerant fluid flows and which are placed in contact with a first service fluid which, generally, is composed of air, water or other liquid or aeriform fluids.
• the first heat exchange means are composed of an evaporator in which the refrigerant fluid absorbs heat from the first service fluid and evaporates at low pressure.
• a movement element for the first service fluid consisting of a fan which allows suctioning the air from the surrounding environment and conveying it at the first heat exchange means.
• the refrigerant fluid coming from the first heat exchange means is suctioned and compressed by means of compressor means.
• the refrigerant fluid absorbs a certain amount of heat and is overheated.
• the refrigerant fluid which is still in the gaseous state, is conveyed to the second heat exchange means composed of a condenser in which the fluid itself condenses at high pressure passing from the gaseous state to the liquid state.
• the refrigerant fluid transfers heat to a second service fluid, which may be air, water or other liquid or aeriform fluids.
• the machine also comprises an expansion valve in which, coming from the second heat exchange means, the refrigerant fluid undergoes a reduction in pressure and the refrigerant fluid itself passes to a state in which both the liquid phase and the gaseous phase are present.
• the first service fluid is defined as the cold source, from which the refrigerant fluid absorbs heat
• the second service fluid is defined as the hot source, to which the refrigerant fluid transfers heat
• the second service fluid is defined as the cold source, from which the refrigerant fluid absorbs heat
• the first service fluid is defined as the hot source, to which the refrigerant fluid transfers heat.
• a first type of mono-bloc thermal machines in which all the components of the machine are grouped in the same unit located in specific containment premises inside which the piping dedicated to the passage of the continuous flow of water leaving and returning to the swimming pool are also present.
• the heat exchange takes place in the containment premises between the second heat exchange means and the piping arranged near to these.
• This first type of thermal machines of a known type has the main drawback of requiring the presence of channelling means of the first service fluid in the proximity of the thermal machine, inside the containment premises.
• a second type of mono-bloc thermal machines located outside the containment premises, in the proximity of the first service fluid.
• the thermal machine requires special fluid- operated connections with the water in the swimming pool.
• the main drawback of this second type of thermal machines is that of offering less energy efficiency with equal consumption for heating the water in the swimming pool, above all in the winter months in which the air temperature is particularly low and the evaporation operations of the refrigerant fluid are longer and more difficult due to the dispersion of heat due to the length of the fluid- operated connections.
• a third type of thermal machines is known, called “split", which comprise two units connected together by means of at least two tubular elements for the transit of the refrigerant fluid between a first unit, located outside the containment premises, and a second unit, located inside these premises.
• the first unit comprises first heat exchange means for the passage of the refrigerant fluid from the liquid to the gaseous state and the second unit comprises second heat exchange means through which the water contained in the swimming pool is heated.
• the flow of water to be heated coming from the swimming pool is channelled through special tubular elements placed in the proximity of the second heat exchange means to exchange the heat between them and, once this heat exchange has taken place, the flow of water continues and returns to the swimming pool.
• the third type of thermal machines of known type also has some drawbacks.
• the first unit is in fact usually composed of one or more very bulky fans, which stand next to, on one side, the radiator in which the refrigerant fluid circulates and, to guarantee an appropriate heat exchange, the first unit is rather large in size and implies many limits for freedom of installation.
• the distance between the first unit and the second unit requires the presence of tubular elements connecting the two units, the energy dissipation depending on the length of these tubular elements.
• the main aim of the present invention is to provide a heat pump with a small size in order to maximise its efficiency and reduce energy consumption and environmental impacts.
• Another object of the present invention is to provide a heat pump which allows maximising the energy supplied by the first service fluid, protecting the fan and the first heat exchange means from the atmospheric agents in the outside environment.
• Another object of the present invention is to provide a heat pump which allows maximising personal safety by making the air movement means hard to reach by the persons themselves.
• Another object of the present invention is to provide a heat pump which allows to overcome the mentioned drawbacks of the prior art within the ambit of a rational and effective to use solution.
• the above mentioned objects are achieved by the present heat pump for the heating and/or cooling of fluids having the characteristics of claim 1.
• Figure 1 is an axonometric view of the heat pump according to the invention
• Figure 2 shows a diagram of operation of the heat pump according to the invention
• FIG. 3 is a side view of the heat pump according to the invention.
• Figure 4 is an axonometric view of a detail of the heat pump according to the invention.
• reference numeral 1 globally indicates a heat pump for the heating and/or cooling of fluids.
• the heat pump 1 comprises a first unit 2 having:
• a first fluid- operated circuit 3 suitable for the circulation within the same of a first fluid of the refrigerant type
• the heat pump 1 also comprises a second unit 6 having:
• a fourth fluid- operated circuit 8 suitable for the circulation within the same of a third fluid of the liquid type (e.g. water) by means of suitable pumping means 9 which facilitate the transit of the same in the proximity of the second heat exchange means 11 ;
• a third fluid of the liquid type e.g. water
• compressor means 10 suitable for the suction and compression of the first fluid coming from the first heat exchange means 13, 15, 17;
• the first heat exchange means 13, 15, 17 comprise: a first heat exchange member 13, in which the first fluid circulates, substantially plate-shaped and lying on a first plane 12;
• a second heat exchange member 15 in which the first fluid circulates, connected in a fluid- operated manner to the first heat exchange member 13, substantially plate-shaped and lying on a second plane 14 substantially parallel to the first plane 12;
• the expression "substantially plate-shaped” does not mean, exclusively, that the first heat exchange member 13 and the second heat exchange member 15 are plate-shaped in form, but simply that the form of the first heat exchange member 13 and of the second heat exchange member 15 are extended further along two directions of the Cartesian plane parallel to the planes 12, 14, and to a lesser extent along the third direction of the Cartesian plane perpendicular to the planes 12, 14.
• the expression "interposed in a sandwich-like manner” refers to the specific structure of the first heat exchange means 13, 15, 17, in which the first heat exchange member 13 and the second heat exchange member 15, being parallel and spaced apart from each other, define two external layers of a sandwich and the fan 17 is interposed within the space between the first heat exchange member 13 and the second heat exchange member 15.
• the first heat exchange member 13 is of the type of a substantially plate-shaped radiator with a rectangular or quadrangular outline. It cannot however be ruled out that the first heat exchange member 13 be constituted by a tubular element with a coil-type shape which extends along the first plane 12.
• the second heat exchange member 15 is of the type of a substantially plate-shaped radiator with a rectangular or quadrangular outline.
• the second heat exchange member 15 be constituted by a tubular element with a coil-type shape which extends along the second plane 14.
• the three planes 12, 14 and 16 are substantially vertical, while the axis of rotation A is substantially horizontal and extends perpendicularly to them.
• the first heat exchange means 13, 15, 17 comprise an electric motor 18 operatively connected to the fan 17 for the rotation of the fan itself around the axis of rotation A.
• the electric motor 18 is arranged in the space between the second plane 14 and the third plane 16.
• the second fluid is moved in a vortex by the fan itself along the axis of rotation A and passes through the first heat exchange member 13 to reach the second heat exchange member 15.
• the second fluid laps the electric motor 18 and promotes the recovery of the heat due to the relative overheating.
• the first unit 2 comprises a first container body 19 having at least one cover 20. Conveniently, the fan 17 is connected and supported by the cover 20.
• the first container body 19 comprises a plurality of walls associated with each other to define a substantially U-like shape, inside which are accommodated the first heat exchange means 13, 15, 17.
• the fan 17 is supported by the cover 20 by means of appropriate support brackets 21 with a first ending part fixed to the cover itself and a second ending part fixed to a housing body 22 of the fan 17.
• the first unit 2 comprises at least one expansion valve element 23 arranged along the first fluid- operated circuit 3, upstream of the first heat exchange means 13, 15, 17 and adapted to expand the first fluid.
• upstream and downstream are related to the operating cycle of the heat pump 1 for the heating of a fluid having a lower temperature than the temperature of another fluid.
• the expansion valve element 23 is chosen from the group comprising thermostatic expansion valves or electronic expansion valves, but the use of other types of valve cannot be ruled out.
• the expansion valve element 23 has a special throttle adapted to generate friction in the passage of the first fluid circulating through it, and more in particular, this friction promotes the complete transition from the gaseous state to the liquid state of the first fluid which, more in detail, has a substantially nebulised biphasic state.
• the first fluid is injected into the first heat exchange member 13 and the second heat exchange member 15.
• the first unit 2 comprises a bypass valve element 24 arranged in parallel to the expansion valve element 23.
• the bypass valve element 24 is of the type of a check valve adapted to defrost the first heat exchange member 13 and the second heat exchange member 15 through the inlet of a hot gas following the inversion of the refrigerating cycle, which is done with the use of a special 4-way valve 25.
• the 4-way valve 25 allows inverting the normal heating operating cycle of a fluid with respect to a cold source, in a cooling cycle of the fluid itself with respect to a hot source.
• the 4-way valve 25 allows exchanging the physical state of the refrigerant fluid inside the first and second heat exchange member 13, 15 and of the second heat exchange means 11, with respect to the physical state that such refrigerant fluid would have in them during the heating operating cycle.
• This exchange takes place by inverting the operating mode of the first heat exchange means 13, 15, 17 and of the second heat exchange means 11 with respect to the relative operating mode during the heating operating cycle.
• the second unit 6 comprises at least a second container body 26, substantially rectangular, having a plurality of walls, each of which comprising an inner face and an outer face.
• each of the inner faces is covered with a plurality of layers in a sound absorbing material so as to guarantee the noiselessness of the second unit itself.
• the second unit 6 also comprises:
• third heat exchange means 27 suitable for the heat exchange between the fourth fluid- operated circuit 8 and the fifth fluid- operated circuit 28, 29.
• the fourth fluid is of the type of swimming pool water including, e.g., chlorinated water, saline water or seawater.
• the fifth fluid- operated circuit 28, 29 is composed of a first tubular element 28, along which the fourth fluid leaving the swimming pool flows, and of a second tubular element 29, along which the fourth fluid returning to the swimming pool flows.
• the first tubular element 28 and the second tubular element 29 are connected e.g. to filtering means of the swimming pool water.
• the third heat exchange means 27 allow maintaining the fourth fluid separate from the first fluid, as the exchange of heat between these is done by means of the third fluid.
• the third heat exchange means 27 are made from special material suited to resisting the corrosion of all possible types of water contained in the swimming pool.
• the second unit 6 comprises recovery means 30a, 30b of the heat dissipated by the compressor means 10 during the compression of the first fluid.
• recovery means 30a, 30b comprise:
• a first recovery element 30a with a coil shape wrapped around the casing of the compressor means 10 to recover the heat dissipated by the compressor means themselves during operation;
• a second recovery element 30b positioned at the fourth fluid- operated circuit 8 and connected to the first recovery element 30a via a pipe in which a heat-conveying fluid flows, transferring the heat from the first recovery element 30b to the second recovery element 30b.
• the second unit 6 comprises a command unit 31 , suitable for the control of the operation of the first unit 2 and of the second unit 6.
• the command unit 31 is contained inside the second unit 6 to prevent exposure to atmospheric agents and to ensure optimal operation.
• the command unit 31 comprises a limiting device for the startup inrush current of the compressor means 10.
• the inrush current limiting device is substantially a soft-starter system which electronically controls the ramp of the inrush current, in order to ensure the optimal operation of the compressor means 10.
• the heat pump 1 comprises a first pressure transducer 32, positioned along the third fluid- operated circuit 7 upstream of the compressor means 10 and adapted to detect the pressure level of the first fluid leaving the first heat exchange means 13, 15, 17.
• the second pressure transducer 33 is adapted to detect the pressure level of the first fluid following the relative compression exerted by the compressor means 10.
• Both pressure transducers 32 and 33 are operatively connected to the command unit 31, which stops the heat pump 1 in case of abnormal pressure being detected, and can be used for the continuous adjustment of any electronic expansion valve.
• the heat pump 1 In addition to the pressure levels of the first fluid, the heat pump 1 also controls the temperature of the first, second and fourth fluid.
• the first unit 2 comprises:
• a first temperature sensor 34 of the first fluid arranged along the first fluid- operated circuit 3 between the first heat exchange means 13, 15, 17 and the expansion valve element 23;
• a second temperature sensor 35 of the second fluid arranged in the proximity of the fan 17.
• the temperature sensors 34, 35, 36 and 37 are operationally connected to the command unit 31 to process the acquired signals.
• the command unit 31 manages the operation of the heat pump 1 via a suitable software implemented to perform the many automatic functions.
• the difference in temperature between the first fluid and the second fluid leads to the formation of rime at the first heat exchange member 13 and at the second heat exchange member 15 which causes a progressive obstruction of the passage of the second fluid.
• the first fluid circulates in the first fluid- operated circuit 3 positioned at the first heat exchange means 13, 15, 17 and, more specifically, in the first heat exchange member 13 and in the second heat exchange member 15.
• the second fluid is moved in a vortex by this along the axis of rotation A and passes through the first heat exchange member 13 to reach the second heat exchange member 15.
• the second fluid lapping the electric motor 18, promotes the recovery of the heat due to the overheating of the electric motor itself in order to promote the transformation from liquid to gaseous state of the first fluid.
• the first fluid After the first fluid has passed from the liquid state to the gaseous state, the first fluid transfers from the first fluid- operated circuit 3 to the third fluid- operated circuit 7 and is suctioned by means of the compressor means 10 which send it to the second heat exchange means 11.
• the first fluid in gaseous state, transfers its own heat to the fourth intermediate fluid- operated circuit 8 in which water circulates, which is pumped in it by means of the pumping means 9 and, when the heat has been exchanged between the first fluid and the third fluid, the first fluid is transformed from gaseous to liquid state.
• the fourth fluid- operated circuit 8 is in turn connected to the third heat exchange means 27 to transfer the heat acquired from the third fluid, circulating in the fourth fluid- operated circuit 8, to the flow of the fourth fluid leaving the swimming pool and circulating in the fifth fluid- operated circuit 28, 29.
• the fourth fluid After the heat has been exchanged between the fourth and the fifth fluid- operated circuit 8, 28, 29, the fourth fluid returns heated to the swimming pool.
• the first fluid after having passed through the second heat exchange means 11, flows through the expansion valve element 23 which promotes the cooling and therefore the transition of the first fluid itself from the gaseous state to the liquid state which, more specifically, has a substantially nebulised biphasic state.
• the command unit 31 by means of the first temperature sensor 34, the second temperature sensor 35, the third temperature sensor 36 and the fourth temperature sensor 37, switches on the heat pump 1 when the temperature of the fourth fluid is below a minimum set value and switches off the heat pump 1 when the fourth fluid reaches the required temperature.
• the command unit 31 cuts in to block the operation of the heat pump 1 when the temperature of the second fluid is detected and found to be below a given threshold. With the command unit 31 it is possible to set the optimal rotational speed of the fan 17 according to the noise it generates.
• the particularly small size of the first unit leads to a reduction in environmental impact both if the first unit is placed inside a small lightwell, positioned outside or supported by a wall.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Physics & Mathematics (AREA)
• Thermal Sciences (AREA)
• Other Air-Conditioning Systems (AREA)
• Sorption Type Refrigeration Machines (AREA)
• Heat-Pump Type And Storage Water Heaters (AREA)

Priority Applications (2)

Applications Claiming Priority (2)

Publications (1)

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Family Applications (1)

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Citations (4)

Family Cites Families (4)

• 2015
  • 2015-10-26 IT ITUB2015A005349A patent/ITUB20155349A1/it unknown
• 2016
  • 2016-10-24 WO PCT/IB2016/056366 patent/WO2017072643A1/en active Application Filing
  • 2016-10-24 CN CN201680061817.7A patent/CN108139090A/zh active Pending
  • 2016-10-24 EP EP16802136.8A patent/EP3368831B1/en active Active

Patent Citations (4)

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