EP4365503A1 - A heat pump with a bladeless fan heat exchanger - Google Patents
A heat pump with a bladeless fan heat exchanger Download PDFInfo
- Publication number
- EP4365503A1 EP4365503A1 EP23202106.3A EP23202106A EP4365503A1 EP 4365503 A1 EP4365503 A1 EP 4365503A1 EP 23202106 A EP23202106 A EP 23202106A EP 4365503 A1 EP4365503 A1 EP 4365503A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat
- heat exchanger
- air
- air flow
- heat exchange
- 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.)
- Pending
Links
- 239000012530 fluid Substances 0.000 claims description 56
- 239000003507 refrigerant Substances 0.000 claims description 52
- 230000000694 effects Effects 0.000 claims description 13
- 238000010438 heat treatment Methods 0.000 claims description 12
- 238000011144 upstream manufacturing Methods 0.000 claims description 12
- 238000001816 cooling Methods 0.000 claims description 10
- 230000001681 protective effect Effects 0.000 claims description 7
- 238000004891 communication Methods 0.000 claims description 6
- 239000007792 gaseous phase Substances 0.000 claims description 5
- 238000005192 partition Methods 0.000 claims description 3
- 230000002093 peripheral effect Effects 0.000 claims description 3
- 238000000926 separation method Methods 0.000 claims description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 34
- 239000007788 liquid Substances 0.000 description 5
- 238000007710 freezing Methods 0.000 description 3
- 230000008014 freezing Effects 0.000 description 3
- 238000010257 thawing Methods 0.000 description 3
- 230000000903 blocking effect Effects 0.000 description 2
- 239000012071 phase Substances 0.000 description 2
- 238000007493 shaping process Methods 0.000 description 2
- 208000027418 Wounds and injury Diseases 0.000 description 1
- 238000009825 accumulation Methods 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000006378 damage Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 208000014674 injury Diseases 0.000 description 1
- 239000007791 liquid phase Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 238000004513 sizing Methods 0.000 description 1
- 230000002195 synergetic effect Effects 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
Images
Classifications
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- 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
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/41—Defrosting; Preventing freezing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/60—Mounting; Assembling; Disassembling
- F04D29/601—Mounting; Assembling; Disassembling specially adapted for elastic fluid pumps
- F04D29/602—Mounting in cavities
Definitions
- the invention relates to a heat exchanger, for example in a heat pump, for example for heating and/or cooling air and/or water, for example in a plant for heating and/or cooling rooms and/or water.
- a heat pump comprises a circuit for the circulation of a refrigerant fluid, an evaporator (consisting of a first heat exchanger) placed in the circuit, a compressor placed in the circuit downstream of the evaporator, a condenser (consisting of a second heat exchanger) placed in the circuit downstream of the compressor, and an expansion valve placed in the circuit downstream of the condenser and upstream of the evaporator.
- the indications "downstream” and "upstream” refer to the circulation direction of the refrigerant fluid in at least one operating mode.
- the compressor is operable to suck in the refrigerant fluid in the gaseous phase and at low pressure from the evaporator, compress the refrigerant fluid, and push it into the condenser.
- the compressed refrigerant fluid releases heat and condensation at high pressure.
- the refrigerant fluid passes through the expansion valve which decompresses it, bringing the refrigerant fluid to a depressurized liquid phase with a possibly lower amount of gaseous phase.
- the depressurized liquid refrigerant fluid is conveyed into the evaporator where the refrigerant fluid absorbs heat and evaporates at low pressure, before being sucked in and compressed again by the compressor.
- the refrigerant fluid changes state inside the evaporator, switching from liquid to gaseous by absorbing heat, and inside the condenser, switching from gaseous to liquid by yielding heat.
- the space where the evaporator is located is thus cooled, whereas the space where the condenser is located is heated.
- a (four-way) switching valve which allows inverting the compression and circulation direction of the refrigerant fluid and thus switching the first heat exchanger from evaporator to condenser and the second heat exchanger from condenser to evaporator, allowing both cooling and heating the spaces in which the first and second heat exchangers are located.
- Known heat pumps can be used in a heating mode, e.g., in winter months, taking heat from the external air and bringing heat into a building.
- the refrigerant fluid crosses the expansion valve and becomes a liquid-vapor mixture at low pressure, then enters into the evaporator, placed outside, where it absorbs heat until it becomes vapor at low temperature, which vapor is then sucked in and compressed by the compressor with the consequent temperature increase, and the hot and compressed vapor is pushed from the compressor outlet into the condenser, where it yields heat, e.g., to a water circuit for heating an indoor environment, and changes phase again from gas to liquid releasing the liquefaction heat.
- the liquid refrigerant fluid returns to the expansion valve and the cycle is repeated.
- the same heat pump can be used in a cooling mode, e.g., in the summer months, where the refrigerant fluid evaporates in the internal heat exchanger and condenses in the external heat exchanger.
- the heat exchange conditions between air and refrigerant fluid, in both an outdoor and indoor environment greatly affect both the energy efficiency of the heat pump and the external and internal structural configurations of the heat exchangers and, therefore, of the external and internal units of the heating and/or cooling systems.
- an axial fan for moving an air flow through the air-refrigerant fluid heat exchanger, for example a surface heat exchanger, e.g., finned, which allows a heat exchange between the air flow and the refrigerant fluid through the surfaces that separate the two fluids.
- a surface heat exchanger e.g., finned
- Axial fans in the context of heat exchanger applications, generate an axial air flow component, a radial air flow component, and a tangential air flow component.
- the air flow component useful for the heat exchange generated by an axial fan is only the axial component, since it contributes to the air flow rate value, while the radial and tangential flow components do not contribute to the air flow rate nor to the heat exchange of the air-refrigerant fluid exchanger.
- the magnitude of the radial and tangential components of the air flow depends, as a first approximation, on the rotation speed and geometry of the fan. Only under idealized conditions, which are not actually achievable, the air velocity in the fan suction region is equal to the axial velocity component of the air downstream of the fan.
- heat exchange assembly understood as the set of ducts and heat exchange surfaces crossed by the two or more fluid flows involved in the heat exchange
- the vector of the air flow in the suction phase is not ideally axial, but disturbed by the heat exchange unit itself and by other structural components necessary, for example, for the stable and safe assembly of the fan itself.
- a similar situation also occurs downstream of the fan due to the presence of a protective grille (necessary to protect the fan blades from external influences and to protect users from the risk of injury caused by the rotating blades).
- the protective grille also affects the flow generated by the axial blade fan, making it further uneven and increasing the non-axial components thereof.
- the work done by the fan to generate the non-axial flow components is a source of unnecessary operating costs, as well as undesired noise and vibrations.
- the geometry of the axial fan and the need for a protective grille further are a source of undesirable sizing and aesthetic constraints.
- the fan blades can accumulate a layer of ice and frost resulting in the risk of blocking the rotation of the heat exchanger air fan impeller.
- a heat exchanger in particular for a heat pump, comprises:
- the suggested configuration allows the generation of a driven air flow due to the ejector effect and the Coand effect which is more uniform than the air flows generated by a bladed fan in the heat exchangers of the prior art and which also obviates the presence of rotating blades at the heat exchange unit.
- the air flow useful for heat exchange only consists of the driven air flow (position of the annular outlet slot downstream) or the sum of the driving and driven air flows (position of the annular outlet slot upstream).
- the heat exchanger configuration according to the invention obviates the risk of freezing the fan blades resulting in the risk of operational interruptions due to freezing.
- a heat pump comprises:
- the heat exchanger according to the invention can be implemented in an external unit of the heat pump.
- a heat exchanger 100 in particular for a heat pump 1, comprises:
- the annular outlet slot 108 and the guide surface 112 are formed together in a single tubular closed-loop structure 115 (not necessarily circular) mounted to the support structure 101.
- the guide surface 112 is formed by, or forms, a peripheral edge 116 of an external housing 117 of the heat exchanger 100 delimiting an air outlet opening 118 of the external housing 117.
- the annular outlet slot 108 and/or the tubular closed-loop structure 115 has a circular shape ( figures 1 , 8 ) or oval shape ( figure 2 ) or polygonal shape, e.g., rectangular or square ( figure 4 ), preferably with rounded corners. This allows adapting the sectional shape of the air flow, at least at the heat exchange unit 102, to the shape of the heat exchange unit 102 itself, and adapting the external dimensions of the heat exchange unit 102 to the space conditions of the housing 117 of the heat exchanger 100.
- the conveying channel 106 is configured to expel the driving air flow 110 with a substantially uniform, i.e., constant, flow rate along the annular outlet slot 108. This is particularly advantageous in the case of a circular outlet slot 108.
- the conveying channel 106 is configured to expel the driving air flow 110 with a non-uniform flow rate, i.e., not constant, along the annular outlet slot 108. This allows compensating for potential non-uniformity of the driven air flow 113 in the case of a non-circular shape of the outlet slot 108.
- a local slowdown of the driving air flow 110 for example at corners or regions of the outlet slot 108 with a small radius of curvature (which can be achieved by targeted shaping of the inner section of the conveying channel 106), reduces the local divergence trend of driven air flow 113.
- a local increase in flow rate for example at corners or regions of the outlet slot 108 with a small radius of curvature (which can be achieved by shaping the inner section of the conveying channel 106 in a targeted manner), ensures the presence of a sufficient amount of driven air for the heat exchange even at the margins of the overall dimensions of the heat exchange unit 102.
- annular outlet slot 108 and/or the tubular closed-loop structure 115 extend in a single conveyor plane 119, ( figures 5, 6, 7 , 8 ) substantially orthogonal to the driven flow direction 114.
- the air conveyor 105 can comprise two or more of said annular outlet slots 108 and/or two or more of the tubular closed-loop structures 115 ( figures 3, 4 , 5, 6 ) associated with the same heat exchange unit 102 or with one of a plurality of said heat exchange units 102, respectively.
- This allows optimizing the shape of a "composite" total flow section while using a shape with possibly regular and even curvature, for example a circular or oval shape, of the annular outlet slot 108 and the guide surface 112, advantageous with reference to the uniformity of the driven air flow 113.
- the conveying channel 106 comprises an annular portion (not necessarily circular) 120 forming the annular outlet slot 108, a fan seat 121 accommodating (at least a part of) the driving air fan 109, and a linear portion 122 (curved or straight) connected between the fan seat 121 and the annular portion 120 ( figures 7 , 8 ).
- the conveying channel 106 comprises a multiple (e.g., double) annular portion (not necessarily circular) 120, 120 forming the multiple annular outlet slots 108, 108' (e.g., double), a fan seat 121 accommodating (at least a part of) the driving air fan 109, and a single linear portion 120 (curved or straight) connected between the fan seat 121 and the multiple, e.g. double, annular portions 120, 120' ( figure 6 ).
- the conveying channel 106 comprises a multiple (e.g., double) annular portion (not necessarily circular) 120, 120' forming multiple, e.g., double, annular outlet slots 108, 108', a plurality of, e.g., two, distinct fan seats 121, 121' each accommodating (at least a part of) one of a plurality of (e.g., two) driving air fans 109, 109' and a plurality of, e.g., two, distinct linear portions 120, 120' (curved or straight), each connected between one of the fan seats 121, 121' and one of the multiple annular portions 120, 120'), respectively ( figure 5 ).
- a multiple (e.g., double) annular portion (not necessarily circular) 120, 120' forming multiple, e.g., double, annular outlet slots 108, 108', a plurality of, e.g., two, distinct fan seats 121, 121' each accommodating (at least a part of) one of
- the different configurations of the conveying channel 106 allow optimized use of the spaces available inside the housing 117 of the heat exchanger 100 or of the heat pump 1 to which it is integrated.
- the annular outlet slot 108 is arranged (only) upstream of the heat exchange unit 102, seen in the direction of the driven air flow 113.
- the annular outlet slot 108 is arranged (only) downstream of the heat exchange unit 102, seen in the direction of the driven air flow 113.
- a first outlet slot of the one or more annular outlet slots 108 of the one or more air conveyors 105 is arranged upstream of the heat exchange unit 102, and a second slot of the one or more annular outlet slots 108 of the one or more air conveyors 105 is arranged downstream of the heat exchange unit 102, seen in a driven air flow direction 113. This allows obtaining a very high flow rate.
- the driven air flow 113 is generated due to the ejector effect, shown in figure 20 .
- the driven air flow 113 is generated by the Coand effect in combination with the ejector effect, shown in figure 21 .
- the driven air flow 113 is generated by an amplified Coand effect in combination with the ejector effect, shown in figure 22 .
- the air conveyor 105 comprises a heating device 123, for example an electric resistance, for example arranged upstream of or at the annular outlet slot 108, in order to be able to free the air annular outlet slot 108 and/or the guide surface 112 from deposits of ice or frost.
- a heating device 123 for example an electric resistance, for example arranged upstream of or at the annular outlet slot 108, in order to be able to free the air annular outlet slot 108 and/or the guide surface 112 from deposits of ice or frost.
- the inlet opening 107 can be in communication with an opening formed in the support structure 101 and/or in the outer housing 117.
- the heat exchanger 100 either lacks a protective grille at the driven air flow 113 or forms a protective grille 124 with gaps being wider than a human finger.
- a heat pump 1 comprises:
- the heat pump 1 comprises an external unit 14 intended to be positioned outdoors, an internal unit 15 intended to be positioned inside a building and connected to a user/application 35, for example a heating/cooling system with a primary water circuit 16.
- the first heat exchanger 3 is a heat exchanger 100 according to the invention.
- the second heat exchanger 6 is a heat exchanger 100 according to the invention.
- the external unit 14 comprises (inside a housing which can coincide with the external housing 117 of the heat exchanger 100):
- the internal unit 15 comprises (inside a housing):
- the user/application 35 comprises a part of the primary water circuit 16 and a water vessel 36 and/or a plurality of heaters or radiators 36 for heating and cooling.
- the external unit 14 of the heat pump 1 comprises an external housing, which coincides with the external housing 117 of the heat exchanger 100, and an internal separation partition 10, which separates a heat exchange compartment 11 from a compressor compartment 17, where:
- the entire air conveyor 105 is positioned in the heat exchange compartment 11 ( figures 8 , 13 , 14, 16 ). This allows utilizing spaces, for example in corners, currently unoccupied, in order to generate the air flow.
- the conveying channel 106 extends from the compressor compartment 17 into the heat exchange compartment 11 and the driving air fan 109, 109' is positioned in the compressor compartment 17 ( figures 9 , 11 , 12 , 15, 17 ). This allows utilizing the entire heat exchange compartment 11, even in the extension thereof in the direction of the air flow, for the heat exchange function and utilizing currently unused spaces of the compressor compartment 17 to generate the driving air flow 110.
- the inlet opening 107 of the air conveyor 105 can be in communication with the compressor 5 for cooling the compressor 5.
- the compressor compartment 17 is laterally near the heat exchange compartment 11 ( figures 8 , 11 , 12, 13 ).
- the compressor compartment 17 is positioned below the heat exchange compartment 11 ( figures 14 , 15 ).
- the compressor compartment 17 is positioned above the heat exchange compartment 11 ( figures 16 , 17 ).
- the driven air flow 113 is substantially vertical, preferably upwards ( figures 9 , 11 ), or less preferably downwards.
- the driven air flow 113 is substantially horizontal ( figure 8 ).
- the compressor compartment 17 also accommodates the temperature sensor 20 for the refrigerant fluid on the suction side of the compressor 5, and the temperature sensor 21 for the refrigerant fluid on the delivery side of the compressor 5, the storage vessel 13 for refrigerant fluid arranged on the suction side of the compressor 5, the switching/reversing valve 12, the expansion device 8, and the refrigerant temperature sensor 24 located in the circuit 2 between the expansion device 8 and the second heat exchanger 6.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
A heat exchanger (100) in an external unit of a heat pump (1), comprises a heat exchange unit (102), an air conveyor (105) operable to convey an air flow through an air channel system (104) of the heat exchange unit (102), wherein the air conveyor (105) comprises a conveying channel (106) with an annular outlet slot (108), a driving air fan (109) for sucking a driving air flow (110) into the conveying channel (106) and expelling the driving air flow (110) from the conveying channel (106), through the annular outlet slot 108, in the form of an annular air blade so as to generate an aerodynamic depression which takes in a driven air flow (113) with a higher flow rate than the flow rate of the driving air flow (110), wherein the outlet slot (108) is arranged at the heat exchange unit (102), so that at least the driven air flow (113) crosses the air channel system (104).
Description
- The invention relates to a heat exchanger, for example in a heat pump, for example for heating and/or cooling air and/or water, for example in a plant for heating and/or cooling rooms and/or water.
- A heat pump comprises a circuit for the circulation of a refrigerant fluid, an evaporator (consisting of a first heat exchanger) placed in the circuit, a compressor placed in the circuit downstream of the evaporator, a condenser (consisting of a second heat exchanger) placed in the circuit downstream of the compressor, and an expansion valve placed in the circuit downstream of the condenser and upstream of the evaporator. The indications "downstream" and "upstream" refer to the circulation direction of the refrigerant fluid in at least one operating mode. The compressor is operable to suck in the refrigerant fluid in the gaseous phase and at low pressure from the evaporator, compress the refrigerant fluid, and push it into the condenser. Inside the condenser, the compressed refrigerant fluid releases heat and condensation at high pressure. After the exit from the condenser, the refrigerant fluid passes through the expansion valve which decompresses it, bringing the refrigerant fluid to a depressurized liquid phase with a possibly lower amount of gaseous phase. Still due to the suction effect of the compressor, the depressurized liquid refrigerant fluid is conveyed into the evaporator where the refrigerant fluid absorbs heat and evaporates at low pressure, before being sucked in and compressed again by the compressor.
- The refrigerant fluid changes state inside the evaporator, switching from liquid to gaseous by absorbing heat, and inside the condenser, switching from gaseous to liquid by yielding heat. The space where the evaporator is located is thus cooled, whereas the space where the condenser is located is heated.
- It is further known to connect the compressor in the circuit by the interposition of a (four-way) switching valve which allows inverting the compression and circulation direction of the refrigerant fluid and thus switching the first heat exchanger from evaporator to condenser and the second heat exchanger from condenser to evaporator, allowing both cooling and heating the spaces in which the first and second heat exchangers are located.
- Known heat pumps, described above, can be used in a heating mode, e.g., in winter months, taking heat from the external air and bringing heat into a building.
- In this case, the refrigerant fluid crosses the expansion valve and becomes a liquid-vapor mixture at low pressure, then enters into the evaporator, placed outside, where it absorbs heat until it becomes vapor at low temperature, which vapor is then sucked in and compressed by the compressor with the consequent temperature increase, and the hot and compressed vapor is pushed from the compressor outlet into the condenser, where it yields heat, e.g., to a water circuit for heating an indoor environment, and changes phase again from gas to liquid releasing the liquefaction heat. The liquid refrigerant fluid returns to the expansion valve and the cycle is repeated.
- By inverting the cooling cycle, e.g., through the (four-way) switching valve, the same heat pump can be used in a cooling mode, e.g., in the summer months, where the refrigerant fluid evaporates in the internal heat exchanger and condenses in the external heat exchanger.
- The heat exchange conditions between air and refrigerant fluid, in both an outdoor and indoor environment, greatly affect both the energy efficiency of the heat pump and the external and internal structural configurations of the heat exchangers and, therefore, of the external and internal units of the heating and/or cooling systems.
- In the prior art it is known to provide an axial fan for moving an air flow through the air-refrigerant fluid heat exchanger, for example a surface heat exchanger, e.g., finned, which allows a heat exchange between the air flow and the refrigerant fluid through the surfaces that separate the two fluids.
- Axial fans, in the context of heat exchanger applications, generate an axial air flow component, a radial air flow component, and a tangential air flow component.
- The air flow component useful for the heat exchange generated by an axial fan is only the axial component, since it contributes to the air flow rate value, while the radial and tangential flow components do not contribute to the air flow rate nor to the heat exchange of the air-refrigerant fluid exchanger.
- The magnitude of the radial and tangential components of the air flow depends, as a first approximation, on the rotation speed and geometry of the fan. Only under idealized conditions, which are not actually achievable, the air velocity in the fan suction region is equal to the axial velocity component of the air downstream of the fan.
- Considering a positioning of the fan downstream of the heat exchange unit (heat exchange assembly understood as the set of ducts and heat exchange surfaces crossed by the two or more fluid flows involved in the heat exchange), even the vector of the air flow in the suction phase is not ideally axial, but disturbed by the heat exchange unit itself and by other structural components necessary, for example, for the stable and safe assembly of the fan itself.
- A similar situation also occurs downstream of the fan due to the presence of a protective grille (necessary to protect the fan blades from external influences and to protect users from the risk of injury caused by the rotating blades). The protective grille also affects the flow generated by the axial blade fan, making it further uneven and increasing the non-axial components thereof. The work done by the fan to generate the non-axial flow components (and which do not contribute to the flow rate and heat transfer) is a source of unnecessary operating costs, as well as undesired noise and vibrations.
- The geometry of the axial fan and the need for a protective grille further are a source of undesirable sizing and aesthetic constraints.
- Moreover, in very humid environmental conditions or in the case of accumulation of moisture when defrosting the evaporator heat exchanger of a heat pump during winter operation, the fan blades can accumulate a layer of ice and frost resulting in the risk of blocking the rotation of the heat exchanger air fan impeller.
- Therefore, it is the object of the present invention to provide an improved heat exchanger and heat pump having features such as to overcome at least some of the disadvantages of the prior art.
- Within the scope of the general purpose, it is a particular object of the invention to provide an improved heat exchanger and heat pump having features such as to reduce the structural constraints and safety measures required by rotary blade fans, as well as to reduce the resistance to the air flow through the heat exchange unit.
- It is a further particular object of the invention to provide a heat exchanger and a heat pump having features such as to make the air flow through the heat exchange unit more uniform and, possibly, less noisy.
- It is a further particular object of the invention to provide a heat exchanger and a heat pump having features such as to generate an air flow through the heat exchange unit having small radial and tangential flow components as compared to the prior art.
- It is a further particular object of the invention to provide a heat exchanger and a heat pump having features such as to generate an air flow through the heat exchange unit having an increased flow rate with the same electric power absorbed by the air conveyor.
- It is a further particular object of the invention to provide a heat exchanger and a heat pump having a simplified structure.
- It is an even further object of the invention to overcome the risk of freezing the fan resulting in risk of blocking the rotation of the impeller of the air fan.
- These and other objects are achieved by a heat exchanger, in particular a heat pump, according to
claim 1. The dependent claims relate to advantageous and preferred embodiments. - According to an aspect of the invention, a heat exchanger, in particular for a heat pump, comprises:
- a support structure,
- a heat exchange unit connected to the support structure and having a fluid channel system and an air channel system in heat exchange communication with the fluid channel system,
- an air conveyor connected to the support structure and operable to convey an air flow through the air channel system of the heat exchange unit, where the air conveyor comprises:
- a tubular conveying channel extending from an inlet opening to an annular outlet slot (not necessarily circular),
- a driving air fan placed in the conveying channel and operable to suck in a driving air flow through the inlet opening into the conveying channel and expel the driving air flow from the conveying channel, through the annular outlet slot, in the form of an annular air blade (not necessarily circular) in a driving flow direction,
- optionally, an annular guide surface with a continuous convex curvature, formed downstream along the entire annular outlet slot,
- so as to generate a depression due to the aerodynamic and/or Coand effect, which takes in a driven air flow with a higher flow rate than the driving air flow, in a driven flow direction,
- where the annular outlet slot and, if provided, the annular guide surface are arranged at the heat exchange unit, so that at least the driven air flow crosses the air channel system, where the driving air fan is arranged outside and at a distance from the driven air flow and the heat exchanger has no impellers with blades at the driven air flow.
- The suggested configuration allows the generation of a driven air flow due to the ejector effect and the Coand effect which is more uniform than the air flows generated by a bladed fan in the heat exchangers of the prior art and which also obviates the presence of rotating blades at the heat exchange unit.
- Depending on the position of the annular outlet slot upstream or downstream of the heat exchange unit, the air flow useful for heat exchange only consists of the driven air flow (position of the annular outlet slot downstream) or the sum of the driving and driven air flows (position of the annular outlet slot upstream).
- The absence of the fan with rotating blades at the heat exchange unit, and thus within the air flow directly involved in the heat exchange, reduces the structural constraints of the heat exchanger and the necessary safety measures.
- In particular, it is possible to reduce or completely eliminate the resistance to the flow due to the very narrow safety grilles of the prior art and to the support structure of the fans of the prior art.
- Due to the absence of rotating blades in the generated air flow, the air flow itself has much smaller or almost absent radial and tangential components.
- Due to the greater directional uniformity of the air flow generated and by virtue of the multiplication effect of the flow rate, with the same electrical power absorbed by the conveyor, both the flow rate of air useful for the heat exchange and the energy efficiency of the heat exchanger, in terms of lower electrical energy consumption of the conveyor with the same flow rate of air generated, are increased.
- The absence of an impeller with rotating blades at the heat exchange unit also allows enlarging the heat exchange unit with the same dimensions as the external housing and simplifying the entire structure of the heat exchanger.
- Moreover, the heat exchanger configuration according to the invention obviates the risk of freezing the fan blades resulting in the risk of operational interruptions due to freezing.
- According to a further aspect of the invention, a heat pump comprises:
- a circuit for circulating a refrigerant fluid,
- a first heat exchanger placed in the circuit and forming an evaporator,
- a compressor placed in the circuit downstream of the first heat exchanger,
- a second heat exchanger placed in the circuit downstream of the compressor and forming a condenser,
- an expansion device placed in the circuit downstream of the second heat exchanger,
- an electronic control system controlling the compressor, the expansion device, the first heat exchanger, and the second heat exchanger,
where:- the compressor is operable to suck in the refrigerant fluid in the gaseous phase and at low pressure from the evaporator, compress the refrigerant fluid, and push it into the condenser,
- in the condenser, the compressed refrigerant fluid releases heat and condenses at high pressure,
- after leaving the condenser, the refrigerant fluid passes through the expansion device which depressurizes it,
- the refrigerant fluid depressurized by the expansion device enters into the evaporator where it absorbs heat and evaporates at low pressure, before being sucked in and compressed again by the compressor,
- The advantages described with reference to the heat exchanger also similarly apply to the heat pump. Further synergistic advantages concern greater freedom in designing the structure and dimensioning the external unit of the heat pump, as well as greater freedom in choosing the shape, structure, and aesthetics of the internal and external units of the heat pump.
- With particular advantage, the heat exchanger according to the invention can be implemented in an external unit of the heat pump.
- In order to better understand the invention and appreciate the advantages thereof, some non-limiting embodiments thereof will be described below with reference to the accompanying drawings, in which:
-
figures 1, 2, 3, 4 are perspective views of external units of heat pumps with a heat exchanger according to embodiments of the invention, -
figures 5, 6, 7 are diagrammatic perspective views of an air conveyor of the heat exchanger according to embodiments, -
figure 7A is a diagrammatic sectional view taken along thesection plane 7A-7A infigure 7 , -
figure 8 is an exploded perspective view of an external unit of a heat pump, comprising a heat exchanger according to an embodiment, -
figures 9, 10 ,11 are a perspective view (figure 9 ), a side view (figure 10 ) and an exploded view (figure 11 ) of an external unit of a heat pump, comprising a heat exchanger according to an embodiment, -
figures 12, 13 ,14, 15, 16, 17 are diagrammatic views of external or internal units of heat pumps having a heat exchanger according to embodiments of the invention, -
figure 18 shows a heat pump according to an embodiment of the invention, -
figure 19 shows a heat pump according to a further embodiment, -
figures 20, 21, 22 show an air entrainment effect depending on the absence (figure 20 ), presence (figure 21 ), and presence with divergent convex curvature (figure 22 ) of a guide surface. - With reference to the figures, a
heat exchanger 100, in particular for aheat pump 1, comprises: - a
support structure 101, - a
heat exchange unit 102 connected to thesupport structure 101 and having afluid channel system 103 and anair channel system 104 in heat exchange communication with thefluid channel system 103, - an
air conveyor 105 connected to thesupport structure 101 and operable to convey an air flow through theair channel system 104 of theheat exchange unit 102, - a
tubular conveying channel 106 extending from aninlet opening 107 to an annular outlet slot 108 (not necessarily circular), - a driving
air fan 109 placed in the conveyingchannel 106 and operable to suck in a drivingair flow 110 through the inlet opening 107 into the conveyingchannel 106 and expel the drivingair flow 110 from the conveyingchannel 106, through theannular outlet slot 108, in the form of an annular air blade (not necessarily circular) in adriving flow direction 111, - optionally, an annular guide surface 112 (not necessarily circular) with convex continuous curvature, formed downstream of the annular outlet slot 108 (in the direction of the driving air flow 111) and along the entire annular extension of the
annular outlet slot 108, so as to generate a depression due to the aerodynamic and/or Coand effect, which takes in a drivenair flow 113 with a greater flow rate than the drivingair flow 110 in a drivenair flow direction 114, - where the
outlet slot 108 and, if provided, theguide surface 112 are arranged at theheat exchange unit 102, so that at least the drivenair flow 113 crosses theair channel system 104, - where the driving
air fan 109 is arranged outside and at a distance from the drivenair flow 113 and theheat exchanger 100 has no impellers with blades at the drivenair flow 113. - According to an embodiment, the
annular outlet slot 108 and theguide surface 112 are formed together in a single tubular closed-loop structure 115 (not necessarily circular) mounted to thesupport structure 101. - According to an embodiment, the
guide surface 112 is formed by, or forms, aperipheral edge 116 of anexternal housing 117 of theheat exchanger 100 delimiting an air outlet opening 118 of theexternal housing 117. - According to embodiments, the
annular outlet slot 108 and/or the tubular closed-loop structure 115 has a circular shape (figures 1 ,8 ) or oval shape (figure 2 ) or polygonal shape, e.g., rectangular or square (figure 4 ), preferably with rounded corners. This allows adapting the sectional shape of the air flow, at least at theheat exchange unit 102, to the shape of theheat exchange unit 102 itself, and adapting the external dimensions of theheat exchange unit 102 to the space conditions of thehousing 117 of theheat exchanger 100. - According to an embodiment, the conveying
channel 106 is configured to expel the drivingair flow 110 with a substantially uniform, i.e., constant, flow rate along theannular outlet slot 108. This is particularly advantageous in the case of acircular outlet slot 108. - According to an alternative embodiment, the conveying
channel 106 is configured to expel the drivingair flow 110 with a non-uniform flow rate, i.e., not constant, along theannular outlet slot 108. This allows compensating for potential non-uniformity of the drivenair flow 113 in the case of a non-circular shape of theoutlet slot 108. - A local slowdown of the driving
air flow 110, for example at corners or regions of theoutlet slot 108 with a small radius of curvature (which can be achieved by targeted shaping of the inner section of the conveying channel 106), reduces the local divergence trend of drivenair flow 113. - Otherwise, a local increase in flow rate, for example at corners or regions of the
outlet slot 108 with a small radius of curvature (which can be achieved by shaping the inner section of the conveyingchannel 106 in a targeted manner), ensures the presence of a sufficient amount of driven air for the heat exchange even at the margins of the overall dimensions of theheat exchange unit 102. - Advantageously, the
annular outlet slot 108 and/or the tubular closed-loop structure 115 extend in asingle conveyor plane 119, (figures 5, 6, 7 ,8 ) substantially orthogonal to the drivenflow direction 114. - According to embodiments, the
air conveyor 105 can comprise two or more of saidannular outlet slots 108 and/or two or more of the tubular closed-loop structures 115 (figures 3, 4 ,5, 6 ) associated with the sameheat exchange unit 102 or with one of a plurality of saidheat exchange units 102, respectively. This allows optimizing the shape of a "composite" total flow section while using a shape with possibly regular and even curvature, for example a circular or oval shape, of theannular outlet slot 108 and theguide surface 112, advantageous with reference to the uniformity of the drivenair flow 113. - According to an embodiment, the conveying
channel 106 comprises an annular portion (not necessarily circular) 120 forming theannular outlet slot 108, afan seat 121 accommodating (at least a part of) the drivingair fan 109, and a linear portion 122 (curved or straight) connected between thefan seat 121 and the annular portion 120 (figures 7 ,8 ). - According to a further embodiment, the conveying
channel 106 comprises a multiple (e.g., double) annular portion (not necessarily circular) 120, 120 forming the multipleannular outlet slots 108, 108' (e.g., double), afan seat 121 accommodating (at least a part of) the drivingair fan 109, and a single linear portion 120 (curved or straight) connected between thefan seat 121 and the multiple, e.g. double,annular portions 120, 120' (figure 6 ). - According to a further embodiment, the conveying
channel 106 comprises a multiple (e.g., double) annular portion (not necessarily circular) 120, 120' forming multiple, e.g., double,annular outlet slots 108, 108', a plurality of, e.g., two,distinct fan seats 121, 121' each accommodating (at least a part of) one of a plurality of (e.g., two) drivingair fans 109, 109' and a plurality of, e.g., two, distinctlinear portions 120, 120' (curved or straight), each connected between one of the fan seats 121, 121' and one of the multipleannular portions 120, 120'), respectively (figure 5 ). - The different configurations of the conveying
channel 106 allow optimized use of the spaces available inside thehousing 117 of theheat exchanger 100 or of theheat pump 1 to which it is integrated. - According to an embodiment, the
annular outlet slot 108 is arranged (only) upstream of theheat exchange unit 102, seen in the direction of the drivenair flow 113. - According to an alternative embodiment, the
annular outlet slot 108 is arranged (only) downstream of theheat exchange unit 102, seen in the direction of the drivenair flow 113. - According to a still further embodiment, a first outlet slot of the one or more
annular outlet slots 108 of the one ormore air conveyors 105 is arranged upstream of theheat exchange unit 102, and a second slot of the one or moreannular outlet slots 108 of the one ormore air conveyors 105 is arranged downstream of theheat exchange unit 102, seen in a drivenair flow direction 113. This allows obtaining a very high flow rate. - According to an embodiment which is not preferred but still falls within the scope of the invention, in the complete absence of the
guide surface 112, the drivenair flow 113 is generated due to the ejector effect, shown infigure 20 . - According to an embodiment which is not preferred but still falls within the scope of the invention, in the presence of a
guide surface 112 with a straight section in the direction of the drivingair flow 110, the drivenair flow 113 is generated by the Coand effect in combination with the ejector effect, shown infigure 21 . - According to a further, preferred, embodiment, in the presence of a
guide surface 112 with a convex section gradually diverging in the direction of the drivingair flow 110, the drivenair flow 113 is generated by an amplified Coand effect in combination with the ejector effect, shown infigure 22 . - The choice and definition of the precise shape of the
guide surface 112 takes place in a known way, through numerical experimentation (simulation) and practical experimentation (testing), by applying aerodynamic design criteria of the wings of airplanes known per se. Therefore the method of designing theguide surface 112 is not the subject matter of the invention. - According to an embodiment, the
air conveyor 105 comprises aheating device 123, for example an electric resistance, for example arranged upstream of or at theannular outlet slot 108, in order to be able to free the airannular outlet slot 108 and/or theguide surface 112 from deposits of ice or frost. - This is particularly advantageous in external units of
heat pumps 1, with theair conveyor 104 placed downstream of theheat exchange unit 102, when defrosting theheat exchange unit 102 during winter operation. In fact, the moisture from the defrosting of theheat exchange unit 102 could otherwise deposit and freeze at theoutlet slot 108 and/or theguide surface 112. - According to an embodiment, the inlet opening 107 can be in communication with an opening formed in the
support structure 101 and/or in theouter housing 117. - According to an embodiment, the
heat exchanger 100 either lacks a protective grille at the drivenair flow 113 or forms aprotective grille 124 with gaps being wider than a human finger. - Description of embodiments of the
heat pump 1 - According to an embodiment (
figure 18 ) aheat pump 1 comprises: - a
circuit 2 for circulating a refrigerant fluid, - a
first heat exchanger 3 placed in thecircuit 2 and forming anevaporator 4, - a
compressor 5 placed in thecircuit 2 downstream of thefirst heat exchanger 3, - a
second heat exchanger 6 placed in thecircuit 2 downstream of thecompressor 5 and forming acondenser 7, - an
expansion device 8 placed in thecircuit 2 downstream of thesecond heat exchanger 6, - an
electronic control system 9 controlling thecompressor 5, theexpansion device 8, thefirst heat exchanger 3, and thesecond heat exchanger 6, - the
compressor 5 is operable to suck in the refrigerant fluid in the gaseous phase and at low pressure from theevaporator 4, compress the refrigerant fluid, and push it into thecondenser 7, - in the
condenser 7, the compressed refrigerant fluid releases heat and condenses at high pressure, - after leaving the
condenser 7, the refrigerant fluid passes through theexpansion device 8 which depressurizes it, - the refrigerant fluid depressurized by the
expansion device 8 enters into theevaporator 4 where it absorbs heat and evaporates at low pressure, before being sucked in and compressed again by thecompressor 5, - According to an embodiment, the
heat pump 1 comprises anexternal unit 14 intended to be positioned outdoors, aninternal unit 15 intended to be positioned inside a building and connected to a user/application 35, for example a heating/cooling system with aprimary water circuit 16. - Preferably, the
first heat exchanger 3 is aheat exchanger 100 according to the invention. - Preferably, the
second heat exchanger 6 is aheat exchanger 100 according to the invention. - The
external unit 14 comprises (inside a housing which can coincide with theexternal housing 117 of the heat exchanger 100): - the
first heat exchanger 3 provided with an externalair temperature sensor 18 and a refrigerantfluid temperature sensor 19, - the
compressor 5 with atemperature sensor 20 for the refrigerant fluid on the suction side of thecompressor 5, and with atemperature sensor 21 for the refrigerant fluid on the delivery side of thecompressor 5, - a refrigerant
fluid storage vessel 13 arranged on the suction side of thecompressor 5, - a
high pressure switch 22 arranged on the delivery side of thecompressor 5, - the switching/reversing
valve 12, - (connection attachment)
tubes 23 ofcircuit 2, - the
expansion device 8 with one or more electric expansion valves, - a
refrigerant temperature sensor 24 placed in thecircuit 2 between theexpansion device 8 and thesecond heat exchanger 6. - The
internal unit 15 comprises (inside a housing): - the
second heat exchanger 6 which exchanges heat between thecircuit 2 of the refrigerant fluid and theprimary water circuit 16, - a
water pump 25 in theprimary water circuit 16 upstream of thesecond heat exchanger 6, - a flow rate sensor (flowmeter) 26, e.g., on the inlet side of the
water pump 25, - a water
return temperature sensor 27, e.g., on the inlet side of thewater pump 25, - an
expansion vessel 28 of the water connected to theprimary water circuit 16, e.g., on the inlet side of thewater pump 25, - a
water filter 29 connected to theprimary water circuit 16, e.g., upstream of thewater pump 25 and/or upstream of thewater expansion vessel 28, - a water delivery temperature sensor 30 (LWT = Leaving Water Temperature) at the outlet of the
second heat exchanger 6, - a backup
electric heater 31 connected in theprimary water circuit 16, preferably downstream of thesecond heat exchanger 6, to an associated temperature sensor 32, for the water at the outlet of the backupelectric heater 31, and - (connection attachments of)
tubes 33 ofcircuit 2, and - (connection attachments of)
tubes 34 of the primary water circuit. - The user/
application 35 comprises a part of theprimary water circuit 16 and awater vessel 36 and/or a plurality of heaters orradiators 36 for heating and cooling. - According to an embodiment, the
external unit 14 of theheat pump 1 comprises an external housing, which coincides with theexternal housing 117 of theheat exchanger 100, and aninternal separation partition 10, which separates aheat exchange compartment 11 from acompressor compartment 17, where: - the
heat exchange compartment 11 accommodates theheat exchange unit 102, and - the
compressor compartment 17 accommodates thecompressor 5. - According to an embodiment, the
entire air conveyor 105 is positioned in the heat exchange compartment 11 (figures 8 ,13 ,14, 16 ). This allows utilizing spaces, for example in corners, currently unoccupied, in order to generate the air flow. - According to an alternative embodiment, the conveying
channel 106 extends from thecompressor compartment 17 into theheat exchange compartment 11 and the drivingair fan 109, 109' is positioned in the compressor compartment 17 (figures 9 ,11 ,12 ,15, 17 ). This allows utilizing the entireheat exchange compartment 11, even in the extension thereof in the direction of the air flow, for the heat exchange function and utilizing currently unused spaces of thecompressor compartment 17 to generate the drivingair flow 110. - According to an embodiment, the inlet opening 107 of the
air conveyor 105 can be in communication with thecompressor 5 for cooling thecompressor 5. - According to an embodiment, the
compressor compartment 17 is laterally near the heat exchange compartment 11 (figures 8 ,11 ,12, 13 ). - According to an embodiment, the
compressor compartment 17 is positioned below the heat exchange compartment 11 (figures 14, 15 ). - According to an embodiment, the
compressor compartment 17 is positioned above the heat exchange compartment 11 (figures 16, 17 ). - According to an embodiment, the driven
air flow 113 is substantially vertical, preferably upwards (figures 9 ,11 ), or less preferably downwards. - According to an embodiment, the driven
air flow 113 is substantially horizontal (figure 8 ). - According to an embodiment, the
compressor compartment 17 also accommodates thetemperature sensor 20 for the refrigerant fluid on the suction side of thecompressor 5, and thetemperature sensor 21 for the refrigerant fluid on the delivery side of thecompressor 5, thestorage vessel 13 for refrigerant fluid arranged on the suction side of thecompressor 5, the switching/reversingvalve 12, theexpansion device 8, and therefrigerant temperature sensor 24 located in thecircuit 2 between theexpansion device 8 and thesecond heat exchanger 6. -
-
heat pump 1 -
circuit 2 -
first heat exchanger 3 -
evaporator 4 - a
compressor 5 -
second heat exchanger 6 -
condenser 7, -
expansion device 8 -
electronic control system 9 -
internal separation partition 10 -
heat exchange compartment 11 - switching/reversing
valve 12 -
storage vessel 13 -
external unit 14 -
internal unit 15 -
primary water circuit 16 -
compressor compartment 17 - external
air temperature sensor 18 -
temperature sensor 19 for the refrigerant fluid in the first heat exchanger, -
temperature sensor 20 for the refrigerant fluid on the suction side of thecompressor 5 -
temperature sensor 21 for the refrigerant fluid on the delivery side of thecompressor 5 -
high pressure switch 22 - (connection attachments of)
tubes 23 of therefrigerant circuit 2 -
refrigerant temperature sensor 24 -
water pump 25 - water
flow rate sensor 26 -
water temperature sensor 27 -
water expansion vessel 28 -
water filter 29 - water
delivery temperature sensor 30 - backup
electric heater 31 - temperature sensor 32 for the water at the outlet of the electric heater (connection attachments of)
tubes 33 of the refrigerant circuit 2 (connection attachments of the)tubes 34 of the primarywater circuit user 35 - water vessels/
radiators 36 -
heat exchanger 100 -
support structure 101 -
heat exchange unit 102 -
fluid channel system 103 -
air channel system 104 -
air conveyor 105 - conveying
channel 106 -
inlet opening 107 -
outlet slot 108 - driving
air fan 109, 109' - driving
air flow 110 - driving
flow direction 111 - guide
surface 112 - driven
air flow 113 - driven
flow direction 114 - tubular closed-
loop structure 115 -
peripheral edge portion 116 -
external housing 117 - air outlet opening 118 of the housing
-
conveyor plane 119 -
annular portion 120, 120' of the conveying channel -
fan seat 121, 121' -
linear portion 122, 122' -
heating device 123 -
protective grille 124
Claims (16)
- A heat pump (1) comprising:- a circuit (2) for circulating a refrigerant fluid,- a first heat exchanger (3) placed in the circuit (2) and forming an evaporator (4),- a compressor (5) placed in the circuit (2) downstream of the first heat exchanger (3),- a second heat exchanger (6) placed in the circuit (2) downstream of the compressor (5) and forming a condenser (7),- an expansion device (8) placed in the circuit (2) downstream of the second heat exchanger (6),- an electronic control system (9) controlling the compressor (5), the expansion device (8), the first heat exchanger (3), and the second heat exchanger (6),wherein:- the compressor (5) is operable to suck the refrigerant fluid in the gaseous phase and at low pressure from the evaporator (4), compress the refrigerant fluid, and push it into the condenser (7),- in the condenser (7), the compressed refrigerant fluid releases heat and condenses at high pressure,- after leaving the condenser (7), the refrigerant fluid passes through the expansion device (8) which depressurizes it,- the refrigerant fluid depressurized by the expansion device (8) enters in the evaporator (4) where it absorbs heat and evaporates at low pressure, before being sucked and compressed again by the compressor (5),wherein the heat pump (1) comprises an external unit (14) intended to be positioned in an external environment, an internal unit (15) intended to be positioned inside a building,wherein at least one of the first (3) and second (4) heat exchangers is a heat exchanger (100) integrated in the external unit (14),wherein said heat exchanger (100) integrated in the external unit (14) comprises:- a support structure (101),- a heat exchange unit (102) connected to the support structure (101) and having a fluid channel system (103) and an air channel system (104) in heat exchange communication with the fluid channel system (103),- an air conveyor (105) connected to the support structure (101) and operable to convey an air flow through the air channel system (104) of the heat exchange unit (102), wherein the air conveyor (105) comprises:- a tubular conveying channel (106) extending from an inlet opening (107) to an annular outlet slot (108),- a driving air fan (109) placed in the conveying channel (106) and operable to suck a driving air flow (110) through the inlet opening (107) into the conveying channel (106) and expel the driving air flow (110) from the conveying channel (106), through the annular outlet slot (108), in the form of an annular air blade in a driving flow direction (111),so as to generate an aerodynamic depression which sucks a driven air flow (113) with a higher flow rate than the flow rate of the driving air flow (110), in a driven flow direction (114),wherein the outlet slot (108) is arranged at the heat exchange unit (102), so that at least the driven air flow (113) crosses the air channel system (104),wherein the driving air fan (109) is arranged outside and at a distance from the driven air flow (113) and the heat exchanger (100) has no impellers with blades at the driven air flow (113).
- A heat pump (1) according to claim 1, wherein said heat exchanger (100) comprises an annular guide surface (112) with convex continuous curvature, formed downstream of the annular outlet slot (108) in the direction of the driving air flow (111) and along the entire annular extension of the annular outlet slot (108), so as to generate a depression also due to the Coand effect, which sucks the driven air flow (113).
- A heat pump (1) according to claim 2, wherein the annular outlet slot (108) and the guide surface (112) are formed together in a single tubular closed-loop structure (115) mounted to the support structure (101).
- A heat pump (1) according to claim 2 or 3, wherein the guide surface (112) is formed by - or forms - a peripheral edge (116) of an external housing (117) of the heat exchanger (100) delimiting an air outlet opening (118) of the external housing (117).
- A heat pump (1) according to one of the preceding claims, wherein the annular outlet slot (108) and/or the tubular closed-loop structure (115) has a circular or oval shape or polygonal shape with rounded edges.
- A heat pump (1) according to one of the preceding claims, wherein the annular outlet slot (108) and/or the tubular closed-loop structure (115) extend in a single conveyor plane (119) orthogonal to the driven flow direction (114).
- A heat pump (1) according to one of the preceding claims, wherein the air conveyor (105) comprises two or more of said annular outlet slots (108) associated with the same heat exchange unit (102) or with one of a plurality of said heat exchange units (102), respectively.
- A heat pump (1) according to one of the preceding claims, wherein the conveying channel (106) comprises an annular portion (120) forming the annular outlet slot (108), a fan seat (121) accommodating at least a part of the driving air fan (109), and a linear portion (122) connected between the fan seat (121) and the annular portion (120).
- A heat pump (1) according to one of the preceding claims, wherein the conveying channel (106) comprises a multiple or double annular portion (120, 120') forming multiple or double annular outlet slots (108, 108'), a fan seat (121) accommodating at least a part of the driving air fan (109), and a single linear portion (120) connected between the fan seat (121) and the multiple or double annular portions (120, 120').
- A heat pump (1) according to one of claims 1 to 8, wherein the conveying channel (106) comprises a multiple annular portion (120, 120') forming multiple annular outlet slots (108, 108'), a plurality of distinct fan seats (121, 121') each accommodating at least a part of one of a plurality of driving air fans (109, 109') and a plurality of distinct linear portions (120, 120'), respectively, each connected between one of the fan seats (121, 121') and one of the annular portions (120, 120'), respectively.
- A heat pump (1) according to any one of the preceding claims, wherein the annular outlet slot (108) is arranged upstream of the heat exchange unit (102), seen in the driven flow direction (114), or wherein the annular outlet slot (108) is arranged downstream of the heat exchange unit (102), seen in the driven flow direction (114).
- A heat pump (1) according to any one of the preceding claims, wherein the air conveyor (105) comprises a heating device (123) configured to defrost the annular outlet slot (108).
- A heat pump (1) according to any one of the preceding claims, wherein said heat exchanger (100) has no protective grille at the driven air flow (113).
- A heat pump (1) according to any one of the preceding claims, wherein the external unit (14) comprises an external housing, which coincides with an external housing (117) of the heat exchanger (100), and an internal separation partition (10), which separates a heat exchange compartment (11) containing the heat exchange unit (102) from the compressor compartment (17) housing the compressor (5),
wherein the annular outlet slot (108) is positioned at the heat exchange compartment (11). - A heat pump (1) according to claim 14, wherein the entire air conveyor (105) is positioned in the heat exchange compartment (1 1),or
wherein the conveying channel (106) extends from the compressor compartment (17) into the heat exchange compartment (11) and the driving air fan (109, 109') is positioned in the compressor compartment (17). - A heat pump (1) according to any one of the preceding claims, wherein the inlet opening (107) of the air conveyor (105) is or can be switched, in communication with the compressor (5) for at least temporarily cooling the compressor (5) and at least temporarily heating the driving air flow (110) upstream of the annular outlet slot (108).
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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IT202200022833 | 2022-11-07 |
Publications (1)
Publication Number | Publication Date |
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EP4365503A1 true EP4365503A1 (en) | 2024-05-08 |
Family
ID=85019068
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP23202106.3A Pending EP4365503A1 (en) | 2022-11-07 | 2023-10-06 | A heat pump with a bladeless fan heat exchanger |
Country Status (2)
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EP (1) | EP4365503A1 (en) |
CN (1) | CN117989751A (en) |
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CN107655075A (en) * | 2017-09-28 | 2018-02-02 | 青岛海尔空调器有限总公司 | Wall-hanging indoor unit of air conditioner |
US20180045203A1 (en) * | 2016-08-15 | 2018-02-15 | Chia-Ning Yang | Fan |
CN113757825A (en) * | 2021-09-28 | 2021-12-07 | 珠海格力节能环保制冷技术研究中心有限公司 | Air conditioner outdoor unit and air conditioning equipment |
-
2023
- 2023-10-06 EP EP23202106.3A patent/EP4365503A1/en active Pending
- 2023-11-07 CN CN202311472469.0A patent/CN117989751A/en active Pending
Patent Citations (7)
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CN104033955A (en) * | 2013-03-06 | 2014-09-10 | 广东美的暖通设备有限公司 | Air conditioner indoor unit and air conditioner with same |
CN204693612U (en) * | 2015-03-31 | 2015-10-07 | 四川长虹电器股份有限公司 | A kind of air-conditioning indoor host computer |
US20170097164A1 (en) * | 2015-10-02 | 2017-04-06 | Google Inc. | See-through in-window air conditioner unit |
CN205048677U (en) * | 2015-10-12 | 2016-02-24 | 珠海格力电器股份有限公司 | Air guide structure of air conditioner, air duct machine and air conditioner |
US20180045203A1 (en) * | 2016-08-15 | 2018-02-15 | Chia-Ning Yang | Fan |
CN107655075A (en) * | 2017-09-28 | 2018-02-02 | 青岛海尔空调器有限总公司 | Wall-hanging indoor unit of air conditioner |
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CN117989751A (en) | 2024-05-07 |
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