US20200300498A1 - A compact heat recovery ventilation system - Google Patents

A compact heat recovery ventilation system Download PDF

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Publication number
US20200300498A1
US20200300498A1 US16/089,431 US201716089431A US2020300498A1 US 20200300498 A1 US20200300498 A1 US 20200300498A1 US 201716089431 A US201716089431 A US 201716089431A US 2020300498 A1 US2020300498 A1 US 2020300498A1
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United States
Prior art keywords
ventilation system
heat recovery
recovery ventilation
compact heat
exhaust gas
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Abandoned
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US16/089,431
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English (en)
Inventor
Edward Lopatinsky
Daniel Schaefer
Loftsson JOHANNES
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INDUSTRIAL DESIGN LABORATORIES Inc
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Individual
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Priority to US16/089,431 priority Critical patent/US20200300498A1/en
Assigned to INDUSTRIAL DESIGN LABORATORIES INC. reassignment INDUSTRIAL DESIGN LABORATORIES INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: JOHANNES, Loftsson, LOPATINSKY, EDWARD, SCHAEFER, DANIEL
Publication of US20200300498A1 publication Critical patent/US20200300498A1/en
Abandoned legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating devices
    • B60H1/00321—Heat exchangers for air-conditioning devices
    • B60H1/00335—Heat exchangers for air-conditioning devices of the gas-air type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • F24F12/006—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an air-to-air heat exchanger
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating devices
    • B60H1/00321—Heat exchangers for air-conditioning devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating devices
    • B60H1/02—Heating, cooling or ventilating devices the heat being derived from the propulsion plant
    • B60H1/03—Heating, cooling or ventilating devices the heat being derived from the propulsion plant and from a source other than the propulsion plant
    • B60H1/039—Heating, cooling or ventilating devices the heat being derived from the propulsion plant and from a source other than the propulsion plant from air leaving the interior of the vehicle, i.e. heat recovery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression
    • 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
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • 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
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • 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
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • F04D25/163—Combinations of two or more pumps ; Producing two or more separate gas flows driven by a common gearing arrangement
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/20—Casings or covers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0014—Recuperative heat exchangers the heat being recuperated from waste air or from vapors
    • 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
    • F24F2221/14—Details or features not otherwise provided for mounted on the ceiling
    • 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
    • F24F2221/17—Details or features not otherwise provided for mounted in a wall
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/56—Heat recovery units

Definitions

  • the present invention relates generally to heat ventilation and air conditioning (HVAC) systems for moving air, and/or regulating the temperature, humidity, chemistry and quality of indoor air. More particularly, the present invention relates to air processing devices such as ventilators, including heat ventilators, coolers, air conditioners humidifiers and air purifiers.
  • HVAC heat ventilation and air conditioning
  • the present invention is particularly, but not exclusively, useful for systems that are mounted inside a wall or ceiling and constitute a part of room decor; therefore, thickness of the system is a critical factor. Another critical factor is the countercurrent air flow (air flowing in opposite directions) that provides the highest energy recovery efficiency or chemical recovery efficiency.
  • HVAC heat ventilation and air conditioning
  • the countercurrent principle is a vital factor in many ventilation processes. Heating or cooling energy in the exhaust air can be preserved by recovering it and directing it into the replacement air through a heat exchanger. Low indoor humidity levels can also be better maintained in hot and humid environments by extracting the humidity out of the supply air into the exhaust air through various countercurrent processes (like desiccant wheel, water permeable membrane etc.). Same method can be used to help maintain sufficient high indoor humidity level by extracting much of the humidity from the exhaust air into the supply air. Some industrial processes can also benefit from using an extraction method based on a countercurrent (or cross-current) principle, in order to minimize pollution or waste, or to make the process more efficient.
  • good ventilation systems can also have various other air processing units, such as filters including activated carbon, humidifier, dehumidifier, heater, cooler and others, which may improve the quality of air, while a long duct system may be necessary to efficiently extract or supply the air in the right locations. All these processes and systems (countercurrent, cross-current or in-line) restrict the airflow and contribute to the pressure drop of the ventilation system. Ambient pressure fluctuations due to weather or movement of an enclosure is another source of the pressure load that requires additional power consumption for ventilation system.
  • Crossflow blowers are used in air processing devices more often due to their affordable mounting performance and a well-known ability to achieve relatively high efficiency that does not depend upon diameter size. Moreover, the crossflow blower creates much more static pressure at the same airflow, unlike the centrifugal blower, when other conditions are equal.
  • air processing devices comprise a base with a flat surface for wall mounting and the axis of the crossflow blower is parallel in respect to that surface.
  • electric motors for typical crossflow blowers are located adjacent to the impellers, because if a conventional electric motor is placed inside the impeller, it greatly affects the internal aerodynamic structure of the crossflow blower, thus dramatically decreasing performance characteristics.
  • Heat exchanging type fan consisting of a casing and two centrifugal fans mounted on the same shaft inside the casing, but oriented in opposite directions in regard to each other, creating concurrent flow through a heat exchanger.
  • Two co-current channels for heat carriers of different temperatures are formed in the casing, separated by a partition separating both fans.
  • the heat exchange element comprises radial fins mounted on both surfaces of the partition beyond the edges of the impellers of the fans.
  • Heat-exchanger is one of the most important part of the countercurrent heat recovery ventilation system.
  • changeable air flow sides could be made in the following ways: designed as folded fins with a center plate divider, or as plate heat exchanger based on the same principals as changing air flow sides.
  • the center plate dividers are only located at the open ends of the heat exchanger but not inside it. This gives additional flexibility in design as the air is free to move between one side of the outside panel at the intake of heat exchanger, to the opposite side of outside panel at the outtake of heat exchanger.
  • the airstream is separated to plurality of thin airstreams moving in a way that any other thin stream flows in opposite direction.
  • Efficient motor is very important part for any heat recovery system as the part that providing energy saving.
  • Several improvements for better motor efficiency level have been done according to US Patent 2004 245866 (A1) “Integrated cooler for electronic devices,” which describes a flat cooling unit consisting of crossflow blower connected to heatsink removing heat from a co-current flow around heat pipes.
  • US Patent 2005 121996A1 “Electric dive for radial impeller” describes a flat peripheral motor with coils printed on a PCB board and magnetic means fixed with the radial impeller and even integrated in the blades. This compact design has high efficiency which is increased further by leaving space in center of the radial blower allowing higher airflow.
  • Integrated blower for cooling device describes a peripheral motor for a radial blower with stator and rotor in the same plane. This arrangement produces lower motor vibration, which results in lower motor noise, higher efficiency and ensures higher airflow.
  • US patent 2006 238064A1 “Flat radially integrated electric drive and method of the manufacturing the same”, describes stator of the motor printed in a PCB board where the motor and the rotor are on the same plane.
  • US 2006 056153 A1 “Multi-heatsink integrated cooling device,” describes flat crossflow cooler connected to two heat sinks.
  • US Patent 2008 101966A1 “High efficient compact radial blower” describes an integrated blower, motor and heat sink, which uses printed coils, and locates the heat sink inside the blower.
  • US Patent 2007 166177(A1) “Thin air processing device for heat ventilation air conditioning system”, describes an efficient design for a single flat cross flow blower and the benefits of connecting it to an air processing unit like purifier, humidifier or temperature regulating means.
  • US Patent 2008 238218(A1) describes an improved method of arranging coils in motor partially printed on a PCB board. This arrangement increases the motor power, and efficiency.
  • the present invention is an approach to resolve in particular situations where only limited space is available for ventilation system, by inventing a ventilation system that can easily be integrated into the structural envelope of an enclosure (building, car, boat, plane or similar).
  • a ventilation system that can easily be integrated into the structural envelope of an enclosure (building, car, boat, plane or similar).
  • Such configuration is achieved herein by a system, based on the countercurrent principle, with flat countercurrent heat exchanger and flat blowers powerful enough to perform and the system thin enough to fit inside the wall or ceiling.
  • An additional benefit of the compact flat system of the invention is that the system's length does not have to be restricted. Any air handling unit which has the same thickness and width can be added to the system without compromising aesthetics or style of the system. This gives the system additional functional flexibility (modularity), as each of the air treatment modules can be chosen independently so that it can meet its functional requirements, thus allowing for additional flexibility in design.
  • the whole heat recovery system is made from two major components, namely a air module assembly and heat exchanger assembly.
  • the air module assembly comprises two radial blowers surrounded by airflow guides, placed on the common axis using peripheral motor. Housing made from two side panels and base plate between these side panels. These blowers along with airflow guides, side panels and base plate form two hydraulically isolated counter flow canals with inlet and outlet openings for each of the canal.
  • Heat exchanger assembly comprises a box with heat exchange elements surrounded by outside panels.
  • the box further compromises an intake and outtake openings and a center plate dividing the whole heat exchanger assembly in two hydraulically isolated flow conduits with intake and outtake openings.
  • Side panels of the air module assembly are fixed with outside panels of the heat exchanger.
  • Base plate of the air module assembly is fixed with center plate of the heat exchanger assembly. Therefore, such arrangement allows hydraulically connecting canals of the air module assembly to flow conduits of heat exchanger assembly respectively.
  • the air module assembly comprises a base plate fixed with the side panels thru airflow guides and placed parallel between the side panels.
  • Two radial blowers are spaced between side panels from both sides of the base plate, while the other part of the base is fixed to the center plate of the heat exchange assembly.
  • Two radial blowers further comprise two radial impellers spaced from both sides of the base plate, thus each of the radial impellers is located at one of flow passages.
  • Each of the radial impellers comprises a back plate disk with radial blades that are spaced apart.
  • Heat exchanging elements protruding from both sides of the base plate thus spaced inside of each flow passages are forming an exhaust and fresh heat-exchanging sides of the integrated heat exchanger.
  • the heat-exchanger could also done as changing flow side heat-exchanger made as folded fins or plates, thus each of the both flow passages split in many separate flow channels. Every other channel forcing the flow in the opposite direction.
  • the electric drive preferably comprises a flat stator fixed attached to the base plate, and a rotor with magnetic elements integrated with at least one of the back plate disk, thus the double side radial impeller serves as the rotor of the motor.
  • the stator size (diameter) is larger than the radial blower diameter, when electrically powered, creates alternating electromagnetic fields that interact with a magnetic field created by the magnetic elements, thus providing a rotation of the double side radial impeller, causing the exhaust gas flow through the outtake side of the heat exchanger, while fresh gas flows through the intake side of the heat exchanger.
  • the base plate of the air module assembly further comprises volute casings for each of the radial impeller, that formed by flow guides protruding from both sides of the base plate, one of the two flow guides serves as a tongue of the volute casing, while the other flow guide serves as a spiral part.
  • one of the inlet opening is located at the side panel, both radial impellers rotate in one direction and one of the radial impellers operates as a centrifugal blower, while the other radial impeller operates as a crossflow blower.
  • the flow guides of the centrifugal blower serve as the volute casings directing the airflow for one part of the flow canal.
  • the flow guides on other of base plate create the second flow canal made by crossflow blower.
  • the Heat Exchanger assembly includes heat exchanging elements located in the line of the intake and the outtake openings in a consecutive way for the flow conduits, thus providing counter-flow heat exchange process.
  • the electric drive can be made as a conventional electric motor spaced inside of the radial impeller of the centrifugal blower.
  • the radial impellers rotate in one direction and operate as crossflow blowers, two flow guides are shifted in view perpendicular to the shaft in angular direction, therefore the fresh gas flows through the intake openings, the heat exchanging elements, inlet, the crossflow impeller and the outlet openings in a consecutive way, while other air flows through the inlet openings, the radial impeller, intake of the heat exchanging elements, outtake in a consecutive way form another flow passage, thus providing countercurrent flow heat exchange process.
  • the electric drive can be made as a peripheral thin motor placed between crossflow impellers.
  • the heat exchanger assembly can further comprise the heat exchanging elements, thus forming two elongated flow passages serving as the exhaust and fresh sides of the integrated heat exchanger.
  • the heat-exchanger could also be built as changing flow side heat-exchanger made as folded fins or plates, thus both flow passages split in plurality of flow channels. Every other channel would be forcing the flow in opposite direction.
  • a preferred heat-exchanger for this design is per patent DE 4301296 A1 with some improvements described further.
  • the flat stator comprises circumferential arrayed coil windings with magnetic axes coincided with a plane of the flat stator and integrated with the base plate, while the magnetic elements made as circumferential arrayed permanent magnets are placed and magnetized along the plane of the flat stator, thus magnetic axes of the coil windings and the permanent magnets are located at one plane substantially.
  • the exhaust air flows through the intake opening, the heat exchange elements, the radial impeller, and the outlet openings in a consecutive way for one airflow passage while the other airflow passage of the fresh air flows through inlet opening, radial impeller, heat exchange elements and outtake opening.
  • FIG. 1 is a perspective view showing the first embodiment of the compact heat recovery ventilation system for the present invention containing one centrifugal and one crossflow blower. (ducts and filters are not shown)
  • FIG. 2 is a perspective view showing the second embodiment of the compact heat recovery ventilation system for the present invention containing two crossflow blowers. (ducts and filters are not shown).
  • FIG. 3 is an exposed view of one of the crossflow blowers from FIG. 2 that shows the integrated crossflow blower including motor elements.
  • FIG. 4 is perspective view showing the second embodiment of the current invention including ducts.
  • FIGS. 5-7 are schematic views showing options for mounting inside the wall or ceiling for the compact heat recovery ventilation system using changing side heat exchanger for the present invention.
  • FIGS. 8-10 are schematic views showing options for mounting inside the wall or ceiling for the heat recovery system using traditional heat exchanger for the present invention
  • FIGS. 11-12 are schematic views showing options for mounting on the wall or ceiling for the compact heat recovery ventilation system using changing side heat exchanger for the present invention.
  • FIGS. 13-14 are schematic views showing options for mounting on the wall or ceiling for the compact heat recovery ventilation system using traditional heat exchanger for the present invention.
  • FIG. 15 Flat schematic view showing all connected in length components including blower, heat exchanger, filter, silencers with the exhaust gas duct.
  • FIG. 16 Flat schematic view showing all connected in length components including blower, heat exchanger, filter, silencers with the fresh gas duct.
  • FIG. 17 is a cross section of the two blowers including integrated motor placed inside the housing.
  • FIG. 18 a is showing a traditional heat-exchanger view from the intake and outtake;
  • FIG. 18 b showing a traditional heat-exchanger cross-sectioned along the flow conduit.
  • FIG. 19 a is showing a changing flow sides corrugated fins heat-exchanger front view from one open end;
  • FIG. 19 b the same heat-exchanger back view from the other open end.
  • FIG. 19 c is showing cross-sectioned along one of the odd changing sides flow conduit.
  • FIG. 19 d is showing cross-sectioned along one of the even changing sides flow conduit.
  • FIG. 20 a is showing a changing flow sides plate fins heat-exchanger 3 d section view from the open end (top outside panel is not shown).
  • FIG. 20 b is showing cross-sectioned along one of the odd changing sides flow conduit.
  • FIG. 20 c is showing cross-sectioned along one of the even changing sides flow conduit.
  • FIG. 21 is a perspective view showing the second embodiment of the current invention with L-shaped transition duct between heat exchanger and blowers.
  • FIG. 22 is a perspective view showing the second embodiment of the current invention with L-shaped heat exchanger.
  • FIG. 23 is a perspective view showing the second embodiment of the current invention with 2 transition ducts between the heat exchanger assembly and air module assembly.
  • a compact heat recovery system 1 ( FIGS. 1-23 ) comprises air module assembly 2 and heat exchanger assembly 3 .
  • Air module assembly 2 includes base plate 4 , two radial blowers 5 and 6 airflow guides 7 , two side panels 8 and 9 .
  • the base plate 4 located between radial blower 5 and 6 , divides the airflow in two hydraulically isolated canals, exhaust gas canal 12 and fresh gas canal 13 with exhaust gas inlet 14 , fresh gas inlet 15 and exhaust gas outlet 16 , fresh gas outlet 17 .
  • the heat exchanger assembly 3 comprises of heat exchanging elements 20 , center plate 21 fixed with outside panels 22 and 23 and withe with heat exchanger sides 18 and 19 .
  • the center plate 21 divides openings of the ends 24 , 25 of the heat exchanger assembly 3 for two hydraulically isolated flow conduits 28 and 29 with exhaust gas intake 31 , fresh gas intake 32 and exhaust gas outtake 34 , fresh gas 36 outtake located at the ends 24 , 25 .
  • the base plate 4 , side panels 8 , 9 of the air module assembly 2 connected respectively to the center plate 21 , outside panels 22 , 23 of the heat exchanger assembly 3 .
  • FIG. 1 shows the option of two blowers 5 and 6 , one of them is a centrifugal blower 41 and the other is a cross flow blower 42 . Both blowers 41 and 42 placed on the common shaft 44 and integrated with electric drive 45 .
  • FIG. 2 shows the option of two radial blowers 5 and 6 , both of them made as crossflow blowers 49 and 50 .
  • both crossflow impellers 46 and 47 placed on the common shaft 44 and integrated with electric drive 45 rotate in one direction and operate as crossflow blowers 49 , 50 .
  • Two airflow guides 51 , 52 are outside the cross flow impellers 46 , 47 and a guide vain 56 is located inside of each cross flow impeller 46 , 47 , therefore, exhaust gas flows through exhaust gas inlet duct 54 A, exhaust gas inlet 53 , cross flow blower 49 , in exhaust gas canal 12 , exhaust gas outlet 53 A, exhaust gas intake 31 through heat exchanging elements 20 and exhaust gas outtake 34 of heat exchanger assembly 3 and exhaust gas outtake duct 54 , while fresh gas flows through the fresh gas intake duct 55 , fresh gas intake 32 through heat exchanging elements 20 , fresh gas outtake 36 of the heat exchanger assembly 3 , fresh gas inlet 15 , cross flow blower 50 in fresh gas canal 13 , and fresh gas outlet 17 , fresh gas outlet duct 55 A of air module assembly 2 , thus providing countercurrent
  • the double radial impeller 57 comprises two radial impellers 46 and 47 that are respectively spaced between each side 58 and 59 of the base plate 4 and side panels 8 and 9 , thus each of the radial impellers 46 and 47 located in each of the canal 12 and 13 .
  • One of the back plate disk 61 comprises magnetic elements 62 , thus both of the back plate discs 60 and 61 form the rotor 63 .
  • Base plate 4 is divided in plane perpendicular to its thickness in two parts 64 , 65 having between them a stator 67 that along with rotor 63 serves as the electric drive 45 of the air module assembly 2 .
  • the stator 67 comprises of a circumferential arrayed coil windings 72 with magnetic axes coincided with a plane of the flat stator 67 and integrated with the base plate 4 , while the magnetic elements 62 made as circumferential arrayed permanent magnets 70 placed and magnetized along the plane of the flat stator 68 , thus magnetic axes of the coil windings 69 and the permanent magnets 70 located at one plane substantially.
  • a first design option FIG. 3
  • the stator 67 comprises of a circumferential arrayed coil windings 72 with magnetic axes coincided with a plane of the flat stator 67 and integrated with the base plate 4
  • the magnetic elements 62 made as circumferential arrayed permanent magnets 70 placed and magnetized along the plane of the flat stator 68 , thus magnetic axes of the coil windings 69 and the permanent magnets 70 located at one plane substantially.
  • the flat stator 68 comprises circumferential arrayed coil windings 72 with magnetic axes perpendicular to a plane of the flat stator 68 and integrated with the base plate 4 , while the magnetic elements made 62 as circumferential arrayed permanent magnets 70 are magnetized perpendicular to the plane of the flat stator 68 , thus magnetic axes of the coils windings 72 and the permanent magnets 70 of the rotor 63 are substantially parallel.
  • Peripheral parts 60 and 61 of the rotor 63 placed inside of cylindrical cavities 91 and 92 , creating a labyrinth 93 hydraulically isolating canals 12 and 13 of air module assembly 2 .
  • FIG. 15 shows the fresh gas passage in a planar section of a compact heat recovery ventilation system 1 , including air module assembly 2 , heat exchanger assembly 3 , fresh air filter assembly 86 and silencer assemblies 87 .
  • Fresh gas flows through filter assembly 86 , silencer assembly 87 , heat exchanger assembly 3 , transition duct 88 , crossflow blower 50 of air module assembly 2 , and through a silencer assembly 87 .
  • FIG. 16 shows the exhaust gas passage in a planar section of a compact heat recovery ventilation system 1 , including air module assembly 2 , heat exchanger assembly 3 , fresh air filter assembly 86 and silencer assemblies 87 . Exhaust gas flows through filter assembly 86 , silencer assembly 87 , crossflow blower 49 of air module assembly 2 , transition duct 88 , heat exchanger assembly 3 , silencer assembly 87 and exhaust gas outtake duct 54 .
  • FIG. 18 a and FIG. 18 b shown one of the options for heat exchanger assembly 3 with traditional heat exchange elements 20 made as a center plate 21 with protruded fins 76 from both sides of the center plate 21 .
  • the center plate 21 forms separation between the two conduits 28 , 29 along the length of the heat exchanger assembly 3 .
  • Exhaust gas is restricted to flow through conduit 28 from end 25 to end 24 along the side of the outside panel 22 thus exiting on the same outside panel side 22 as entered.
  • Fresh gas is restricted to flow through conduit 29 from end 24 to end 25 along the side of the outside panel 23 thus exiting on the same outside panel side 23 as it entered.
  • FIGS. 19 ( a,b,c,d ) show changeable gas flow side heat exchangers could be made as corrugated fins with a base plate divider or as plate heat exchanger based on the same principles FIGS. 20 ( a,b,c,d ).
  • the center plate 21 splits in two end center plates 74 , 75 located respectively at the ends 24 , 25 of the heat exchanger assembly 3 for both configurations.
  • FIG. 19 ( a,b,c,d ) includes the heat exchanger assembly 3 with heat exchanging elements 20 shaped as corrugated fins 78 made as a plurality of channels 79 divided by end center plate 74 and 75 located respectively at the ends 24 , 25 of the heat exchanger assembly 3 .
  • End 25 has exhaust gas intake 31 and fresh gas outtake, 36 while the end 24 has fresh gas intake 32 and exhaust gas outtake 34 .
  • every even channel 81 is sealed and every odd channel 82 is open, while at the fresh gas outtake 36 at the same end 24 every odd channel 82 is sealed and every even channel 81 is open.
  • Fresh gas flows through the fresh gas intake 32 next to outside panel 23 at end 25 , through open even channels 81 out to the fresh gas outtake 36 next to outside panel 22 at end 24 , thus gas is forced to change sides.
  • FIGS. 20 ( a,b,c,d ) includes the heat exchanger assembly 3 with heat exchanging elements 20 .
  • the heat exchanging elements 20 are of plate type, where at both ends 24 and 25 at exhaust gas outtake 34 and exhaust gas intake 31 plurality of pairs of all odd plates 84 and even plates 83 are bended and sealed together.
  • the exhaust gas intake 31 is separated from fresh gas outtake 36 by center plate 74 .
  • the fresh gas intake 32 is separated from exhaust gas outtake 34 by center plate 75 .
  • the exhaust gas flows through the exhaust gas intake 31 next to outside panel 22 at end 24 , through open odd channels 82 to the exhaust gas outtake 34 next to outside panel 23 at end 25 , thus gas is forced to change sides.
  • Fresh gas flows through the fresh gas intake 32 next to outside panel 23 at end 25 , through open even channels 81 out to the fresh gas outtake 36 next to outside panel 22 at end 24 , thus gas is forced to change sides.
  • the heat exchangers described in FIGS. 19 and 20 are the most beneficial for our proposed application.
  • the heat transfer distance is much shorter, and therefore, the heat exchanger efficiency relies in much lesser degree on heat conductance coefficient of the heat exchanger material.
  • the heat exchanger can therefore be made out of plastic material.
  • upgrading the heat recovery system to an energy recovery system is very beneficial for our proposed application.
  • the changing or sides of the airflow inside the heat exchanger is also beneficial as it can be used to prevent formation of dead pockets inside the heat exchanger which may accumulate and condensate dirt, hence, having both outlets on the bottom side can help reduce any such accumulation inside the heat exchanger.
  • FIGS. 21, 22 and 23 show three different alignments of the compact heat recovery ventilation system 1 .
  • FIG. 21 shows L-shaped transition 89 where heat exchanger outside panels 22 , 23 and center plate 21 no longer connect directly with the air module assembly 2 , and are no longer parallel with side panels 8 , 9 or base plate 4 of the air module assembly 2 .
  • FIG. 22 shows a configuration where the compact heat recovery ventilation system 1 has a bent exchanger assembly 3 .
  • FIG. 23 shows configuration where the compact heat recovery ventilation assembly 1 , has two separate transition ducts connecting heat exchanger assembly 3 to the air module assembly 2 .
  • the air module assembly 2 is connected to the heat exchanger assembly 3 with transition ducts.
  • the exhaust gas flows through the exhaust gas duct inlet duct 54 A, exhaust gas inlet 14 , crossflow blower 49 in the exhaust gas canal 12 of the air module assembly 2 , the exhaust gas outlet 53 A, the exhaust transition channel 90 of the L shaped transition 89 , exhaust gas intake 31 through heat exchanging elements 20 and exhaust gas outtake 34 of heat exchanger assembly 3 , while fresh gas flows through the fresh gas intake 32 through heat exchanging elements 20 , fresh gas outtake 36 of the heat exchanger assembly 3 , fresh air transition channel 91 of the transition 89 , fresh gas inlet 15 , cross flow blower 50 in fresh gas canal 13 , and fresh gas outlet 17 , fresh gas outlet duct 55 A of air module assembly 2 , thus providing countercurrent heat exchange process.
  • the air module assembly 2 is connected to the heat exchanger assembly 3 which is L-shaped.
  • the exhaust gas flows through the exhaust gas inlet duct 54 A, exhaust gas inlet 14 , crossflow blower 49 in the exhaust gas canal 12 of the air module assembly 2 , the exhaust gas outlet 16 , exhaust gas intake 31 through heat exchanging elements 20 and exhaust gas outtake 34 of the L shaped heat exchanger assembly 3 , while fresh gas flows through the fresh gas intake 32 through heat exchanging elements 20 , fresh gas outtake 36 of the L-shaped heat exchanger assembly 3 , fresh gas inlet 15 , cross flow blower 50 in fresh gas canal 13 , and fresh gas outlet 17 , fresh gas outlet duct 55 A of air module assembly 2 , thus providing countercurrent heat exchange process.
  • the air module assembly 2 is connected to the heat exchanger assembly 3 with transition duct assembly 94 .
  • the exhaust gas flows through the exhaust gas inlet duct 54 A, exhaust gas inlet 14 , crossflow blower 49 in the exhaust gas canal 12 of the air module assembly 2 , the exhaust gas outlet 16 , exhaust gas transition duct 95 , exhaust gas intake 31 through heat exchanging elements 20 and exhaust gas outtake 34 of heat exchanger assembly 3 , while fresh gas flows through the fresh gas intake 32 through heat exchanging elements 20 , fresh gas outtake 36 of the heat exchanger assembly 3 , fresh gas transition duct 96 , fresh gas inlet 15 , cross flow blower 50 in fresh gas canal 13 , and fresh gas outlet 17 , fresh gas outlet duct 55 A of air module assembly 2 , thus providing countercurrent heat exchange process.
  • the compact heat recovery ventilation system 1 operates in the following way.
  • an electric power is supplied to the flat stator 68 of the electric drive 45 .
  • This electromagnetic field is controlled by the electronic controllers (not shown on Figs.) and interacts with a magnetic field created by the magnetic rotor 63 .
  • the magnetized rotor 63 causes the double radial impeller 57 to rotate.
  • the exhaust gas flows through the exhaust gas inlet duct 54 A, crossflow blower 49 in the exhaust gas canal 12 of the air module assembly 2 , the exhaust gas outlet 53 A, exhaust gas intake 31 through heat exchanging elements 20 and exhaust gas outtake 34 of heat exchanger assembly 3 and exhaust gas outtake duct 54 , while fresh gas flows through the fresh gas intake duct 55 , fresh gas intake 32 through heat exchanging elements 20 , fresh gas outtake 36 of the heat exchanger assembly 3 , flexible fresh air transition channel 91 of the transition 89 , fresh gas inlet 15 , cross flow blower 50 in fresh gas canal 13 , and fresh gas outlet 17 , fresh gas outlet duct 55 A of air module assembly 2 , thus providing countercurrent heat exchange process.
  • the compact heat recovery ventilation system 1 due to the mutual arrangement of the hydraulic schemes of the crossflow blowers 42 with the double side radial impeller 75 parallel to the base plate 4 of the air module assembly 2 , provides a thin, compact, highly efficient, simple, reliable and less expensive device that can easily be mounted inside the wall, ceiling or inside a vehicle.

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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)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
US16/089,431 2016-03-31 2017-03-29 A compact heat recovery ventilation system Abandoned US20200300498A1 (en)

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US201662316325P 2016-03-31 2016-03-31
PCT/US2017/024865 WO2017173001A1 (en) 2016-03-31 2017-03-29 A compact heat recovery ventilation system
US16/089,431 US20200300498A1 (en) 2016-03-31 2017-03-29 A compact heat recovery ventilation system

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US11536290B2 (en) * 2020-04-08 2022-12-27 Carrier Corporation Fan coil unit and air conditioning system
WO2023275742A1 (en) * 2021-06-29 2023-01-05 3J Marine S.R.L. Vessel provided with an improved air circulation system
WO2023075590A1 (en) * 2021-10-29 2023-05-04 Citech Energy Recovery System Malaysia Sdn Bhd Flow diverter
EP4187169A1 (en) * 2021-11-26 2023-05-31 Alteko, s.r.o. Air transfer and treatment device
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WO2023075590A1 (en) * 2021-10-29 2023-05-04 Citech Energy Recovery System Malaysia Sdn Bhd Flow diverter
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GB2638443A (en) * 2024-02-22 2025-08-27 Passihvac Ltd Ventilation apparatus

Also Published As

Publication number Publication date
EP3436747A1 (en) 2019-02-06
CN109477657A (zh) 2019-03-15
JP2019516061A (ja) 2019-06-13
WO2017173001A1 (en) 2017-10-05
EP3436747A4 (en) 2019-11-20
KR20190003541A (ko) 2019-01-09

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