WO2001016530A2 - Heat exchanger type fan - Google Patents
Heat exchanger type fan Download PDFInfo
- Publication number
- WO2001016530A2 WO2001016530A2 PCT/US2000/023900 US0023900W WO0116530A2 WO 2001016530 A2 WO2001016530 A2 WO 2001016530A2 US 0023900 W US0023900 W US 0023900W WO 0116530 A2 WO0116530 A2 WO 0116530A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- impeller
- fan
- blades
- heat exchanger
- exchanger type
- Prior art date
Links
- 239000007787 solid Substances 0.000 claims description 20
- 230000002093 peripheral effect Effects 0.000 claims description 5
- 239000000969 carrier Substances 0.000 abstract description 28
- 238000000034 method Methods 0.000 abstract description 10
- 238000004378 air conditioning Methods 0.000 abstract description 4
- 238000009423 ventilation Methods 0.000 abstract description 4
- 238000005192 partition Methods 0.000 description 15
- 238000004519 manufacturing process Methods 0.000 description 13
- 230000001419 dependent effect Effects 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 238000003801 milling Methods 0.000 description 3
- 238000009434 installation Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
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
- F24F7/00—Ventilation
- F24F7/007—Ventilation with forced flow
-
- 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
-
- 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
- F04D25/166—Combinations of two or more pumps ; Producing two or more separate gas flows using fans
-
- 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
- F04D29/424—Double entry casings
-
- 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
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
- F04D29/5853—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps heat insulation or conduction
-
- 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
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- 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
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
- F28F13/125—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation by stirring
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- 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 claimed invention belongs to heat exchange devices where the heat carriers do not mix, and may be used, for instance, in ventilation and air conditioning systems for heat exchange between the intake and the exhaust air streams.
- a heat exchanger type fan is known, described in a Japanese application 60- 75634, (Int. Cl. F 28 D 9/00, Filed 10.04.85, Publ. Date 06.07.94), 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. Two channels for heat carriers (air streams) of different temperature are formed in the casing, separated by a heat exchange element made as a corrugated radial partition installed beyond the edges of the impellers of the fans and equipped with a disk to separate the fans.
- a heat exchanger type fan is known, described in a Japanese application 60- 75635 (Int. Cl. F 28 D 9/00, Filed 10.04.85, Publ. date 06.07.94), 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. Two channels for heat carriers of different temperature are formed in the casing, separated by a partition separating also both fans.
- the heat exchange element is made as radial fins mounted on both surfaces of the partition beyond the edges of the impellers of the fans.
- the closest to the claimed invention is the heat exchanger type fan described in the Japanese application 61-86463 (Int. Cl. F 28 D 11/02, Filed 15.04.86, Publ. date 01.06.94), consisting of a casing and an impeller of a double-sided centrifugal fan made as a radially corrugated disk with an outer rim, the faces of the corrugation performing the function of radial blades.
- the former is explained by the fact that it is the radially corrugated surface that performs the function of the blades.
- the air stream outgoing from the impeller of the fan has a surplus pressure exceeding that necessary pressure to overcome the total hydraulic resistance of the fan. This will require more power to be supplied.
- blades of a different shape are required, namely backward-curved blades. It is obvious that manufacturing a corrugated disk with bent blades presents a rather difficult engineering problem. The curvature of such corrugation will be determined by the permissible plastic deformation of the material the impeller is made of.
- the low heat exchange efficiency of the known device is explained by the following.
- the heat exchange efficiency is to a certain extent influenced by both the area of the heat exchange surface and the rate at which the heat carrier passes over it.
- the area of heat exchange will be at its minimum, since the radial blades are of minimum length, and, secondly, the rate at which the heat carrier passes over that area will decrease towards the periphery of the impeller, which is caused, taking into account the continuity of the air stream, by the fact that the cross-section area of the interblade space increases towards its periphery.
- the area of heat exchange is comparatively large, its efficiency is not going to be high.
- the engineering problem at the solution whereof the claimed invention is aimed is to increase the efficiency of heat exchange and to lower the power consumption.
- Three embodiments of the solution for the stated problem are claimed.
- the essence of the claimed invention according to the first embodiment consists in that in a heat exchanger type fan comprising a casing and an impeller of a double-sided centrifugal fan mounted in it, the casing being divided into two isolated chambers which, together with the impeller, form two isolated centrifugal fans, in accordance with the invention the impeller is made as a solid dividing disk on both sides whereof blades are made normal to its plane, said blades being bent backwards (backward-curved).
- impeller blades may be made with a constant width of the interblade channel to provide for the uniform rate of the heat carrier flow in the interblade channel and, accordingly, to raise the efficiency of heat exchange.
- the fans may have a front disk attached to the blades, with an axial passage to let the heat carrier through into the interblade space.
- the front disk encloses the interblade space, thus reducing the fan losses and increasing the efficiency of heat exchange.
- blower outlets of both fans may be made axisymmetric and turned in the axial direction towards the side opposite to the respective suction inlet. Such arrangement will ensure that the heat carriers pass from the one to the opposite side of the device. This will considerably facilitate the installation of the claimed heat exchanger type fan in the systems of ventilation and air conditioning, corresponding to the direction of the input and the exhaust airflows.
- the essence of the claimed invention according to the second embodiment consists in that in a heat exchanger type fan comprising a casing and a two-sided impeller mounted in it, on one side whereof the blades of a centrifugal fan are arranged, the casing being divided into two isolated chambers which, together with the impeller, form two isolated sections, one of which being a centrifugal fan, in accordance with the invention the impeller is made as a dividing disk, the above-mentioned blades of the centrifugal fan being arranged on one side of the dividing disk, while on its other side the blades of a centripetal fan are made, in the aggregate forming the above-mentioned two- sided impeller, one side whereof serving as the impeller of said centrifugal fan, and the other one - as that of the centripetal fan.
- the blades should be made bent backwards (backward-curved).
- the blades of the fans with the ratio of their length to the distance between the blades over the mid-radius being no less than 10.
- intermediate blades may be installed over the periphery of the dividing disk
- the impeller blades may be made with a constant width of the interblade channel to provide for the uniform rate of the heat carrier flow in the interblade channel and, accordingly, to raise the efficiency of heat exchange.
- the impeller of the centrifugal fan may have a solid front disk (impeller shroud) attached to the blades, and the dividing disk may have an axial passage, around which the outlet of the centripetal fan can be made, connected to the interblade space of the centrifugal fan impeller.
- the above-mentioned outlet of the centripetal fan shall be located inside the suction inlet of the centrifugal fan.
- the impeller of the centrifugal fan may have a front disk (impeller shroud) attached to the blades, with an axial passage to let the drawn-in heat carrier into the interblade space of the centrifugal fan.
- the front disk (impeller shroud) encloses the interblade space, thus reducing the fan losses and increasing the efficiency of heat exchange.
- an inlet may be arranged around the axial passage of the impeller front disk (impeller shroud) of the centrifugal fan, said inlet being connected to the interblade space of the centrifugal fan impeller; at that this inlet should be installed inside the suction inlet of the centrifugal fan with a minimum gap allowed, said gap to be selected so that during rotation of the centrifugal fan the outside surface of the above-mentioned inlet would not come into contact with the suction inlet.
- the impeller of the centripetal fan may have a solid front disk attached to the blades, and the dividing disk may have an axial passage, around which the outlet of the centripetal fan can be arranged, connected to the interblade space of the centripetal fan impeller, the above-mentioned outlet of the centripetal fan located inside the inlet of the centrifugal fan. As shown above, such configuration ensures that the heat carriers pass from the one to the opposite side of the device.
- the essence of the claimed invention according to the third embodiment consists in that in a heat exchanger type fan comprising a casing and a two-sided impeller mounted in it, on one side whereof the blades of a centrifugal fan are arranged, the casing being divided into two isolated chambers which, together with the impeller, form two isolated sections, one of which being a centrifugal fan, in accordance with the invention the impeller is made as a dividing disk, the above-mentioned blades of the centrifugal fan being arranged on one side of the dividing disk, while on its other side turbine blades are arranged, in the aggregate forming the impeller, one side whereof serving as the impeller of the above-mentioned centrifugal fan, and the other one - as that of the centripetal turbine.
- a blower may be additionally installed in the inlet of the turbine.
- the inlet of the turbine is made as a ring-shaped orifice coaxial to the impeller, and the blower is made as an axial fan whose blades overlap the above-mentioned ring-shaped orifice of the turbine inlet.
- the inlet of the turbine is made as an orifice in its peripheral part, and the blower is made as a centrifugal fan installed in this orifice.
- the respective blades should be made bent backwards (backward-curved).
- the blades of the centrifugal fan and/or blades of the centripetal turbine shall be manufactured with the ratio of their length to the distance between the blades over the mid-radius being no less than 10.
- intermediate vanes may be installed over the periphery of the dividing disk
- the blades of the centrifugal fan and/or blades of the turbine may be made with a constant width of the interblade channel to provide for the uniform rate of the heat carrier flow in the interblade channel and to raise, accordingly, the efficiency of heat exchange.
- the impeller of the turbine may have a solid front disk attached to the blades, and the dividing disk may have an axial passage, around which the outlet of the turbine can be arranged, connected to the interblade space of the turbine impeller.
- the above- mentioned outlet of the turbine shall be located inside the suction inlet of the centrifugal fan.
- the impeller of the centrifugal fan may have a front disk (impeller shroud) attached to the blades, with an axial passage to let the drawn-in heat carrier into the interblade space of the centrifugal fan.
- an inlet can be arranged around the axial passage of the impeller front disk (impeller shroud) of the centrifugal fan, said inlet being connected to the interblade space of the centrifugal fan impeller, at that this inlet should be installed inside the suction inlet of the centrifugal fan with a minimum gap allowed.
- the impeller of the turbine may also have a solid front disk (impeller shroud) attached to the blades, and the dividing disk may have an axial passage, around which the outlet of the turbine can be arranged, connected to the interblade space of the turbine impeller, the above-mentioned outlet of the turbine located inside the inlet of the centrifugal fan.
- a solid front disk impeller shroud
- the dividing disk may have an axial passage, around which the outlet of the turbine can be arranged, connected to the interblade space of the turbine impeller, the above-mentioned outlet of the turbine located inside the inlet of the centrifugal fan.
- centripetal turbine permits, in the latter configuration of the inlet and the outlet of the centrifugal fan, as well as of the inlet and the outlet of the turbine, to implement a two-stage heat exchange pattern.
- the described device will serve as the first stage, complemented with the second identical stage, both stages being installed coaxially and with the front disks of the turbines towards each other, while the blower outlets of the centrifugal fans of one stage are connected to the inlets of the turbines of the other stage.
- the suction inlet of the first stage and the outlet of the second stage will respectively serve as the inlet and the outlet for one heat carrier, while the suction inlet of the second stage and the outlet of the first stage will respectively serve as the inlet and the outlet for the other heat carrier.
- the centrifugal fan of one of those (of one stage) will deliver the stream of one of the heat carriers to the turbine of the other device.
- the transfer of the other heat carrier will proceed in the opposite direction. Heat exchange between the heat carriers will take place as stated above - according to the counter-flow pattern.
- Fig. 1 - heat exchanger type fan (according to the first design embodiment) with a unidirectional, symmetrical arrangement of blower outlets;
- FIG. 2 - the same as in Fig. 1 (side view by cross section 2);
- Fig. 3 heat exchanger type fan (according to the first design embodiment) with a different-direction, axisymmetric arrangement of blower outlets;
- Fig. 5 heat exchanger type fan (according to the first design embodiment) with a different-direction, axisymmetric arrangement of blower outlets turned in the axial direction to the opposite side in relation to the corresponding suction inlets;
- Fig. 6 the same as in Fig. 5 (side view by cross section 6);
- Fig. 7 an example of impeller blades with an interblade channel of constant width
- FIG. 8 an illustration of relationships for calculating blade profile for the case when an interblade channel is of constant width
- Fig. 9 heat exchanger type fan (according to the second design embodiment) with suction inlets and blower outlets of both centrifugal and centripetal fans being located on one side;
- FIG. 10 the same as in Fig. 9 (side view from the left by cross section 10);
- Fig. 11 the same as in Fig. 9 (side view from the right by cross section 11);
- Fig. 12 blade of a centripetal fan
- Fig. 13 heat exchanger type fan (according to the second design embodiment) with suction inlets of both centrifugal and centripetal fans being located opposite the blower outlets of both centrifugal and centripetal fans;
- Fig. 14 the same as in Fig. 13 (side view from the left by cross section 14);
- Fig. 15 the same as in Fig. 13 (side view from the right by cross section 15);
- Fig. 16 - heat exchanger type fan (according to the third design embodiment) with an axial fan used as a blower and installed in the inlet of the turbine;
- Fig. 17 the same as in Fig. 16 (side view from the right by cross section 17);
- Fig. 18 the same as in Fig. 16 (side view from the right);
- Fig. 19 heat exchanger type fan (according to the third design embodiment) with a centrifugal fan used as a blower and installed in the inlet of the turbine;
- FIG. 20 the same as in Fig. 19 (side view from the left by cross section 20);
- Fig. 21 the same as in Fig. 19 (side view from the right by cross section 21);
- Fig. 22 double-stage heat exchanger type fan (according to the third design embodiment) with separate impellers;
- Fig. 25 the same as in Fig. 22 (side view by cross section 25);
- Fig. 26 double-stage heat exchanger type fan (according to the third design embodiment) with a combined solid disk for the turbines of both stages;
- the first design embodiment of the heat exchanger type fan applied herein (Figs. 1-6) consists of a casing 101 of spiral shape having axial inlets 102 and 103 on the opposite face and end sides and corresponding tangentially located blower outlets 104 and 105.
- An impeller consisting of a dividing disk 107 with blades 108 and 109 (normally fixed to both surfaces of said disk) that are bent backwards (backward-curved) in relation to rotation direction is installed on shaft 106 in casing 101.
- the inner space of casing 101 is separated by partition 110 into two internal spaces (chambers) 111 and 112 serving as the volutes for two centrifugal fans.
- the central part of partition 110 is adjacent to the outer edge of disk 107 (via a labyrinth seal 113 made, for example, out of rubber or felt).
- the arrows in Fig. 1 through Fig. 6 show the direction of airflows that serve as heat carriers.
- Figs. 1-2 present an example of an embodiment of a heat exchanger type fan with a unidirectional, symmetrical arrangement of blower outlets 104 and 105
- Figs. 3-4 demonstrate an example of an embodiment of a heat exchanger type fan with a differently-directed axisymmetric arrangement of blower outlets 104 and 105.
- FIGs. 5-6 represents the preferred embodiment of a heat exchanger type fan.
- an impeller has impeller shrouds 114 and 115 on its each side, and said impeller shrouds have axial passages intended for the flow of the drawn-in air into the interblade space.
- Impeller shrouds 114 and 115 have inlet shrouds 116 and 117, respectively, in the area of said axial passages.
- Inlet shrouds 116 and 117 are placed in the corresponding axial inlets 102 and 103 with a minimally admissible gap.
- Intermediate blades 118 are installed on the both sides of dividing disk 107 - over its periphery (Fig. 6 shows said intermediate blades only on one side of disk 107).
- blower outlets 104 and 105 constitutes the distinguishing feature of this design. Said blower outlets are placed axisymmetrically in such a manner that they are directed in different directions and turned in the axial direction to the opposite side in relation to the corresponding axial inlets 102 and 103.
- Fig. 7 presents an example of design of blades 108 (or 109) of the centrifugal fan with an interblade channel of constant width.
- Fig. 8 shows two adjacent blades (arc AB and arc CD) and corresponding geometric constructions for designing the said blade profile.
- point E of arc AB located at a distance r from the center O of the impeller and for point F of arc CD corresponding to said point E (the distance between point E and point F - t(r) is the width of the interblade channel)
- point G of arc CD that is also located at a distance r from the center O of the impeller.
- Distance a(r) between points E and G for a great number of blades Z is approximately equal to the length of arc EG - in other words, a(r) « 2 ⁇ r/Z. Under these conditions the value of t(r) could be defined as t(r) « a(r)-sin ⁇ (r).
- Milling of a disk represents one of the ways for making blades of the indicated profile.
- a milling cutter of diameter T should be used, while the calculated values ⁇ (r) should be used by the program control unit of a milling machine.
- the first embodiment of the device applied herein operates in the following manner.
- shaft 106 rotates (together with the impeller fixed on it) the air streams (i.e. heat carriers) of different temperature pass from both sides through axial inlets 102 and 103 and then get into the space between blades 108 and 109, respectively.
- air streams i.e. heat carriers
- air streams flow by interblade space to the outer surface of the impeller and then get to the corresponding snail-like internal spaces (chambers) 111 and 112. Then they get expelled from casing 101 through blower outlets 104 and 105.
- a process of direct-flow heat exchange between them takes place.
- the second embodiment of the heat exchanger type fan applied herein comprises a casing 201 divided by partition 202 into two chambers - one of them serves as section 203 of the centrifugal fan, while another serves as section 204 of the centripetal fan.
- Casing 201 has suction inlet 205 and blower outlet 206 of the centrifugal fan plus suction inlet 207 and blower outlet 208 of the centripetal fan intended to let the pass-through of heat carriers of different temperature (the directions of air stream motion are shown by arrows).
- An impeller consisting of dividing disk 210 with centrifugal fan blades 211 and centripetal fan blades 212 that are normally fixed to the dividing disk 210 and that are bent backwards (backward-curved) in relation to the rotation direction is installed on shaft 209 in casing 201.
- centripetal fan blades 212 are turned transversely to the rotation direction thus forming blower blades 213 (see Fig. 12) that provide for the suction of heat carrier through inlet 207 of the centripetal fan.
- both fans i.e.
- centrifugal fan and centripetal fan could be additionally equipped with intermediate blades installed in the peripheral part of dividing disk 210 between blades 211 and 212, respectively.
- Intermediate blades 214 of the centrifugal fan are shown as an example in Fig. 10.
- the central part of partition 202 is adjacent to the outer edge of dividing disk 210 (only labyrinth seal 215 made, for example, out of rubber of felt separates them), owing to which fact section 203 of the centrifugal fan and section 204 of the centripetal fan are sealed off from one another.
- Figs. 9-11 present a design embodiment of a heat exchanger type fan with centrifugal fan inlet 205 and outlet 206 and centripetal fan inlet 207 and outlet 208 being located on one side
- Figs. 13-15 present a design embodiment of a heat exchanger type fan with the above-indicated inlets/outlets being placed on different sides of the device.
- blower outlet 206 of the centrifugal fan is turned in the axial direction so that it facing away from suction inlet 205.
- the device comprises (see Fig. 13) impeller shroud 216 fastened together with blades 211 of the centrifugal fan.
- Impeller shroud 216 has passage 217 intended to let the pass-through of heat carrier being drawn-in into the interblade space of the centrifugal fan.
- Inlet 218 (that is connected to the interblade space of the centrifugal fan and that is placed in suction inlet 205 with a minimal gap between them) is located around passage 217 of impeller shroud 216.
- Solid impeller shroud 219 is attached to blades 212 of the centrifugal fan, while dividing disk 210 has axial passage 220, around which outlet 221 of the centripetal fan is made in such a manner that it is connected to the interblade space of this fan.
- outlet 221 is placed inside centrifugal fan inlet 218.
- Blades 211 of the centrifugal fan can be made in such a way that the width of the interblade channel is constant (as shown in Fig. 7).
- the second embodiment of the device applied herein operates in the following manner.
- the air streams i.e. heat carriers
- the air stream flows by interblade space to the periphery of the impeller, then gets into the spiral chamber of the centrifugal section 203, and then it gets expelled out of casing 201 through blower outlet 206.
- the centripetal fan another air stream flows by interblade space to the center of the impeller and then is removed from casing 201 through outlet 208.
- the heat exchange process in the device presented in Figs. 13-15 proceeds in the same manner.
- This device design differs from that presented in Figs. 9-11 only by the flow of air streams downstream of the impeller.
- the air stream from the centrifugal fan passes through blower outlet 206 turned in the axial direction to the opposite side (in relation to suction inlet 205), while the air stream from the centripetal fan passes through axial passage 220 of dividing disk 210 and then gets into centripetal fan outlet 221 oriented in the axial direction to the opposite side in relation to inlet 207 of this fan.
- the third embodiment of the single-stage heat exchanger type fan applied herein see Figs.
- casing 301 comprises a casing 301 separated by partition 302 into two chambers - one of them serves as section 303 of the centrifugal fan, while another serves as section 322 of the turbine.
- Casing 301 has suction inlet 305 and outlet shroud 306 of the centrifugal fan plus inlet 323 and outlet 324 of the turbine intended to let the pass- through of heat carriers of different temperature (the directions of air stream motion are shown by arrows).
- Turbine's inlet 323 is made in the form of an annular opening in casing 301.
- an impeller consisting of dividing disk 310 with centrifugal fan blades 311 and turbine blades 325 that are normally fixed to the dividing disk 310 and that are bent backwards (backward-curved) in relation to the rotation direction is installed in casing 301.
- the central part of partition 302 is adjacent to the outer edge of dividing disk 310 (only labyrinth seal 315 made, for example, out of rubber of felt separates them), owing to which fact section 303 of the centrifugal fan and section 322 of the turbine are sealed off from one another.
- the device comprises impeller shroud 316 fastened together with blades 311 of the centrifugal fan.
- Impeller shroud 316 has passage 317 intended to let the pass-through of heat carrier being drawn-in into the interblade space of the centrifugal fan.
- Inlet 318 (that is connected to the interblade space of the centrifugal fan and that is placed in centrifugal fan suction inlet 205 with a minimal gap) is located around passage 317 of impeller shroud 316.
- Solid impeller shroud 326 is attached to turbine blades 325, while dividing disk 310 has axial passage 320, around which the above-mentioned outlet 324 of the turbine is made in such a manner that it is connected to the interblade space of this turbine.
- outlet 324 is placed inside inlet 318 of the centrifugal fan.
- the impeller is installed on shaft 309 in casing 301 through the use of turbine's impeller shroud 326.
- the device also comprises a blower (an axial fan 327 serves as such), the blades
- Axial fan 327 can be installed on shaft 309 (as shown in Fig. 17) or it can be installed on a separate rotation shaft (that is not connected with shaft 309 and that is driven by a separate drive). In the latter case the drive of axial fan 327 may also serve as the drive for the entire device - this is so because the turbine will provide for the rotation of impeller and, hence, the operation of centrifugal section 303.
- turbine inlet 329 in this design is made in the form of an opening in its peripheral part, while centrifugal fan 330 installed just opposite this opening serves as the blower.
- the third embodiment of the device applied herein operates in the following manner.
- the impeller is set in motion by a drive connected to shaft 309 plus due to one of the air streams (heat carriers) forced into turbine section 322 by axial fan 327 (Figs. 16-18) or centrifugal fan 330 (Figs. 19-21). Given sufficient pressure, the impeller can rotate only due to stream forced into turbine section 322. Air streams having different temperature are fed from both sides through inlets 305 and 323, and then they get into the space between blades 311 and 325, respectively.
- the air stream flows by interblade space to the periphery of the impeller, then gets into the spiral chamber of the centrifugal section 303, and then it gets expelled out of casing 301 through outlet shroud 306.
- another air stream flows by interblade space to the center of the impeller, then through axial passage 320 of dividing disk 310 it gets to outlet 321, via which it is removed from casing 301.
- a process of counter-flow heat exchange between them (through blades 311, 325 and dividing disk 310) takes place.
- the third embodiment of a double-stage heat exchanger type fan applied herein (see Figs. 22-25 and 26-29) consists of two identical stages - the first stage 331 and second stage 332, each of which comprises section 333 and section 334 of the centrifugal fan plus section 335 and section 336 of the turbine, respectively. Both stages (i.e. stage 331 and stage 332) are made in the same manner as a single-stage heat exchanger type fan presented in Figs. 16-18 and Figs. 19-21. Stages 331 and 332 are oriented towards one another and installed on one and the same shaft 309 that is set in rotation by an external drive (this drive is not shown in Figs. 22-25 and Figs. 26-29).
- Partition 337 separates stage 331 from stage 332.
- Blower outlet 338 of section 333 of the centrifugal fan of the first stage 331 is connected to inlet 339 of turbine section 336 of the second stage 332, while blower outlet 340 of section 334 of the centrifugal fan of the second stage 332 is connected to inlet 341 of turbine section 335 of the first stage 331.
- Suction inlet 342 of the first stage 331 and outlet 343 of the second stage 332 serve as an inlet and outlet, respectively, for one heat carrier, while suction inlet 344 of the second stage 332 and outlet 345 of the first stage 331 respectively serve as an inlet and outlet for another heat carrier.
- a double-stage heat exchanger type fan design presented in Figs. 26-29 represents the preferred third embodiment of the present invention. Unlike the example presented in Figs. 22-25, the impeller shrouds of turbine sections 335 and 336 of both stages (i.e. stage 331 and stage 332) in this design are made in the form of a combined solid disk 346.
- the third embodiment of a double-stage heat exchanger type fan (see Figs. 22-25 and 26-29) operates in the following manner.
- the air streams i.e. heat carriers
- the air streams are drawn-in through suction inlets 342 and 344 by centrifugal fans of sections 333 and 334, respectively.
- the air streams get into turbine sections 334 and 335, respectively. Then they are forced out from the device through the respective outlets 343 and 345.
- each air stream passes through both stages - stage 331 and stage 332.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU74722/00A AU7472200A (en) | 1999-09-02 | 2000-08-31 | Heat exchanger type fan |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
RU99119164 | 1999-09-02 | ||
RU99119121/06A RU2224914C2 (en) | 1999-09-02 | 1999-09-02 | Fan-heat exchanger (modifications) |
RU99119121 | 1999-09-02 | ||
RU99119164/06A RU2224913C2 (en) | 1999-09-02 | 1999-09-02 | Fan-heat exchanger |
Related Child Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09830844 A-371-Of-International | 2001-05-01 | ||
US10/195,576 Continuation US6695038B2 (en) | 1999-09-02 | 2002-07-15 | Heat exchanger type fan |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2001016530A2 true WO2001016530A2 (en) | 2001-03-08 |
WO2001016530A3 WO2001016530A3 (en) | 2001-09-07 |
Family
ID=26654020
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US2000/023900 WO2001016530A2 (en) | 1999-09-02 | 2000-08-31 | Heat exchanger type fan |
Country Status (2)
Country | Link |
---|---|
AU (1) | AU7472200A (en) |
WO (1) | WO2001016530A2 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2002097338A2 (en) * | 2001-05-31 | 2002-12-05 | Venmar Ventilation Inc. | Ventilation method and device |
WO2003023289A2 (en) * | 2001-09-07 | 2003-03-20 | Advanced Rotary Systems, Llc | Integrated cooler for electronic devices |
CN103277326A (en) * | 2013-06-04 | 2013-09-04 | 上海布威重工机械有限公司 | Multi-vane fan |
CN112682338A (en) * | 2020-12-24 | 2021-04-20 | 北京理工大学 | Air compressor for fuel cell system |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4102597A (en) * | 1976-03-31 | 1978-07-25 | Teizo Sakai | Ventilating suction and exhaust fan device of plate type |
-
2000
- 2000-08-31 AU AU74722/00A patent/AU7472200A/en not_active Abandoned
- 2000-08-31 WO PCT/US2000/023900 patent/WO2001016530A2/en active Application Filing
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4102597A (en) * | 1976-03-31 | 1978-07-25 | Teizo Sakai | Ventilating suction and exhaust fan device of plate type |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2002097338A2 (en) * | 2001-05-31 | 2002-12-05 | Venmar Ventilation Inc. | Ventilation method and device |
WO2002097338A3 (en) * | 2001-05-31 | 2003-04-10 | Venmar Ventilation Inc | Ventilation method and device |
US6855050B2 (en) | 2001-05-31 | 2005-02-15 | Venmar Ventilation Inc. | Ventilation method and device |
WO2003023289A2 (en) * | 2001-09-07 | 2003-03-20 | Advanced Rotary Systems, Llc | Integrated cooler for electronic devices |
WO2003023289A3 (en) * | 2001-09-07 | 2003-05-22 | Advanced Rotary Systems Llc | Integrated cooler for electronic devices |
US7071587B2 (en) | 2001-09-07 | 2006-07-04 | Rotys Inc. | Integrated cooler for electronic devices |
CN103277326A (en) * | 2013-06-04 | 2013-09-04 | 上海布威重工机械有限公司 | Multi-vane fan |
CN112682338A (en) * | 2020-12-24 | 2021-04-20 | 北京理工大学 | Air compressor for fuel cell system |
Also Published As
Publication number | Publication date |
---|---|
WO2001016530A3 (en) | 2001-09-07 |
AU7472200A (en) | 2001-03-26 |
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