US3835921A - Rotatable heat exchanger - Google Patents

Rotatable heat exchanger Download PDF

Info

Publication number
US3835921A
US3835921A US00328686A US32868673A US3835921A US 3835921 A US3835921 A US 3835921A US 00328686 A US00328686 A US 00328686A US 32868673 A US32868673 A US 32868673A US 3835921 A US3835921 A US 3835921A
Authority
US
United States
Prior art keywords
fluid
passages
blades
collection
peripheral
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.)
Expired - Lifetime
Application number
US00328686A
Other languages
English (en)
Inventor
G Faris
Champs N Des
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
DONBAR DEV CORP
Original Assignee
DONBAR DEV CORP
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by DONBAR DEV CORP filed Critical DONBAR DEV CORP
Priority to US00328686A priority Critical patent/US3835921A/en
Priority to DE2404488A priority patent/DE2404488A1/de
Priority to FR7403376A priority patent/FR2216536B3/fr
Priority to JP49013569A priority patent/JPS5047242A/ja
Application granted granted Critical
Publication of US3835921A publication Critical patent/US3835921A/en
Anticipated expiration legal-status Critical
Assigned to WHITEHALL BUSINESS CREDIT CORPORATION reassignment WHITEHALL BUSINESS CREDIT CORPORATION SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DES CHAMPS LABORATORIES INCORPORATED
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F5/00—Elements specially adapted for movement
    • F28F5/04—Hollow impellers, e.g. stirring vane
    • 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
    • F28D11/00—Heat-exchange apparatus employing moving conduits
    • F28D11/02—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller
    • 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
    • F28D11/00—Heat-exchange apparatus employing moving conduits
    • F28D11/02—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller
    • F28D11/04—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller performed by a tube or a bundle of tubes
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/135—Movable heat exchanger
    • Y10S165/139—Fully rotatable
    • Y10S165/147—Fluid impeller or material advancer
    • Y10S165/15—Radial or axial impeller
    • Y10S165/151—Radial or axial impeller having hollow blade

Definitions

  • Passages are formed in the rotatable member which receive the preheated or precooled thermal fluid from external equipment and distribute such fluid to the hollow blades within which the fluid circulates causing heat transfer to ambient fluid.
  • the thermal fluid is then directed to collection passages in the rotatable member from which the fluid exits and returns to the external equipment.
  • the distribution and collection passages are formed to obtain a reduced pressure drop and a compact device.
  • a stator is provided enabling the heat exchanger to function as a pump for circulating the thermal fluid.
  • This invention relates to heat exchangers and, more particularly, to heat exchangers of the rotary type.
  • Rotary heat exchangers have advantages due to their relatively high heat transfer efficiency and relatively compact design, in addition to the substantial decrease in the noise output of these devices relative to the conventional stationary heat exchangers equipped with air circulating fans. Further, the power requirements to operate such rotary heat exchangers are substantially smaller than the power required to run conventional heat exchangers.
  • the use of the conventional rotating fan-stationary radiator combination in automobiles has been handicapped by a variety of factors, e.g., noise becomes intolerable at air velocities needed for high efficiency operation; efficiency is reduced due to the requirement of clearance space for the fans resulting in the impracticality of optimum air flow over the entire heat exchanger surface; power in amounts needed to drive the fan often detracts from performance; and the necessity of placement of the radiators in the airstream imposes a severe design limitation under the automobile hood.
  • the low noise, high efficiency and compact design characteristics of rotary heat exchangers provide a feasible solution to these problems.
  • rotary heat exchangers A variety of designs of rotary heat exchangers have been proposed. Essentially, most rotary heat exchangers include a rotor formed by a plurality of hollow blades annularly mounted on side plates. As the rotor rotates, ambient air is caused to pass over the outer surface of the blades while thermal fluid (refrigerant or heated fluid) is directed to and passes through the blade interiors thereby effecting heat transfer between the thermal and ambient fluids.
  • thermal fluid refrigerant or heated fluid
  • rotary heat exchangers provide the advantages set forth hereinabove, in the past several problems have decreased their effectiveness. For example, relatively substantial energy losses occur during the flow of the thermal fluid through the exchanger passages. These flow losses not only result in increased pressure drop within the apparatus but also increase the power requirements to circulate the fluid through the system.
  • the designs of both the interiors and exteriors of the thermal transfer blades have not optimized their heat transfer properties.
  • the relatively complex fluid circulation systems of rotary heat exchangers often have required the use of bulky fluid transport apparatus which have naturally reduced the exchangers compactness.
  • a rotary heat exchanger incorporating improvements of the nature described above is not available wherein the exchanger has the capacity to pump the thermal fluid through the circulation system, thus dispensing with the need for an external pump.
  • an object of this invention is to provide a new and improved rotary heat exchanger.
  • Another object of the invention is the provision of a new and improved fluid distribution and collection element for use in rotary heat exchangers which will reduce pressure drop and energy requirements.
  • a further object is to provide more efficient thermal transfer blades for use in rotary heat exchangers.
  • a still further object is to provide a new and improved compact rotary heat exchanger.
  • Yet another object is to provide a heat exchanger satisfying all of the above objects which also provides pumping action for the thermal fluid circulating therein.
  • an end plate in a rotary heat exchanger having passages which transmit the thermal fluid from external equipment to the blade interiors having a compact configuration wherein the energy necessary to move the fluid from the entrance of the exchanger to the blades is minimal relative to prior art apparatus.
  • the configuration of the passages results in the force due to the rotation of the end plate having a minimum effect on the flow of the thermal fluid.
  • the thermal transfer blades are formed with a plurality of parallel fluid circulation passages extending longitudinally within each blade and with a maximum number of integral heat transfer fins.
  • FIG. 1 is a side view partly in section of the rotary heat exchanger of the present invention
  • FIG. 2 is a front view of the rotary heat exchanger partially broken away.
  • FIG. 3 is a side view in cross section of another embodiment of a rotary heat exchanger.
  • the rotary heat exchanger includes a rotor assembly 12 having a fluid inlet passage 14 and a plurality of outlet openings 16 for transporting thermal fluid to and from the rotor assembly respectively from and to external equipment.
  • the fluid inlet may be coupled to the water line of an automobile engine to receive the coolant in its heated state while the outlets 16 return the coolant subsequent to the dissipation of its heat to the mal fluid rather than as one which heats the fluid.
  • the heat exchanger may be used equally as well to transfer heat to a precooled thermal fluid which circulates through the exchanger.
  • the rotor assembly 12 includes a manifold plate 26 having an end of each of a series of thermal transfer blades 30 fixed thereto, such as by welding, soldering, brazing or any other suitable technique, in an annular configuration.
  • An end plate 28 is provided at the other end of each of the blades having a central opening 62 which serves to direct ambient air drawn into the rotor. In some circumstances, such an end plate is not necessary, e.g., when the blades are relatively short and the rotor is operated at low r.p.m. In such cases, the blades may be cantilevered from the manifold plate.
  • the manifold plate 26 as best seen in FIG. 2 preferably comprises a channel plate 26 having a central circular chamber 29 formed therethrough which comprises the central fluid inlet 14. Emanating from the central fluid inlet 14 are a plurality of distributor channels 32 which extend outwardly towards the periphery of the manifold plate assembly. As seen in FIG. 2, the distributor channels 32 are arcuate in shape, being curved rearwardly relative to the direction of rotation of the rotor indicated by arrow 33. In the preferred embodiment, the channels form segments of a circle. However, it is understood that arcs of other geometric configuration may be utilized within the scope of the invention. Circular segment arcs have been found particularly suitable due to the ease of machining the channels in their circular form.
  • the distributor channels extend outwardly from the central fluid inlet 14 forming a curved spoke or pinwheel type pattern.
  • the outer ends of the distributor channels terminate in enlarged pockets 34 having approximate trapezoidal shapes defined by two substantially concentric curved ends 36 having their centers at the channel plate center and opposed sides 38 having arcuate shapes which are oriented towards each other as they progress away from the periphery of the plate.
  • a plurality of collector channels 40 are formed in channel plate 26' alternately spaced between adjacent pairs of distributor channels 32.
  • Collector channels 40 assume a rearwardly curved shape similar to that of distributor channels 32.
  • the inner ends of the collector channels 40 terminate in respective bores 42 opening onto the right side of channel plate 26 as seen in FIG. 1. These openings are spaced around an inner annular zone of the channel plate 26', each opening defining a thermal fluid outlet 16 through which the thermal fluid exits from the rotor assembly 12 into outlet passage 24 in the hub assembly 20.
  • the outer ends of collector channels 40 are formed into enlarged pockets 44 having trapezoidal configurations similar in shape and size to distributor channel end pockets 34. As seen in FIG. 2, pockets 44 are formed inwardly of pockets 34 and include inwardly directed sides 46 and concentric parallel sides 48. Pockets 44, as will be seen, act as outlets from the thermal transfer blades and direct the thermal fluid from the blades to the outlets 16.
  • the manifold plate assembly 26 is completed by positioning a template plate 26" over the channel plate 26' and fastening it thereto by conventional means such as by bolts 42.
  • the template plate 26" has a plurality of openings 58 formed therethrough, each opening having a shape of a blade cross section so that a blade end may be received therein. These openings 58 are formed so that each aligns with an associated pair of end pockets 34, 44 in a manner described in detail below.
  • the inner surface 51 of template plate 26" overlies all the distributor and collector passages (except where openings 58 are present) so that the channels are closed defining enclosed passages in the manifold plate assembly 26.
  • a substantially circular gasket 60 is provided between the channel and template plates to prevent leakage of thermal fluid from the passages during operation.
  • a series of openings are formed in the gasket which align over the distributor and collector passages to prevent leakage therefrom in a conventional manner.
  • Blades 30 preferably have a curved cross section as best seen in FIG. 2 and have a generally hollow interior within which the thermal fluid is received from the manifold plate assembly.
  • the interior of each blade 30 is formed having a plurality of partitioning walls 50 which extend longitudinally along the length of each blade defining a plurality of circulation passages 52 which conduct the thermal fluid through the blade in a manner to be described.
  • the end of each wall 50 at the blade end remote from the manifold plate assembly 26 is recessed within the blade, the extent of each recess increasing incrementally towards the center of the blade as seen in FIG. 1.
  • the thermal fluid may exit from the lefthand end of those circulation passages communicating with distributor passages 32 and enter the left-hand ends of those circulation passages communicating with collector passages as shown by arrows 86.
  • the plurality of reduced size circulation passages provides a double advantage over conventional blades which usually have two adjacent passages. Firstly, the plurality of passages increases the heat transfer surface area by providing additional surfaces (those of walls which conduct heat to the blade surfaces and, secondly, increases the structural integrity of the blade which is advantageous due to the relatively high pressure of the thermal fluid which circulates through the blade.
  • any number of partitions and cells may be used so long as at least one passage is provided for the fluid to move away from the manifold plate and one is provided for return.
  • a plurality of heat transfer fins 54 are provided on each blade 30 in order to further improve the heat transfer characteristics of the system.
  • the blades are preferably extruded with the walls 50.
  • the outer surfaces of the blades are preferably skived to form a variable number of fins per unit length.
  • the skiving technique has been found to produce finned blades having extremely good heat transfer characteristics because of the fins being an integral part of the tubes thus eliminating contact resistance as well as promoting greater turbulence within the airstream.
  • the ends of walls 50 are trimmed as shown in FIG. 1 to allow for the thermal fluid flow described above.
  • each distributor passage terminal pocket 34 overlaps the corresponding sides 46 of the collector passage terminal pockets 44 in the direction defined by the side edges 38, 46 respectively of the pockets. More specifically, referring to the direction of rotation of the manifold plate indicated by arrow 33 in FIG. 2, the leading edge 38 of each distributor passage terminal pocket overlies the trailing edge 46 of the associated collector passage terminal pocket in front of it whereas the trailing edge 38 of the same distributor passage terminal pocket overlies the leading edge 46 of another collector passage terminal pocket to its rear.
  • Each pair of sides 38, 46 define the locus of a curved path, such for example as path 56 shown in dotted lines in FIG. 2.
  • the curved configuration of the blade cross section is adapted to identically match with the curved configuration of the above-described locus of points.
  • the configuration of blade 30 as seen in FIG. 2 is identical with the dotted path 56.
  • the openings 58 formed in the template plate 26" have an identical configuration as that defined by dotted path 56. Each opening cooperates with a respective pair of pockets by overlying the curved path as shown.
  • each blade 30 By inserting the end of each blade 30 into a template plate opening 58 where it is subsequently bonded into place, such as by welding, a number of the circulation passages are positioned to communicate with "a distributor passage pocket while others communicate with the collector passage pocket.
  • the template plate serves to both position the ends of the blades over the respective distributor and collector passage terminal pockets and also support the blade ends for rotation with the manifold plate assembly 26.
  • thermal transfer blades 30 are supported by a cover plate 28 having a circular opening 62 formed centrally therethrough.
  • the blade ends are received within recessed grooves 64 and are held in place by any conventional means, such as by welding.
  • a cone 66 may be provided having its base attached to the template plate so that its tapered end extends to the vicinity of the plane of the opening 62. The cone serves to improve the flow of ambient air through the device as is explained in the description of the operation of the device.
  • the hub assembly serves to transmit the thermal fluid to and from the rotor assembly from and to external equipment respectively.
  • the hub assembly includes a pulley member 68 rigidly attached, as by welding, to the outer surface of the manifold plate assembly 26.
  • Pulley member 68 is formed with a partially threaded stepped bore 70 formed centrally therethrough.
  • a plurality of angularly oriented passages 72 are formed extending from that end of pulley member 68 which abuts the manifold plate assembly into bore 70. These passages 72 are adapted to align with the thermal fluid outlets 16 formed in the channel plate 26'.
  • a collar 74 is also attached to the manifold plate assembly disposed within bore 70 and aligned with the central fluid inlet 14.
  • a lubricated seal 76 made of a suitable material such as carbon-filled Teflon, lines the inner surface of collar 74 and forms a sleeve which receives fluid inlet tube 22 which is adapted to remain stationary.
  • the seal 76 therefore acts as both a dynamic fluid seal and as a bearing.
  • a tubular fluid return pipe 78 having an externally threaded end is fastened to the interiorly threaded pulley 68 and defines, in cooperation with the outer surface of passage 22, annular fluid return passage 24.
  • the pipe 78 is rotatably mounted in a conventional sealed fluid rotational connection, such as Model No. 755 All-Purpose Union manufactured by the Deublin Co.
  • a pair of belts 80 are provided within grooves 82 formed on pulley member 68 for driving the hub assembly and attached rotor assembly. It should also be noted that the rotor assembly may be used for driving other equipment, such as an automobile generator, either through a belt drive or by direct coupling.
  • the rotor assembly is rotated by belts 80 from conventional driving means, such as an automobile engine.
  • the blades 30 act as centrifugal fan blades thereby drawing ambient air through opening 62 and over the blade surfaces as depicted by arrows 83.
  • Cone 66 insures that the air drawn into the center of the rotor assembly is substantially evenly distributed over the length of the blades by deflecting the air flow in a radial direction along the axis of the rotor.
  • the thermal fluid enters the manifold plate assembly through passage 22 under pressure supplied by external equipment, such as an automobile water pump.
  • the thermal fluid is described as being preheated by the external equipment (such as an automobile engine).
  • the invention is equally applicable to cases where the thermal fluid has been precooled by external equipment.
  • the thermal fluid As the thermal fluid enters central fluid inlet 14, it is moved substantially radially towards the periphery of the manifold plate assembly in a relatively orderly manner through the distributor passages 32 partially under the action of centrifugal force.
  • Such fluid flow is denoted by arrows 82 in FIG. 1.
  • the fluid Upon reaching the terminal pockets 34 of distributor passages 32, the fluid is at a considerably higher pressure than at the inlet due to the rotation of the device. For example, for a onefoot diameter rotor having an angular velocity of 2,000 rpm, the fluid will be at a pressure of approximately p.s.i. more at the blade entrance than at the inlet of the manifold plate assembly.
  • the thermal fluid enters the circulation passages 52 of the thermal tubes 30 which cooperate with pockets 34 as illustrated by arrows 84.
  • the reduced cross sections of the tube circulation passages 52 minimize the effect of the higher pressure and increase the heat transfer to the blade surfaces as described above.
  • the fluid circulates the length of each of the tubes 30 through the inlet passages 52 and is deflected by the inner surface of the cover plate 28 clos ing the blade end which causes the fluid to enter the return circulation passages 52 of the fins as indicated by arrows 86.
  • the fluid completes the circuit exiting through the collector passage terminal pockets 44 as indicated by arrows 88.
  • the thermal fluid exits from rotor assembly 12 via the thermal fluid outlets 16 which communicate with the tubular fluid return passage 24.
  • the design of the manifold plate assembly wherein the inlet and outlet passages are in substantially the same plane serves to in crease the compact character of the heat exchanger.
  • the fluid inlet and outlet passages have been in different planes which not only made the fluid transfer apparatus more complicated and cumbersome, but also increased the bulkiness of the exchanger.
  • the present invention maximizes the compact character of the device while minimizing the structural complexity of the design.
  • the manifold plate structure may be different from that specifically described.
  • the manifold plate may be made in a unitary manner rather than having a multiple plate configuration.
  • Still another advantage derived from the manifold plate construction is the large choice of fabrication techniques available.
  • the manifold plate may be formed by casting, machining (such as by milling), chemical etching, etc.
  • the blades are mounted in a rearward direction, i.e. sloping downwardly and inwardly in the direction of rotation of the rotor assembly.
  • Such orientation provides a relatively high velocity of air over the surface of the blades relative to the surface of the blades while maintaining the power requirements at a relatively low value due to the decreased absolute velocity of the air relative to the stationary surroundings.
  • the blades may be oriented otherwise (e.g. radially) to take advantage of other resulting characteristics, i.e. strength, air velocity, etc.
  • each blade must have an end cover to direct the flow of the thermal fluid from the inlet circulation passage to the outlet circulation passage.
  • FIG. 3 a typical structural arrangement according to the present invention is illustrated, wherein the identical blade structure to that shown in FIGS. 1 and 2 is employed.
  • An inlet tube 100 serves to direct incoming thermal fluids to a distribution chamber 102 defined between a pair of opposed dish-shaped wall members 104, 106 rotatably mounted over tube 100.
  • the inner wall member 104 is formed with a central opening 108 which receives the end of tube 100 and is in continual cooperation with a dynamic seal 107.
  • the central portion of the outer wall member 106 is closed and may be appropriately formed to function as a cone for directing air drawn into the rotor assembly by the blades.
  • the outer periphery of inner wall 104 is turned inwardly to form a lip 112 which abuts the end of each blade 30' so as to divide the blade substantially in half.
  • the outer periphery of the outer wall 106 is inwardly turned to form a lip 114 which cooperates with the blade end edge.
  • the distribution chamber 102 thereby serves to direct the incoming thermal fluid to the lower half portion of the blade as seen in FIG. 3.
  • the blade is formed with a plurality of longitudinally extending cells as was the case in the embodiment described previously.
  • the distribution chamber 102 communicates with the lowermost cells as seen in FIG. 3, and these cells will function as thermal fluid inlet circulation passages.
  • Integrally provided within distribution chamber 102 are a plurality of evenly spaced impeller blades 116 which rotate with the distribution chamber as will be described to direct the incoming thermal fluid outwardly towards the rotating blades 30.
  • An annular thermal fluid collection chamber is formed by an end member 117 having a lip 118 formed on its outer periphery in cooperation with the other edge of the blade end and the outer surface of inner wall member 104.
  • the end member 117 is rotatably mounted on a stationary tubular pipe 122 by means of bearings 121 positioned thereover in cooperation with a collar 124 centrally formed on end member 117.
  • a plurality of stator blades 126 have their ends 128 rigidly attached to the fluid inlet passage 100 so that they are stationary within the fluid collection chamber 120.
  • the inner surface of the stationary tubular pipe 122 cooperates with the outer surface of the inlet tube 100 to form an annular fluid passage 130 which serves to transmit the fluid back to the external equipment.
  • An O-ring assembly 131 is provided to prevent escape of the thermal fluid from the fluid outlet passage 130.
  • the blades are rotated via rotation of a pulley 132 formed on collar 124 which rotates end member 117 thereby causing the rotor blades 30' to revolve.
  • This revolves the inner and outer opposed walls 104, 106 defining the fluid distribution chamber and integral impeller blades which are rigidly connected to the blades.
  • the incoming thermal fluid is directed to the periphery of the distribution chamber and enters the inlet circulation passages in the blades. Upon circulating through the blades, the fluid enters the fluid collection chamber 120.
  • the circular motion of the fluid is interrupted by the stator blades 126 which convert the high circumferential velocity of the fluid to radial movement with little or no loss in momentum thereby causing a pressure increase of the fluid within the collection chamber 120.
  • the fluid is directed outwardly through the fluid transfer passage 130 at a higher pressure than when it entered through inlet passage 100.
  • the rotary heat exchanger functions as a pump. This enables external fluid pumps in the circulation system to be dispensed with.
  • a rotatably mounted rotor assembly including,
  • a substantially circular manifold plate having fluid distribution passages formed therein defining a single plane, the two ends of each of said distribution passages terminating in the central area and the peripheral area of said plate respectively, and fluid collection passages located in the same single plane as said distribution passages, the two ends of each of said collection passages terminating in the central area and the peripheral area of said plate, respectively, and
  • thermal transfer blades extending substantially parallel to the axis of rotation of said rotor assembly, each having one end fixed to the peripheral area of said manifold plate, the interior of at least one of said thermal transfer blades communicating with the peripheral end of one of said fluid distribution passages and the interior of at least one of said thermal transfer blades communicating with the periph- 5 eral end of one of said fluid collection passages;
  • a hub assembly contiguous to said manifold plate including a fluid inlet passage communicating with the central end of each of said fluid distribution passages and a fluid outlet passage communicating with the central end of each of said fluid collection passages.
  • each of said fluid distribution passages has an arcuate shape, said arcuate shapes all lying within said single plane.
  • each of said fluid collection passages has an arcuate shape, said arcuate shapes all lying within said single plane.
  • each of said thermal transfer blades is provided with partitions defining a series of parallel cells extending longitudinally within said blade and wherein the ends of each partition remote from the manifold plate are recessed, the extent of such recess in each partition increasing incrementally in those partitions in closer proximity to the center of said blade.
  • a rotor assembly including,
  • a rotatably mounted fluid distribution chamber having a central fluid inlet for receiving thermal fluid from external equipment and a peripheral fluid outlet for directing thermal fluid into the interior of hollow thermal transfer blades and a plurality of impeller blades fixed within said distribution chamber for rotation therewith; fluid collection chamber having a central fluid outlet and a peripheral fluid inlet for receiving thermal fluid from the interior of hollow thermal transfer blades, said fluid collection chamber having a plurality of stationary stator elements located therein, plurality of hollow thermal transfer blades, the interior of at least one of said blades communicating with the peripheral fluid outlet of said fluid distribution chamber and the interior of at least one of said blades communicating with the peripheral fluid inlet of said fluid collection chamber, a hub assembly contiguous with said rotor assembly including a fluid inlet passage communicating with the central fluid inlet of said distribution chamber and a fluid outlet passage communicating with the central fluid outlet of said collection chamber.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US00328686A 1973-02-01 1973-02-01 Rotatable heat exchanger Expired - Lifetime US3835921A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US00328686A US3835921A (en) 1973-02-01 1973-02-01 Rotatable heat exchanger
DE2404488A DE2404488A1 (de) 1973-02-01 1974-01-31 Rotierender waermeaustauscher
FR7403376A FR2216536B3 (enExample) 1973-02-01 1974-02-01
JP49013569A JPS5047242A (enExample) 1973-02-01 1974-02-01

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US00328686A US3835921A (en) 1973-02-01 1973-02-01 Rotatable heat exchanger

Publications (1)

Publication Number Publication Date
US3835921A true US3835921A (en) 1974-09-17

Family

ID=23281992

Family Applications (1)

Application Number Title Priority Date Filing Date
US00328686A Expired - Lifetime US3835921A (en) 1973-02-01 1973-02-01 Rotatable heat exchanger

Country Status (4)

Country Link
US (1) US3835921A (enExample)
JP (1) JPS5047242A (enExample)
DE (1) DE2404488A1 (enExample)
FR (1) FR2216536B3 (enExample)

Cited By (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4986345A (en) * 1988-02-09 1991-01-22 Nissan Motor Co., Ltd. Rotary heat exchanger
US5791153A (en) * 1995-11-09 1998-08-11 La Roche Industries Inc. High efficiency air conditioning system with humidity control
US5826434A (en) * 1995-11-09 1998-10-27 Novelaire Technologies, L.L.C. High efficiency outdoor air conditioning system
US6120247A (en) * 1999-06-01 2000-09-19 Wheeler; Alton D. Room cooling fan apparatus
US6131653A (en) * 1996-03-08 2000-10-17 Larsson; Donald E. Method and apparatus for dehumidifying and conditioning air
US20050000681A1 (en) * 2001-05-31 2005-01-06 Venmar Ventilation Inc. Air handling systems or devices intermingling fresh and stale air
US20080251238A1 (en) * 2004-11-12 2008-10-16 Bjorn Gudmundsson Cooling Device
US20090071182A1 (en) * 2007-09-18 2009-03-19 Yi-Hsiung Lin Auto-cleaning device for an indoor air conditioner
US20100059204A1 (en) * 2008-07-23 2010-03-11 Klaus Stanke Device and process for heat transfer
CN102889246A (zh) * 2012-10-24 2013-01-23 苏宇贵 直接换热式风扇及使用该风扇的空调系统
DE102016116276A1 (de) 2016-08-31 2018-03-01 Ebm-Papst Mulfingen Gmbh & Co. Kg Wärmetauscherintegration
WO2018102515A1 (en) * 2016-11-30 2018-06-07 Whirlpool Corporation System for cooling components in an electronic module
US10830056B2 (en) 2017-02-03 2020-11-10 General Electric Company Fluid cooling systems for a gas turbine engine
DE102019213613A1 (de) * 2019-09-06 2021-03-11 Hochschule Karlsruhe Verdampfer für eine Wärmepumpe oder Kältemaschine
US10993294B2 (en) 2016-10-19 2021-04-27 Whirlpool Corporation Food load cooking time modulation
US11041629B2 (en) 2016-10-19 2021-06-22 Whirlpool Corporation System and method for food preparation utilizing a multi-layer model
US11051371B2 (en) 2016-10-19 2021-06-29 Whirlpool Corporation Method and device for electromagnetic cooking using closed loop control
US11102854B2 (en) 2016-12-29 2021-08-24 Whirlpool Corporation System and method for controlling a heating distribution in an electromagnetic cooking device
US11184960B2 (en) 2016-12-29 2021-11-23 Whirlpool Corporation System and method for controlling power for a cooking device
US11197355B2 (en) 2016-12-22 2021-12-07 Whirlpool Corporation Method and device for electromagnetic cooking using non-centered loads
US11202348B2 (en) 2016-12-22 2021-12-14 Whirlpool Corporation Method and device for electromagnetic cooking using non-centered loads management through spectromodal axis rotation
US11246191B2 (en) 2016-09-22 2022-02-08 Whirlpool Corporation Method and system for radio frequency electromagnetic energy delivery
US11343883B2 (en) 2016-12-29 2022-05-24 Whirlpool Corporation Detecting changes in food load characteristics using Q-factor
US11412585B2 (en) 2016-12-29 2022-08-09 Whirlpool Corporation Electromagnetic cooking device with automatic anti-splatter operation
US11432379B2 (en) 2016-12-29 2022-08-30 Whirlpool Corporation Electromagnetic cooking device with automatic liquid heating and method of controlling cooking in the electromagnetic cooking device
US11452182B2 (en) 2016-12-29 2022-09-20 Whirlpool Corporation System and method for detecting changes in food load characteristics using coefficient of variation of efficiency
US11483906B2 (en) 2016-12-29 2022-10-25 Whirlpool Corporation System and method for detecting cooking level of food load
US11503679B2 (en) 2016-12-29 2022-11-15 Whirlpool Corporation Electromagnetic cooking device with automatic popcorn popping feature and method of controlling cooking in the electromagnetic device
US11635262B2 (en) * 2018-12-20 2023-04-25 Deere & Company Rotary heat exchanger and system thereof
US11638333B2 (en) 2016-12-29 2023-04-25 Whirlpool Corporation System and method for analyzing a frequency response of an electromagnetic cooking device
US11690147B2 (en) 2016-12-29 2023-06-27 Whirlpool Corporation Electromagnetic cooking device with automatic boiling detection and method of controlling cooking in the electromagnetic cooking device
US11917743B2 (en) 2016-12-29 2024-02-27 Whirlpool Corporation Electromagnetic cooking device with automatic melt operation and method of controlling cooking in the electromagnetic cooking device
US12376202B2 (en) 2016-12-27 2025-07-29 Whirlpool Corporation Nano-cooling in solid-state cooking microwave ovens

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100475947B1 (ko) * 2002-06-26 2005-03-10 현대자동차주식회사 자동차용 공조장치

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1829753A (en) * 1928-10-22 1931-11-03 Turbo Mixer Corp Heat interchange and mixing apparatus
DE888048C (de) * 1950-04-29 1953-08-27 Richard Dipl-Ing Schiel Einstufige Hohllaeufer-Kreiselpumpe
US3347059A (en) * 1964-01-22 1967-10-17 Laing Nikolaus Heat pump
US3477499A (en) * 1968-06-13 1969-11-11 Edward E Goetz Rotatable thermal transfer units

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1829753A (en) * 1928-10-22 1931-11-03 Turbo Mixer Corp Heat interchange and mixing apparatus
DE888048C (de) * 1950-04-29 1953-08-27 Richard Dipl-Ing Schiel Einstufige Hohllaeufer-Kreiselpumpe
US3347059A (en) * 1964-01-22 1967-10-17 Laing Nikolaus Heat pump
US3477499A (en) * 1968-06-13 1969-11-11 Edward E Goetz Rotatable thermal transfer units

Cited By (40)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4986345A (en) * 1988-02-09 1991-01-22 Nissan Motor Co., Ltd. Rotary heat exchanger
US5791153A (en) * 1995-11-09 1998-08-11 La Roche Industries Inc. High efficiency air conditioning system with humidity control
US5826434A (en) * 1995-11-09 1998-10-27 Novelaire Technologies, L.L.C. High efficiency outdoor air conditioning system
US6131653A (en) * 1996-03-08 2000-10-17 Larsson; Donald E. Method and apparatus for dehumidifying and conditioning air
US6120247A (en) * 1999-06-01 2000-09-19 Wheeler; Alton D. Room cooling fan apparatus
US7635296B2 (en) 2001-05-31 2009-12-22 Venmar Ventilation Inc. Air handling systems or devices intermingling fresh and stale air
US20050000681A1 (en) * 2001-05-31 2005-01-06 Venmar Ventilation Inc. Air handling systems or devices intermingling fresh and stale air
US20050006058A1 (en) * 2001-05-31 2005-01-13 Venmar Ventilation Inc. Blower wheel assembly
US20090253365A1 (en) * 2001-05-31 2009-10-08 Venmar Ventilation Inc. Blower wheel assembly having a dynamic seal member for providing an air seal on rotation of a blower wheel
US20080251238A1 (en) * 2004-11-12 2008-10-16 Bjorn Gudmundsson Cooling Device
US20090071182A1 (en) * 2007-09-18 2009-03-19 Yi-Hsiung Lin Auto-cleaning device for an indoor air conditioner
US20100059204A1 (en) * 2008-07-23 2010-03-11 Klaus Stanke Device and process for heat transfer
US8211371B2 (en) * 2008-07-23 2012-07-03 Andritz Technology And Asset Management Gmbh Device and process for heat transfer
CN102889246A (zh) * 2012-10-24 2013-01-23 苏宇贵 直接换热式风扇及使用该风扇的空调系统
DE102016116276A1 (de) 2016-08-31 2018-03-01 Ebm-Papst Mulfingen Gmbh & Co. Kg Wärmetauscherintegration
US11246191B2 (en) 2016-09-22 2022-02-08 Whirlpool Corporation Method and system for radio frequency electromagnetic energy delivery
US11041629B2 (en) 2016-10-19 2021-06-22 Whirlpool Corporation System and method for food preparation utilizing a multi-layer model
US10993294B2 (en) 2016-10-19 2021-04-27 Whirlpool Corporation Food load cooking time modulation
US11051371B2 (en) 2016-10-19 2021-06-29 Whirlpool Corporation Method and device for electromagnetic cooking using closed loop control
WO2018102515A1 (en) * 2016-11-30 2018-06-07 Whirlpool Corporation System for cooling components in an electronic module
CN109416225A (zh) * 2016-11-30 2019-03-01 惠而浦有限公司 用于冷却电子模块中的部件的系统
US12068225B2 (en) 2016-11-30 2024-08-20 Whirlpool Corporation System for cooling components in an electronic module
US11417585B2 (en) 2016-11-30 2022-08-16 Whirlpool Corporation System for cooling components in an electronic module
US11197355B2 (en) 2016-12-22 2021-12-07 Whirlpool Corporation Method and device for electromagnetic cooking using non-centered loads
US11202348B2 (en) 2016-12-22 2021-12-14 Whirlpool Corporation Method and device for electromagnetic cooking using non-centered loads management through spectromodal axis rotation
US12376202B2 (en) 2016-12-27 2025-07-29 Whirlpool Corporation Nano-cooling in solid-state cooking microwave ovens
US11343883B2 (en) 2016-12-29 2022-05-24 Whirlpool Corporation Detecting changes in food load characteristics using Q-factor
US11503679B2 (en) 2016-12-29 2022-11-15 Whirlpool Corporation Electromagnetic cooking device with automatic popcorn popping feature and method of controlling cooking in the electromagnetic device
US11412585B2 (en) 2016-12-29 2022-08-09 Whirlpool Corporation Electromagnetic cooking device with automatic anti-splatter operation
US11184960B2 (en) 2016-12-29 2021-11-23 Whirlpool Corporation System and method for controlling power for a cooking device
US11432379B2 (en) 2016-12-29 2022-08-30 Whirlpool Corporation Electromagnetic cooking device with automatic liquid heating and method of controlling cooking in the electromagnetic cooking device
US11452182B2 (en) 2016-12-29 2022-09-20 Whirlpool Corporation System and method for detecting changes in food load characteristics using coefficient of variation of efficiency
US11483906B2 (en) 2016-12-29 2022-10-25 Whirlpool Corporation System and method for detecting cooking level of food load
US11102854B2 (en) 2016-12-29 2021-08-24 Whirlpool Corporation System and method for controlling a heating distribution in an electromagnetic cooking device
US11917743B2 (en) 2016-12-29 2024-02-27 Whirlpool Corporation Electromagnetic cooking device with automatic melt operation and method of controlling cooking in the electromagnetic cooking device
US11638333B2 (en) 2016-12-29 2023-04-25 Whirlpool Corporation System and method for analyzing a frequency response of an electromagnetic cooking device
US11690147B2 (en) 2016-12-29 2023-06-27 Whirlpool Corporation Electromagnetic cooking device with automatic boiling detection and method of controlling cooking in the electromagnetic cooking device
US10830056B2 (en) 2017-02-03 2020-11-10 General Electric Company Fluid cooling systems for a gas turbine engine
US11635262B2 (en) * 2018-12-20 2023-04-25 Deere & Company Rotary heat exchanger and system thereof
DE102019213613A1 (de) * 2019-09-06 2021-03-11 Hochschule Karlsruhe Verdampfer für eine Wärmepumpe oder Kältemaschine

Also Published As

Publication number Publication date
DE2404488A1 (de) 1974-08-22
JPS5047242A (enExample) 1975-04-26
FR2216536B3 (enExample) 1976-11-26
FR2216536A1 (enExample) 1974-08-30

Similar Documents

Publication Publication Date Title
US3835921A (en) Rotatable heat exchanger
US11519672B2 (en) Liquid-cooled heat dissipation device and vehicle
US5172752A (en) Curved heat exchanger with low frontal area tube passes
US4180130A (en) Heat exchange apparatus including a toroidal-type radiator
US3347059A (en) Heat pump
US3800866A (en) Radiator assembly
US3355883A (en) Closed loop heat exchanger for a gas turbine engine
US4073338A (en) Heat exchangers
US3612168A (en) Rotatable heat transfer means
US2325222A (en) Air impelling apparatus
US4373577A (en) Heat exchanger assembly
US3773106A (en) Rotary heat exchangers
US3811495A (en) Rotary heat exchangers in the form of turbines
US7506680B1 (en) Helical heat exchange apparatus
US4313493A (en) Forced air unit
US5351747A (en) Heat exchanger especially for spacecraft
US1980811A (en) Cooling system for internal combustion engines
WO2024218487A1 (en) Dehumidifier
JP3058233B2 (ja) 空気調和機
GB1346733A (en) Rotary heat-exchanger
CN110098695B (zh) 圆筒状的冷却器结构
JP2958190B2 (ja) エンジン冷却装置
US3295597A (en) Heat exchangers
US3260306A (en) Heat exchangers
US2407496A (en) Fluid transmission

Legal Events

Date Code Title Description
AS Assignment

Owner name: WHITEHALL BUSINESS CREDIT CORPORATION, NEW YORK

Free format text: SECURITY INTEREST;ASSIGNOR:DES CHAMPS LABORATORIES INCORPORATED;REEL/FRAME:013608/0266

Effective date: 20030417