US3872916A - Fan shroud exit structure - Google Patents

Fan shroud exit structure Download PDF

Info

Publication number
US3872916A
US3872916A US34843673A US3872916A US 3872916 A US3872916 A US 3872916A US 34843673 A US34843673 A US 34843673A US 3872916 A US3872916 A US 3872916A
Authority
US
United States
Prior art keywords
fan
shroud
aw
means
section
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
Inventor
Harold D Beck
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.)
CNH Industrial America LLC
Navistar International Corp
Original Assignee
Navistar International 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 Navistar International Corp filed Critical Navistar International Corp
Priority to US34843673 priority Critical patent/US3872916A/en
Application granted granted Critical
Publication of US3872916A publication Critical patent/US3872916A/en
Assigned to PATTERSON, LINDA L., TRUSTEE, FIDELITY UNION BANK, TRUSTEE reassignment PATTERSON, LINDA L., TRUSTEE SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: INTERNATIONAL HARVESTER COMPANY
Assigned to INTERNATIONAL HARVESTER COMPANY reassignment INTERNATIONAL HARVESTER COMPANY ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: FIRST FIDELTY BANK, NATIONAL ASSOCIATION PATTERSON, LINDA L.; TRUSTEES
Assigned to J.I. CASE COMPANY A DE CORP reassignment J.I. CASE COMPANY A DE CORP ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: INTERNATIONAL HARVESTER COMPANY A DE CORP
Assigned to CASE CORPORATION, A CORP. OF DELAWARE reassignment CASE CORPORATION, A CORP. OF DELAWARE CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: J. I. CASE COMPANY, A CORP. OF DELAWARE
Anticipated expiration legal-status Critical
Application status is Expired - Lifetime legal-status Critical

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/40Casings; Connections of working fluid
    • F04D29/52Casings; Connections of working fluid for axial pumps
    • F04D29/54Fluid-guiding means, e.g. diffusers
    • F04D29/541Specially adapted for elastic fluid pumps
    • F04D29/545Ducts
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01PCOOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00Pumping cooling-air or liquid coolants
    • F01P5/02Pumping cooling-air; Arrangements of cooling-air pumps, e.g. fans or blowers
    • F01P5/06Guiding or ducting air to, or from, ducted fans

Abstract

An internal combustion engine, having a heat exchange cooling system, a fan for moving air therethrough and a shroud and shroud exit section for controlling the air path. The shroud exit encloses the fan and includes throat (CF) radial expander (R) and radial flat (RF) sections whereby air is drawn through the heat exchanger axially and expelled radially along said exit sections. The fan has a projected axial width (AW) such that a general relationship exists with the shroud exit sections: CF AW/3, RF AW/3, and R 2AW/3.

Description

States Patent [1 1 Mar. 25, 1975 [73] Assignee: International Harvester Company,

Chicago, Ill.

[22] Filed: Apr. 5., 1973 [21] Appl. No.: 348,436

[52] US. Cl 165/1, 123/4149, 165/51, 165/122, 180/54 A, 415/210, 415/219 R [51] Int. Cl. F28d 21/00 [58] Field of Search 123/4148, 41.49; 180/54 A, 68 R; 415/210, 219 R, D10. 1; 165/1, 51, 122

[56] References Cited UNITED STATES PATENTS 1,519,812 12/1924 Schneider 123/4149 X 1,691,598 11/1928 Zbinden 123/4149 1,966,787 7/1934 Buri 123/4149 2,142,307 l/1939 De Mey ct a1. 415/210 2,415,621 2/1947 Arnhym 415/119 X 2,544,490 3/1951 Curley 415/219 R 2,664,961 l/l954 Goedem. 415/210 X 2,668,523 2/1954 Lamb 415/219 R 3,144,859 3/1964 Walton 123/4149 FOREIGN PATENTS OR APPLlCATlONS 485,410 10/1953 Italy 123/4149 7/1939 Australia...l 415/210 107,876 770,848 3/1957 United Kingdom .1 123/4149 569,241 1/1933 Germany 1. 415/219 R OTHER PUBLlCATlONS Applications of the Coanda Effect, lmants Reba, Sci entific American, Vol. 214, No. 6, 6-66, pps 8492.

Primary E.raminerAlbert W. Davis, Jr.

Assistant Examiner-S. J. Richter Attorney, Agent, or Firm-Frederick J. Krubel; Floyd B. Harman; John A. Schaerli [57] ABSTRACT An internal combustion engine, having a heat exchange cooling system, a fan for moving air there through and a shroud and shroud exit section for controlling the air path. The shroud exit encloses the fan and includes throat (CF) radial expander (R) and radial flat (RF) sections whereby air is drawn through the heat exchanger axially and expelled radially along said exit sections. The fan has a projected axial width (AW) such that a general relationship exists with the shroud exit sections: CF =AW/3, RF =AW/3, and R I 2A W/3.

14 Claims, 4 Drawing Figures sum 1 0 2 PATENTEDHARZSHNS mama p 2 F JQL F M LL PRIOR ART FAN SHROUD EXIT STRUCTURE This invention relates to a cooling assembly and more particularly to a contoured fan shroud exit section and a fan located therein.

Most vehicles in general use today are driven by internal combustion engines. These engines being heat producing are for the most part water cooled, that is the engine is jacketed for circulation of water which takes up the heat and subsequently transfers it to the atmosphere. The radiator is used for cooling the liquid circulating through the engine by dissipating the heat to an air stream. The air flowing through the radiator absorbs the heat and carries it out into the atmosphere. Different types of fan systems are used to achieve the necessary air velocity through the radiator. That is, some fan assemblies draw air from the atmosphere through the radiator and back over the engine thereafter exiting to the atmosphere. This type of fan is known as an axial flow suction fan, drawing air axially through the radiator and discharging it into the engine compartment. Other fans work in the reversed manner, that is, they draw air from the engine compartment wherefrom it is blown forwardly through the radiator to achieve the necessary radiator cooling. This latter system is often employed when the vehicle is performing tasks that generate large amounts of dust or air borne particles, to keep such material from settling in the engine compartment or where thermal and/or air pollution are detrimental to operator environment. This dust problem is found in many cases to have a detrimental effect upon the engine and its performance while heat and noise reduce the efficiency of the operator. Baffle systems are often involved to redirect the air drawn rearwardly by the suction fan, however, such devices are often complicated and as is apparent employ additional parts, labor, and services. The reverse or forwardly blown air through the radiator also suffered from the fact that the air was often heated substantially by the passage around the hot engine and, depending'upon how fast the vehicle was moving forwardly necessitated additional fan power to overcome the rearward vehicle generated air stream. With the increase in power deliv' ered to the fan, fuel consumption increased and noise pollution increased.

It is thus apparent that both above methods possess characteristics which are far from that which aredesirable. It is therefore an object of this invention to provide a cooling assembly which directs dust and air borne particles so as to enhance their expulsion from the engine compartment. Yet another object of this invention is to provide an air exit section for a fan shroud whereby maximizing air flow and improving operator environment by reducing thermal, noise, and air pollution. Still another object of this invention is to provide a fan shroud exit section and a fan having a relationship whereby optimum air flow and noise values are achieved. Another. object ofthis invention is to provide a fan shroud exit section and a fan oriented therein whereby the air flow discharge path can be tailored and, ifso desired, bent to exit radially. A further object of this invention is to provide a fan shroud with an exit section which is capable of producing the Coanda effect. Still another object of this invention is to provide an air exit section and a fan having a relationship whereby the Coanda effect can be maintained over a substantial range of fan speeds. Still another object of this invention is to provide an engine cooling assembly which does not direct heated air toward the operator station.

In accordance with the preferred embodiment of this invention a vehicle is provided having a liquid cooled internal combustion engine and a radiator cooling sys' tem for dissipating the heat produced. The radiator cooling system includes a standard radiator, an axial flow fan facing the radiator and having a plurality of angular blades whereby air is drawn rearwardly through the radiator. A shroud rearwardly extends from the back face of the radiator to channel air through the radiator and hamper the fan from drawing air which has not passed through or at least come in contact with the perforated heat exchanging surfaces of the radiator. For the most part the shroud encloses the entire perforated heat exchanging rear area of the radiator. A fan shroud exit means is also provided having secured to the backwardly extending portion oftbe fan shroud and extending rearwardly thereof as well as outwardly. As will be later explained it is the particular contour of this exit section in combination with an axial flow fan located therein, the location thereof also being important, which allows the air stream to be converged and directed radially away from the engine compartment. As is apparent this invention is also applicable to a stationary engine where it is desired to direct the air stream.

Other objects and advantages of the invention will become apparent upon reading the following detailed description and upon reference to the drawings, in which;

FIG. 1 is a side elevation of an internal combustion engine showing the device of my invention attached to a vehicle;

FIG. 2 is a fragmentary vertical section showing the relationship of the fan to the contoured exit section;

FIG. 3 is a top view of a tractor showing the air stream of the prior art fan assemblies; and

FIG. 4 is atop view of a tractor showing the directed air stream achieved with the radiator cooling assembly herein disclosed.

While the invention will be described in connection with a preferred embodiment, it will be understood that it is not intended to limit the invention to that embodiment. On the contrary, it is intended to cover all alternatives, modifications and equivalents as may be included within the spirit and scope of this invention as defined by the appended claims.

Turning first to FIG. 1 there is shown a conventional water cooled heat producing internal combustion engine means 10 forwardly carried on longitudinally extending parallel support means 12 of vehicle means 14. As shown herein vehicle means 14 is a tractor, however, as will hereafter become more apparent this invention can be applied to any type ofvehicle employing a heat generating internal combustion engine or any other portable or stationary device requiring an air moving fan. Forwardly mounted is a water cooling radiator means 16 employed to dissipate the engine generated heat. Water flows between the waterjacket on the engine (not shown) and the radiator through a series of fluid communicating means l8 and 20. In this particular embodiment sheet metal means 22 encircles engine means 10 thereby forming the engine compartment area means 24.

Carried at the forward end of engine means 10 is a fan shaft means 26 whereby power is delivered to drive fan means 28. As is apparent, the particular mode whereby power is transmitted thereto is not critical and belts and pulleys could also be employed. As employed here, fan means 28 is a rotatable suction fan positioned opposite the radiator means 16, and normally creating a flow of air or drawing in a stream of cooling air rearwardly through the radiator with a subsequent axial discharge thereof. This axial flow of air is directed to the fan means by a shroud means 30. The particular shape of the forward section 32 is dependent upon the shape and design of the perforated heat exchanging design of the radiator. The nature of the connection between the leading edge of 32 and the rear face 34 of the radiator will be dependent upon the particular characteristics of these components, that is, some connections being provided with air gaps while others are substantially sealed over the entire circumference of the enclosure. In the preferred form of this invention the entire perforated area is substantially sealed against the passage of air from any other direction except through the radiator. From the forward edges the shroud means (be it a taper transition as shown or a box type) converges rearwardly to a circular rear section 36.

Referring now to FIG. 2 wherein is more clearly shown a shroud exit means 38 extending rearwardly and outwardly from shroud edge 36. The connection between the shroud and the shroud exit can be achieved by any suitable means, however, it is desirable that such connection be relatively free of gaps or spaces which would allow the passage of air. Exit shroud means 38 includes a tubular means 40, an arcuated means portion 42 and a flat flange portion means 44. For the most part tubular means portion 40 forms the leading edge of the exit shroud means while arcuated means portion 42 still extending generally rearwardly simultaneously extends outwardly around an arch the reference point ofwhich is defined as point 46. That is, arcuated section 42 has a general bell-shaped appearance being a section of a transition surface or some approximation thereof. In the preferred embodimcnt arcuatcd section 42 is a section of a constant radius arch. Flat flange portion 44 forms the trailing edge of exit shroud means 38 and has a major plane perpendicular to that of tubular section 40. For purposes of simplicity, tubular means 40 will be hereafter referred to as the cylindrical throat means, arcuated portion 42 will be referred to as the radial expanding means and flat flange portion 44 will be referred to as radial flat means. Overall the entire fan shroud exit means 38 has a horn-like configuration.

As previously stated, fan means 28 is rotatingly carried adjacent said radiator means and operably to establish a flow of cooling air therethrough. Fan means 28 includes a plurality of fan blade means 48 (only one shown) as is well known in the art. As shown in FIG. 2 fan means 28 is surrounded by said contoured fan shroud exit section 38. The enclosure of the fan means 28 within shroud means 30 is such that a front plane struck out by the leading edge 50 is coextensive and passes through the leading section of throat means 40 and a rear plane struck out by trailing edge 52 is about coextensive and parallel with said radial flat portion 44. It should be noted, however, that there is a plus or minus error factor involved in both of these values of about 12 percent of AW. That is, the respective planes formed by the blade means can be within about 12 percent of optimum and still function satisfactorily within 4 the scope of this invention. Thus, within this range the direction air stream will still be substantially radial.

It has been determined, however, that best results are obtained when the front plane struck out by leading edge means 50 passes through the juncture point between converging shroud 36 and the throat section 40. Even more determinative on the result is the relationship between the rear plane struck out by trailing edge means 52 and the radial flat portion 44. Overall performance is achieved when the rear plane and the radial flat portion 44 are coextensive and parallel. Deviations from this orientation cause the air stream to change more rapidly than corresponding percentage changes in the front plane location.

The following relationship exists between these parameters: RF =AW/3, CF AW/3, and R 2AW/3 where RF is the length of the radial flat portion 44, (F is the length of the cylindrical throat section 40 and R is a radius of the radial expanding section 42 or distance from the reference point to the transistion surface and AW is the projected axial width of fan 28.

Although not obvious from a simple consideration of the layout the cooling assembly embodied herein, horsepower savings and noise reduction are realized. The geometry of the shroud exit and positioning of the fan therein so effects the cooling characteristics of the assembly that fewer rpms of the fan are necessary to achieve the same temperature reduction ofthe coolant. Hence, decreasing the fan speed yields a reduction of fan generated noise and power required to drive the fan. Because of the radial discharge of the air stream dust and particle matter are swept away from the operator and not back on him. The same is true for the heat which has been passed to the air, it issues away from the operator station.

FIGS. 3 and 4 show the path in which air is dispersed by the fan means comprising again a standard assembly and the improved assembly, thus, the achieved is apparent.

In actual tests on an International Harvester tractor model number Fl()26 equipped with the improved cooling assembly provided the same cooling capacity while making a number of improvements. These ineluded about a 20 percent reduction in fan drive power, about a 6dB reduction in actual fan noise, 4dB reduction of overall vehicle noise at operator station and operator station temperature reductions of 20F at his feet, 8F at his head and 5F at the steering wheel. It thus is apparent that shroud exit geometry and fan relationships can make substantial improvements in the air flow and its discharge direction, noise, and required fan drive power characteristics ofa cooling fan. Louver means 56 can also be provided to allow the easy and quick dissipation of the radially discharged air.

The amount or relation of the fan means 28 to the exit section means 38 is most conveniently expressed in terms of the amount of the fan which is exposed past the end of the shroud or projects rearwardly thereof. It has been found that a X,,-equal to zero gives optimum results; however, reasonable results can be achieved by having X,.; about equal to plus or minus 12 percent of AW. That is, as explained previously when the plane swept out by the rear edge is coextensive with the surface of the radial flat or within the tolerance set forth. By changing the orientation of the fan with respect to the fan exit section it is also possible to direct the air stream, straight back, at an angle off radial, etc.,

depending on preference and need.

Thus it is apparent that there has been provided a heat exchange system including, a heat exchange means such as a radiator, a fan shroud and a fan shroud exit section with a fan therein. An exit section includes, in order, a cylindrical throat section, a radial expanding section, and a radial flat portion. The leading edge of the cylindrical throat section being secured to the shroud around its entire circumference. The fan assembly carried in the shroud exit section includes a plurality of fan blades having front or leading edges and trailing or rear edges. These edge means sweep out planes as they rotate, that is, a front and rear plane. The front plane for the most part should intersect thejunction between the shroud end and the cylindrical throat while the rear plane should be parallel to and coextensive with the radial flat portion. By experimentation it has been determined that the relationship of the rear plane to the radial flat is the more critical of the two parameters. [n the assembly the following relationship plus or minus 12 percent ofAW exists: RF =AW divided by 3, (F AW divided by 3, and R 2AW divided by 3 where RF is the length of the radial flat portion, CF is the length of the cylindrical throat, R is the distance from the referencepoint to the radial expanding section and A W is the projected axial width of the fan. As has been pointed out previously the R value in the preferred embodiment is the radius of the radial expanding section, that is, the radial expanding section is a part of a circle. However, as is apparent it may deviate from this preferred form. Accordingly, the fan induced stream of air is converged and directed out of the shroud exit parallel to the radial flat portion thus avoiding the passage of dust and particle laden air currents against the engine and subsequently against the operator station.

Thus it is apparent that there has been provided, in accordance with the invention, a shroud exit means that fully satisfies the objects, aims, and advantages set forth above. While the invention has been described in conjunction with specific embodiments thereof, it is evident that many alternatives, modifications, and variations will be apparent to those skilled in the art in light ofthe foregoing description. Accordingly, it is intended to embrace all such alternatives, modifications, and variations as fall within the spirit and broad scope of the appended claims.

What is claimed is:

l. A method of transferring internal combustion en- 'gine produced heat for cooling said engine comprising the steps of:

transferring the engine generated heat to a coolant;

passing said heated coolant through a heat exchange means;

generating an air stream with a fan means;

drawing the air stream through the heat exchanger transferring heat thereto;

guiding the heated air stream from said heat exchanger to said fan with a shroud; and

expelling the heated air stream from the fan means over a contoured fan shroud configured to produce a Coanda effect directing the air stream generally radially outward, said fan shroud being positioned generally around said fan.

2. A method for dissipating internal combustion en gine produced heat comprising the steps of:

6 absorbing said heat in a liquid media; transporting heated liquid media to a heat exchanger means;

circulating said heated liquid media through said heat 5 exchanger;

generating an airstream with a fan means;

drawing the air stream through said heat exchanger to effect heat transfer thereb'etween and expelling the heated air from the fan means overa fan shroud configured to produce a Coanda effect directing the air stream generally radially outward, said fan shroud being positioned generally around said fan.

3. A method of moving air to dissipate the heat generated by a liquid cooled internal combustion engine such that a Coanda effect is achieved comprising the steps of:

passing liquid from said internal combustion engine through a heat exchanger means;

generating an air stream with a fan means;

drawing the air stream through the heat exchanger;

guiding the air stream from the heat exchanger to the fan means; and expelling the air stream from the fan over a contoured fan shroud configured to produce a Coanda effect directing the air stream generally radially outward, said fan shroud generally surrounding said fan. 4. A method of handling air for cooling a water jacketed internal combustion engine such that a Coanda effeet is achieved comprising the steps of:

generating an air stream with a fan means; drawing the air stream through a heat exchanger; guiding the air stream from said heat exchanger with a shroud means; and

expelling the air stream over a contoured fan shroud means configured to produce a Coanda effect directing said air stream generally radially outward.

5. A heat transfer system for an internal combustion engine comprising:

a heat exchanger including a front and a rear section:

a shroud having a forward section arranged to enclose said rear section of said heat exchanger, and a rearwardly extending unitary contoured exit sec tion including a cylindrical throat, radial expanding section and a radial flat portion; a'fan assembly including a plurality of fan blades having leading and trailing edges, said leading edges positioned adjacent said heat exchanger wherein the following relationship within plus or minus 12 percent ofAWexists: RF =AW/3, CF =AW/3, and R 2A W/3 where RF is the length of the radial flat portion, CF is the length of the cylindrical throat, R is the radius of the radial expanding section and AW is the projected axial width of the fan means whereby fan generated noise and horsepower requirements of said engine are reduced.

6. The heat transfer system of claim 5 wherein the trailing edge of said fan forms a plane parallel, plus or minus 12 percent, with said radial flat portion, whereby the fan induced stream ofair is converged and directed out parallel to the radial flat portion.

7. A heat transfer system for an internal combustion engine comprising:

a heat exchanger having a front and a rear section;

a shroud having a forward section arranged to enclose said rear section, and a rearwardly extending unitary contoured exit section including means defining a cylindrical throat, means defining a radial expanding section and a radial flat portion; I

a fan assembly including a plurality of fan blades each having a leading and a trailing edge, said leading edge being positioned adjacent said heat exchanger, wherein the following relationship exists: RF =AW/3, CF =AW/3, and R =2 A W/3 where RF is the length of the radial flat portion, CF is the length of the cylindrical throat, R is the radius of the radial expanding section and AW is the projected axial width of the fan whereby fan generated noise and horsepower requirements are reduced.

8. A cooling system for an internal combustion engine comprising:

a radiator including means defining a tube and means defining a rearward area; I

a shroud having a forward section arranged to include said rearward area of said radiator, and means defining a rearwardly extending unitary contoured exit section including a cylindrical throat, a radial expanding section and a radial flat portion;

a fan assembly including a plurality of fan blades each having leading and trailing edges, said leading edges being positioned adjacent said radiator, wherein the following relationship plus or minus 12 percent exists: RF =AW/3, CF =AW/3 and R 2 A W/3 where RF is the length of the radial flat portion, (F is the length ofthe cylindrical throat, R is the radius of the radial expanding section and AW is the projected axial width of the fan whereby the fan induced stream of air is converged and directed out generally parallel to the radial flat portion.

9. The cooling system of claim 8 wherein:

said radiator includes means defining a rearwardly extending perforated area;

said shroud enclosing said perforated area, and

said trailing edges of said fan blades are coextensive plus or minus 12 percent with said radial flat portion wherein the following relationship exists: RF AW/3, CF =AW/3, and R 2AW/3 wherev CF is the length of the cylindrical throat, R is the radius of the radial expanding section and AW is the projected axial width of the fan.

10. A vehicle having an operator station, an internal combustion engine, a radiator for cooling fluid from said engine an axial flow fan axially facing said radiator and including a plurality of angular blades drawing air rearwardly through said radiator, and a shroud rearwardly extending from said radiator wherein the improvement comprises:

a unitary shroud exit section closely surrounding said fan and extending in the same direction as said shroud including a tubular portion forming the leading edge thereof, an arcuate portion extending generally rearwardly and outwardly from said tubular portion and terminating in a flat flange portion forming the trailing edge of said shroud and lying in a plane perpendicular to said tubular portion, said fan disposed within at least a portion of said shroud exit section wherein the following relationship plus or minus 12 percent exists: RF=A W/3, CF=A W/3 and R=2 AW/3 where RF is the length of the flat flange portion, CF is the length ofthe tubular portion, R is the radius of the arcuate portion and A W is the projected axial width of the fan whereby fan generated noise and horsepower requirement of said engine are reduced.

11. The shroud exit section of claim 10 wherein said fan has a front plane which intersects said tubular portion and a rear plane which intersects, plus or minus 12 percent, said flat flange portion whereby a stream of air is converged and directed outwardly parallel to said flat flange portion to prevent the passage of dust and particle laden air against said engine, and engine heat against said operator station.

12. The shroud exit section of claim 11 wherein said tubular portion is secured to said shroud around the entire circumference thereof forming a junction section; and

said front plane struck out by said fan intersects said junction section.

13. A vehicle having an operator station and an internal combustion engine, a radiator for cooling fluid from said engine, an axial flow fan axially facing said radiator and including a plurality of angular blades drawing air rearwardly through said radiator, and a shroud rearwardly extending from said radiator wherein the im provementcomprises:

a unitary fan shroud exit portion secured to said shroud and extending rearwardly thereof including:

a cylindrical throat defining a leading edge, a midially expanding portion, and a radial flat portion defining a trailing edge; said fan being enclosed therein, said blade means defining a front plane coextensive with said leading edge wherein the following relationship exists: RF =A W/3, CF A W/3, and R =2 AW/3 where RF is the radial flat portion, CF is the cylindrical throat, R is the radius of the radial expanding section and AW is the projected axial width of the fan whereby fan generated noise and horsepower requirements ofsaid internal combustion engine are reduced.

14. The improvement of claim 13 wherein:

said fan shroud exit portion is secured to said shroud around its entire circumference; and

said blade means defines a rear plane, said plane being coextensive with said radial flat means plus or minus 12 percent.

Claims (14)

1. A method of transferring internal combustion engine produced heat for cooling said engine comprising the steps of: transferring the engine generated heat to a coolant; passing said heated coolant through a heat exchange means; generating an air stream with a fan means; drawing the air stream through the heat exchanger transferring heat thereto; guiding the heated air stream from said heat exchanger to said fan with a shroud; and expelling the heated air stream from the fan means over a contoured fan shroud configured to produce a Coanda effect directing the air stream generally radially outward, said fan shroud being positioned generally around said fan.
2. A method for dissipating internal combustion engine produced heat comprising the steps of: absorbing said heat in a liquid media; transporting heated liquid media to a heat exchanger means; circulating said heated liquid media through said heat exchanger; generating an air stream with a fan means; drawing the air stream through said heat exchanger to effect heat transfer therebetween and expelling the heated air from the fan means over a fan shroud configured to produce a Coanda effect directing the air stream generally radially outward, said fan shroud being positioned generally around said fan.
3. A method of moving air to dissipate the heat generated by a liquid cooled internal combustion engine such that a Coanda effect is achieved comprising the steps of: passing liquid from said internal combustion engine through a heat exchanger means; generating an air stream with a fan means; drawing the air stream through the heat exchanger; guiding the air stream from the heat exchanger to the fan means; and expelling the air stream from the fan over a contoured fan shroud configured to produce a Coanda effect directing The air stream generally radially outward, said fan shroud generally surrounding said fan.
4. A method of handling air for cooling a water jacketed internal combustion engine such that a Coanda effect is achieved comprising the steps of: generating an air stream with a fan means; drawing the air stream through a heat exchanger; guiding the air stream from said heat exchanger with a shroud means; and expelling the air stream over a contoured fan shroud means configured to produce a Coanda effect directing said air stream generally radially outward.
5. A heat transfer system for an internal combustion engine comprising: a heat exchanger including a front and a rear section; a shroud having a forward section arranged to enclose said rear section of said heat exchanger, and a rearwardly extending unitary contoured exit section including a cylindrical throat, radial expanding section and a radial flat portion; a fan assembly including a plurality of fan blades having leading and trailing edges, said leading edges positioned adjacent said heat exchanger wherein the following relationship within plus or minus 12 percent of AW exists: RF AW/3, CF AW/3, and R 2AW/3 where RF is the length of the radial flat portion, CF is the length of the cylindrical throat, R is the radius of the radial expanding section and AW is the projected axial width of the fan means whereby fan generated noise and horsepower requirements of said engine are reduced.
6. The heat transfer system of claim 5 wherein the trailing edge of said fan forms a plane parallel, plus or minus 12 percent, with said radial flat portion, whereby the fan induced stream of air is converged and directed out parallel to the radial flat portion.
7. A heat transfer system for an internal combustion engine comprising: a heat exchanger having a front and a rear section; a shroud having a forward section arranged to enclose said rear section, and a rearwardly extending unitary contoured exit section including means defining a cylindrical throat, means defining a radial expanding section and a radial flat portion; a fan assembly including a plurality of fan blades each having a leading and a trailing edge, said leading edge being positioned adjacent said heat exchanger, wherein the following relationship exists: RF AW/3, CF AW/3, and R 2 AW/3 where RF is the length of the radial flat portion, CF is the length of the cylindrical throat, R is the radius of the radial expanding section and AW is the projected axial width of the fan whereby fan generated noise and horsepower requirements are reduced.
8. A cooling system for an internal combustion engine comprising: a radiator including means defining a tube and means defining a rearward area; a shroud having a forward section arranged to include said rearward area of said radiator, and means defining a rearwardly extending unitary contoured exit section including a cylindrical throat, a radial expanding section and a radial flat portion; a fan assembly including a plurality of fan blades each having leading and trailing edges, said leading edges being positioned adjacent said radiator, wherein the following relationship plus or minus 12 percent exists: RF AW/3, CF AW/3 and R 2 AW/3 where RF is the length of the radial flat portion, CF is the length of the cylindrical throat, R is the radius of the radial expanding section and AW is the projected axial width of the fan whereby the fan induced stream of air is converged and directed out generally parallel to the radial flat portion.
9. The cooling system of claim 8 wherein: said radiator includes means defining a rearwardly extending perforated area; said shroud enclosinG said perforated area, and said trailing edges of said fan blades are coextensive plus or minus 12 percent with said radial flat portion wherein the following relationship exists: RF AW/3, CF AW/3, and R 2AW/3 where CF is the length of the cylindrical throat, R is the radius of the radial expanding section and AW is the projected axial width of the fan.
10. A vehicle having an operator station, an internal combustion engine, a radiator for cooling fluid from said engine an axial flow fan axially facing said radiator and including a plurality of angular blades drawing air rearwardly through said radiator, and a shroud rearwardly extending from said radiator wherein the improvement comprises: a unitary shroud exit section closely surrounding said fan and extending in the same direction as said shroud including a tubular portion forming the leading edge thereof, an arcuate portion extending generally rearwardly and outwardly from said tubular portion and terminating in a flat flange portion forming the trailing edge of said shroud and lying in a plane perpendicular to said tubular portion, said fan disposed within at least a portion of said shroud exit section wherein the following relationship plus or minus 12 percent exists: RF AW/3, CF AW/3 and R 2 AW/3 where RF is the length of the flat flange portion, CF is the length of the tubular portion, R is the radius of the arcuate portion and AW is the projected axial width of the fan whereby fan generated noise and horsepower requirement of said engine are reduced.
11. The shroud exit section of claim 10 wherein said fan has a front plane which intersects said tubular portion and a rear plane which intersects, plus or minus 12 percent, said flat flange portion whereby a stream of air is converged and directed outwardly parallel to said flat flange portion to prevent the passage of dust and particle laden air against said engine, and engine heat against said operator station.
12. The shroud exit section of claim 11 wherein said tubular portion is secured to said shroud around the entire circumference thereof forming a junction section; and said front plane struck out by said fan intersects said junction section.
13. A vehicle having an operator station and an internal combustion engine, a radiator for cooling fluid from said engine, an axial flow fan axially facing said radiator and including a plurality of angular blades drawing air rearwardly through said radiator, and a shroud rearwardly extending from said radiator wherein the improvement comprises: a unitary fan shroud exit portion secured to said shroud and extending rearwardly thereof including; a cylindrical throat defining a leading edge, a radially expanding portion, and a radial flat portion defining a trailing edge; said fan being enclosed therein, said blade means defining a front plane coextensive with said leading edge wherein the following relationship exists: RF AW/3, CF AW/3, and R 2 AW/3 where RF is the radial flat portion, CF is the cylindrical throat, R is the radius of the radial expanding section and AW is the projected axial width of the fan whereby fan generated noise and horsepower requirements of said internal combustion engine are reduced.
14. The improvement of claim 13 wherein: said fan shroud exit portion is secured to said shroud around its entire circumference; and said blade means defines a rear plane, said plane being coextensive with said radial flat means plus or minus 12 percent.
US34843673 1973-04-05 1973-04-05 Fan shroud exit structure Expired - Lifetime US3872916A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US34843673 US3872916A (en) 1973-04-05 1973-04-05 Fan shroud exit structure

Applications Claiming Priority (11)

Application Number Priority Date Filing Date Title
US34843673 US3872916A (en) 1973-04-05 1973-04-05 Fan shroud exit structure
CA184,880A CA992409A (en) 1973-04-05 1973-11-02 Fan shroud exit structure
DE19742411225 DE2411225C3 (en) 1973-04-05 1974-03-08
FR7411223A FR2224318B1 (en) 1973-04-05 1974-03-29
SE7404430A SE402322B (en) 1973-04-05 1974-04-02 For motor vehicles intended vermeoverforingsanordning
NL7404587A NL158255B (en) 1973-04-05 1974-04-03 Vehicle, provided with a radiator, a fan, and one of the radiator in order to running the fan casing.
JP3777174A JPS49129032A (en) 1973-04-05 1974-04-03
IT5004074A IT1004094B (en) 1973-04-05 1974-04-03 Improvement in nozzles for radiators for motor vehicles
BR268574A BR7402685D0 (en) 1973-04-05 1974-04-04 System heat dissipation and perfecter refrigeration and vehicle using the same
AU6756574A AU471444B2 (en) 1973-04-05 1974-04-04
GB1515174A GB1466795A (en) 1973-04-05 1974-04-05 Fan and cowl assembly in a vehicle

Publications (1)

Publication Number Publication Date
US3872916A true US3872916A (en) 1975-03-25

Family

ID=23368047

Family Applications (1)

Application Number Title Priority Date Filing Date
US34843673 Expired - Lifetime US3872916A (en) 1973-04-05 1973-04-05 Fan shroud exit structure

Country Status (11)

Country Link
US (1) US3872916A (en)
JP (1) JPS49129032A (en)
AU (1) AU471444B2 (en)
BR (1) BR7402685D0 (en)
CA (1) CA992409A (en)
DE (1) DE2411225C3 (en)
FR (1) FR2224318B1 (en)
GB (1) GB1466795A (en)
IT (1) IT1004094B (en)
NL (1) NL158255B (en)
SE (1) SE402322B (en)

Cited By (79)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4173995A (en) * 1975-02-24 1979-11-13 International Harvester Company Recirculation barrier for a heat transfer system
US4180130A (en) * 1974-05-22 1979-12-25 International Harvester Company Heat exchange apparatus including a toroidal-type radiator
US4184541A (en) * 1974-05-22 1980-01-22 International Harvester Company Heat exchange apparatus including a toroidal-type radiator
US5143516A (en) * 1989-02-06 1992-09-01 Paccar Inc. Recirculation shield and fan shroud assembly
ES2052431A2 (en) * 1991-02-11 1994-07-01 Carrier Corp Orifice structure and fan cover for enclosure of an air conditioning system.
EP0645543A1 (en) * 1993-08-31 1995-03-29 Caterpillar Inc. Low noise cooling system
US20070036648A1 (en) * 2005-08-11 2007-02-15 York International Corporation Extended venturi fan ring
US20070224044A1 (en) * 2006-03-27 2007-09-27 Valeo, Inc. Cooling fan using coanda effect to reduce recirculation
US20080196678A1 (en) * 2004-11-04 2008-08-21 Naoya Kakishita Radiator-Shroud Structure
US20100226769A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan assembly
US20100226758A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan assembly
US20100226787A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan assembly
US20100226751A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan assembly
US20100226752A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan assembly
US20100226764A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan
US20100226754A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan assembly
US20100226753A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan assembly
US20100226763A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan assembly
US20100225012A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Humidifying apparatus
US20100226749A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan assembly
US20110058935A1 (en) * 2007-09-04 2011-03-10 Dyson Technology Limited Fan
US20110110805A1 (en) * 2009-11-06 2011-05-12 Dyson Technology Limited Fan
US20110164959A1 (en) * 2008-09-23 2011-07-07 Dyson Technology Limited Fan
US20110236229A1 (en) * 2010-03-23 2011-09-29 Dyson Technology Limited Accessory for a fan
US8308432B2 (en) 2009-03-04 2012-11-13 Dyson Technology Limited Fan assembly
US20120307440A1 (en) * 2010-02-26 2012-12-06 Franz John P Mixed-flow ducted fan
US8348596B2 (en) 2009-03-04 2013-01-08 Dyson Technology Limited Fan assembly
US8366403B2 (en) 2010-08-06 2013-02-05 Dyson Technology Limited Fan assembly
US8714937B2 (en) 2009-03-04 2014-05-06 Dyson Technology Limited Fan assembly
US8734094B2 (en) 2010-08-06 2014-05-27 Dyson Technology Limited Fan assembly
US20140165933A1 (en) * 2012-12-19 2014-06-19 Andrew E. Weiss Duct for engine bay cooling and ventilation
US8784071B2 (en) 2009-03-04 2014-07-22 Dyson Technology Limited Fan assembly
US8873940B2 (en) 2010-08-06 2014-10-28 Dyson Technology Limited Fan assembly
US8882451B2 (en) 2010-03-23 2014-11-11 Dyson Technology Limited Fan
US8894354B2 (en) 2010-09-07 2014-11-25 Dyson Technology Limited Fan
US8967980B2 (en) 2010-10-18 2015-03-03 Dyson Technology Limited Fan assembly
US8967979B2 (en) 2010-10-18 2015-03-03 Dyson Technology Limited Fan assembly
US9011116B2 (en) 2010-05-27 2015-04-21 Dyson Technology Limited Device for blowing air by means of a nozzle assembly
USD728092S1 (en) 2013-08-01 2015-04-28 Dyson Technology Limited Fan
USD728769S1 (en) 2013-08-01 2015-05-05 Dyson Technology Limited Fan
USD728770S1 (en) 2013-08-01 2015-05-05 Dyson Technology Limited Fan
USD729376S1 (en) 2013-03-07 2015-05-12 Dyson Technology Limited Fan
USD729375S1 (en) 2013-03-07 2015-05-12 Dyson Technology Limited Fan
USD729374S1 (en) 2013-03-07 2015-05-12 Dyson Technology Limited Fan
USD729373S1 (en) 2013-03-07 2015-05-12 Dyson Technology Limited Fan
USD729372S1 (en) 2013-03-07 2015-05-12 Dyson Technology Limited Fan
USD729925S1 (en) 2013-03-07 2015-05-19 Dyson Technology Limited Fan
US9127855B2 (en) 2011-07-27 2015-09-08 Dyson Technology Limited Fan assembly
US9151299B2 (en) 2012-02-06 2015-10-06 Dyson Technology Limited Fan
USD746425S1 (en) 2013-01-18 2015-12-29 Dyson Technology Limited Humidifier
USD746966S1 (en) 2013-01-18 2016-01-05 Dyson Technology Limited Humidifier
USD747450S1 (en) 2013-01-18 2016-01-12 Dyson Technology Limited Humidifier
US9249809B2 (en) 2012-02-06 2016-02-02 Dyson Technology Limited Fan
USD749231S1 (en) 2013-01-18 2016-02-09 Dyson Technology Limited Humidifier
US9283573B2 (en) 2012-02-06 2016-03-15 Dyson Technology Limited Fan assembly
US9328739B2 (en) 2012-01-19 2016-05-03 Dyson Technology Limited Fan
US9366449B2 (en) 2012-03-06 2016-06-14 Dyson Technology Limited Humidifying apparatus
US9410711B2 (en) 2013-09-26 2016-08-09 Dyson Technology Limited Fan assembly
US9458853B2 (en) 2011-07-27 2016-10-04 Dyson Technology Limited Fan assembly
US9568021B2 (en) 2012-05-16 2017-02-14 Dyson Technology Limited Fan
US9568006B2 (en) 2012-05-16 2017-02-14 Dyson Technology Limited Fan
US9599356B2 (en) 2014-07-29 2017-03-21 Dyson Technology Limited Humidifying apparatus
US9732763B2 (en) 2012-07-11 2017-08-15 Dyson Technology Limited Fan assembly
US9745981B2 (en) 2011-11-11 2017-08-29 Dyson Technology Limited Fan assembly
US9745996B2 (en) 2010-12-02 2017-08-29 Dyson Technology Limited Fan
US9752789B2 (en) 2012-03-06 2017-09-05 Dyson Technology Limited Humidifying apparatus
US9797613B2 (en) 2012-03-06 2017-10-24 Dyson Technology Limited Humidifying apparatus
US9797414B2 (en) 2013-07-09 2017-10-24 Dyson Technology Limited Fan assembly
US9797612B2 (en) 2013-01-29 2017-10-24 Dyson Technology Limited Fan assembly
EP1890042B1 (en) * 2006-08-07 2017-11-08 Deere & Company Fan variable immersion system
US9816531B2 (en) 2008-10-25 2017-11-14 Dyson Technology Limited Fan utilizing coanda surface
US9822778B2 (en) 2012-04-19 2017-11-21 Dyson Technology Limited Fan assembly
US9903602B2 (en) 2014-07-29 2018-02-27 Dyson Technology Limited Humidifying apparatus
US9926804B2 (en) 2010-11-02 2018-03-27 Dyson Technology Limited Fan assembly
US9927136B2 (en) 2012-03-06 2018-03-27 Dyson Technology Limited Fan assembly
US9982677B2 (en) 2014-07-29 2018-05-29 Dyson Technology Limited Fan assembly
US10094392B2 (en) 2011-11-24 2018-10-09 Dyson Technology Limited Fan assembly
US10100836B2 (en) 2010-10-13 2018-10-16 Dyson Technology Limited Fan assembly
US10145583B2 (en) 2012-04-04 2018-12-04 Dyson Technology Limited Heating apparatus

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3304297C2 (en) * 1982-03-15 1988-05-26 Sueddeutsche Kuehlerfabrik Julius Fr. Behr Gmbh & Co Kg, 7000 Stuttgart, De
DE102006037641B4 (en) * 2006-08-10 2019-04-04 Mahle International Gmbh Cooler set for a motor vehicle with a coolant condenser and axial fan
DE102010003635A1 (en) * 2010-04-01 2011-10-06 Behr Gmbh & Co. Kg Cooling air flow

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1519812A (en) * 1923-06-04 1924-12-16 Schneider Heinrich Locomotive driven by internal-combustion engine
US1691598A (en) * 1925-08-23 1928-11-13 Sulzer Ag Internal-combustion-engine locomotive
US1966787A (en) * 1931-03-27 1934-07-17 Sulzer Ag Cooling fan for vehicles driven by internal combustion engines
US2142307A (en) * 1934-06-14 1939-01-03 Mey Rene De Mounting of axial flow fans and the like
US2415621A (en) * 1944-10-20 1947-02-11 Solar Aircraft Co Fan
US2544490A (en) * 1949-07-07 1951-03-06 Jeffrey Mfg Co Adjustable cowling for fans or the like
US2664961A (en) * 1947-10-24 1954-01-05 Joy Mfg Co Adjustable blade fan
US2668523A (en) * 1952-12-11 1954-02-09 Chrysler Corp Fan shroud
US3144859A (en) * 1962-02-15 1964-08-18 Young Radiator Co Fan-shroud structure and mounting

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1374901A (en) * 1917-02-05 1921-04-19 Allis Chalmers Mfg Co Cooling system
DE653227C (en) * 1935-05-17 1937-11-18 Daimler Benz Ag Kuehlvorrichtung for internal combustion engines, particularly for motor vehicles
DE966674C (en) * 1950-12-13 1957-08-29 Wilhelm Elze Cooling device for power plants, in particular vehicle engines
DE1108721B (en) * 1957-02-08 1961-06-15 Voith Gmbh J M For railway traction vehicles with an internal combustion engine cooling installation specific
US2988404A (en) * 1958-10-20 1961-06-13 Young Radiator Co Adjustable power drive
AT225554B (en) * 1959-11-28 1963-01-25 Auto Union Gmbh Air guide box between a cooling fan and a cooler for motor vehicles

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1519812A (en) * 1923-06-04 1924-12-16 Schneider Heinrich Locomotive driven by internal-combustion engine
US1691598A (en) * 1925-08-23 1928-11-13 Sulzer Ag Internal-combustion-engine locomotive
US1966787A (en) * 1931-03-27 1934-07-17 Sulzer Ag Cooling fan for vehicles driven by internal combustion engines
US2142307A (en) * 1934-06-14 1939-01-03 Mey Rene De Mounting of axial flow fans and the like
US2415621A (en) * 1944-10-20 1947-02-11 Solar Aircraft Co Fan
US2664961A (en) * 1947-10-24 1954-01-05 Joy Mfg Co Adjustable blade fan
US2544490A (en) * 1949-07-07 1951-03-06 Jeffrey Mfg Co Adjustable cowling for fans or the like
US2668523A (en) * 1952-12-11 1954-02-09 Chrysler Corp Fan shroud
US3144859A (en) * 1962-02-15 1964-08-18 Young Radiator Co Fan-shroud structure and mounting

Cited By (115)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4180130A (en) * 1974-05-22 1979-12-25 International Harvester Company Heat exchange apparatus including a toroidal-type radiator
US4184541A (en) * 1974-05-22 1980-01-22 International Harvester Company Heat exchange apparatus including a toroidal-type radiator
US4173995A (en) * 1975-02-24 1979-11-13 International Harvester Company Recirculation barrier for a heat transfer system
US5143516A (en) * 1989-02-06 1992-09-01 Paccar Inc. Recirculation shield and fan shroud assembly
ES2052431A2 (en) * 1991-02-11 1994-07-01 Carrier Corp Orifice structure and fan cover for enclosure of an air conditioning system.
EP0645543A1 (en) * 1993-08-31 1995-03-29 Caterpillar Inc. Low noise cooling system
US20080196678A1 (en) * 2004-11-04 2008-08-21 Naoya Kakishita Radiator-Shroud Structure
US20070036648A1 (en) * 2005-08-11 2007-02-15 York International Corporation Extended venturi fan ring
US7481619B2 (en) 2005-08-11 2009-01-27 York International Corporation Extended venturi fan ring
US7478993B2 (en) 2006-03-27 2009-01-20 Valeo, Inc. Cooling fan using Coanda effect to reduce recirculation
US20070224044A1 (en) * 2006-03-27 2007-09-27 Valeo, Inc. Cooling fan using coanda effect to reduce recirculation
EP1890042B1 (en) * 2006-08-07 2017-11-08 Deere & Company Fan variable immersion system
US20110058935A1 (en) * 2007-09-04 2011-03-10 Dyson Technology Limited Fan
US20110223015A1 (en) * 2007-09-04 2011-09-15 Dyson Technology Limited Fan
US8403650B2 (en) 2007-09-04 2013-03-26 Dyson Technology Limited Fan
US8764412B2 (en) 2007-09-04 2014-07-01 Dyson Technology Limited Fan
US8348629B2 (en) 2008-09-23 2013-01-08 Dyston Technology Limited Fan
US20110164959A1 (en) * 2008-09-23 2011-07-07 Dyson Technology Limited Fan
US10145388B2 (en) 2008-10-25 2018-12-04 Dyson Technology Limited Fan with a filter
US9816531B2 (en) 2008-10-25 2017-11-14 Dyson Technology Limited Fan utilizing coanda surface
US8348597B2 (en) 2009-03-04 2013-01-08 Dyson Technology Limited Fan assembly
US20100226749A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan assembly
US20100225012A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Humidifying apparatus
US9513028B2 (en) * 2009-03-04 2016-12-06 Dyson Technology Limited Fan assembly
US20100226763A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan assembly
US20100226753A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan assembly
US9599368B2 (en) 2009-03-04 2017-03-21 Dyson Technology Limited Nozzle for bladeless fan assembly with heater
US8308432B2 (en) 2009-03-04 2012-11-13 Dyson Technology Limited Fan assembly
US8932028B2 (en) 2009-03-04 2015-01-13 Dyson Technology Limited Fan assembly
US8348596B2 (en) 2009-03-04 2013-01-08 Dyson Technology Limited Fan assembly
US20100226754A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan assembly
US20100226764A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan
US8356804B2 (en) 2009-03-04 2013-01-22 Dyson Technology Limited Humidifying apparatus
US20100226752A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan assembly
US8403640B2 (en) 2009-03-04 2013-03-26 Dyson Technology Limited Fan assembly
US9127689B2 (en) 2009-03-04 2015-09-08 Dyson Technology Limited Fan assembly
US8408869B2 (en) 2009-03-04 2013-04-02 Dyson Technology Limited Fan assembly
US8430624B2 (en) 2009-03-04 2013-04-30 Dyson Technology Limited Fan assembly
US10221860B2 (en) 2009-03-04 2019-03-05 Dyson Technology Limited Fan assembly
US8469660B2 (en) 2009-03-04 2013-06-25 Dyson Technology Limited Fan assembly
US8469658B2 (en) 2009-03-04 2013-06-25 Dyson Technology Limited Fan
US8469655B2 (en) 2009-03-04 2013-06-25 Dyson Technology Limited Fan assembly
US8529203B2 (en) 2009-03-04 2013-09-10 Dyson Technology Limited Fan assembly
US8613601B2 (en) 2009-03-04 2013-12-24 Dyson Technology Limited Fan assembly
US20100226751A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan assembly
US8684687B2 (en) 2009-03-04 2014-04-01 Dyson Technology Limited Fan assembly
US8708650B2 (en) 2009-03-04 2014-04-29 Dyson Technology Limited Fan assembly
US8714937B2 (en) 2009-03-04 2014-05-06 Dyson Technology Limited Fan assembly
US20100226787A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan assembly
US10006657B2 (en) 2009-03-04 2018-06-26 Dyson Technology Limited Fan assembly
US20100226758A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan assembly
US20100226769A1 (en) * 2009-03-04 2010-09-09 Dyson Technology Limited Fan assembly
US8784049B2 (en) 2009-03-04 2014-07-22 Dyson Technology Limited Fan
US8784071B2 (en) 2009-03-04 2014-07-22 Dyson Technology Limited Fan assembly
US8783663B2 (en) 2009-03-04 2014-07-22 Dyson Technology Limited Humidifying apparatus
US8721286B2 (en) 2009-03-04 2014-05-13 Dyson Technology Limited Fan assembly
US9004878B2 (en) 2009-11-06 2015-04-14 Dyson Technology Limited Fan having a magnetically attached remote control
US8454322B2 (en) 2009-11-06 2013-06-04 Dyson Technology Limited Fan having a magnetically attached remote control
US20110110805A1 (en) * 2009-11-06 2011-05-12 Dyson Technology Limited Fan
US8649171B2 (en) * 2010-02-26 2014-02-11 Hewlett-Packard Development Company, L.P. Mixed-flow ducted fan
US20120307440A1 (en) * 2010-02-26 2012-12-06 Franz John P Mixed-flow ducted fan
US20110236229A1 (en) * 2010-03-23 2011-09-29 Dyson Technology Limited Accessory for a fan
US8770946B2 (en) 2010-03-23 2014-07-08 Dyson Technology Limited Accessory for a fan
US8882451B2 (en) 2010-03-23 2014-11-11 Dyson Technology Limited Fan
US9011116B2 (en) 2010-05-27 2015-04-21 Dyson Technology Limited Device for blowing air by means of a nozzle assembly
US8734094B2 (en) 2010-08-06 2014-05-27 Dyson Technology Limited Fan assembly
US8366403B2 (en) 2010-08-06 2013-02-05 Dyson Technology Limited Fan assembly
US8873940B2 (en) 2010-08-06 2014-10-28 Dyson Technology Limited Fan assembly
US9745988B2 (en) 2010-09-07 2017-08-29 Dyson Technology Limited Fan
US8894354B2 (en) 2010-09-07 2014-11-25 Dyson Technology Limited Fan
US10100836B2 (en) 2010-10-13 2018-10-16 Dyson Technology Limited Fan assembly
US8967979B2 (en) 2010-10-18 2015-03-03 Dyson Technology Limited Fan assembly
US8967980B2 (en) 2010-10-18 2015-03-03 Dyson Technology Limited Fan assembly
US9926804B2 (en) 2010-11-02 2018-03-27 Dyson Technology Limited Fan assembly
US9745996B2 (en) 2010-12-02 2017-08-29 Dyson Technology Limited Fan
US9127855B2 (en) 2011-07-27 2015-09-08 Dyson Technology Limited Fan assembly
US9291361B2 (en) 2011-07-27 2016-03-22 Dyson Technology Limited Fan assembly
US10094581B2 (en) 2011-07-27 2018-10-09 Dyson Technology Limited Fan assembly
US9458853B2 (en) 2011-07-27 2016-10-04 Dyson Technology Limited Fan assembly
US9335064B2 (en) 2011-07-27 2016-05-10 Dyson Technology Limited Fan assembly
US9745981B2 (en) 2011-11-11 2017-08-29 Dyson Technology Limited Fan assembly
US10094392B2 (en) 2011-11-24 2018-10-09 Dyson Technology Limited Fan assembly
US9328739B2 (en) 2012-01-19 2016-05-03 Dyson Technology Limited Fan
US9283573B2 (en) 2012-02-06 2016-03-15 Dyson Technology Limited Fan assembly
US9151299B2 (en) 2012-02-06 2015-10-06 Dyson Technology Limited Fan
US9249809B2 (en) 2012-02-06 2016-02-02 Dyson Technology Limited Fan
US9752789B2 (en) 2012-03-06 2017-09-05 Dyson Technology Limited Humidifying apparatus
US9366449B2 (en) 2012-03-06 2016-06-14 Dyson Technology Limited Humidifying apparatus
US9797613B2 (en) 2012-03-06 2017-10-24 Dyson Technology Limited Humidifying apparatus
US9927136B2 (en) 2012-03-06 2018-03-27 Dyson Technology Limited Fan assembly
US10145583B2 (en) 2012-04-04 2018-12-04 Dyson Technology Limited Heating apparatus
US9822778B2 (en) 2012-04-19 2017-11-21 Dyson Technology Limited Fan assembly
US9568006B2 (en) 2012-05-16 2017-02-14 Dyson Technology Limited Fan
US9568021B2 (en) 2012-05-16 2017-02-14 Dyson Technology Limited Fan
US9732763B2 (en) 2012-07-11 2017-08-15 Dyson Technology Limited Fan assembly
US20140165933A1 (en) * 2012-12-19 2014-06-19 Andrew E. Weiss Duct for engine bay cooling and ventilation
USD749231S1 (en) 2013-01-18 2016-02-09 Dyson Technology Limited Humidifier
USD747450S1 (en) 2013-01-18 2016-01-12 Dyson Technology Limited Humidifier
USD746966S1 (en) 2013-01-18 2016-01-05 Dyson Technology Limited Humidifier
USD746425S1 (en) 2013-01-18 2015-12-29 Dyson Technology Limited Humidifier
US9797612B2 (en) 2013-01-29 2017-10-24 Dyson Technology Limited Fan assembly
USD729376S1 (en) 2013-03-07 2015-05-12 Dyson Technology Limited Fan
USD729375S1 (en) 2013-03-07 2015-05-12 Dyson Technology Limited Fan
USD729372S1 (en) 2013-03-07 2015-05-12 Dyson Technology Limited Fan
USD729374S1 (en) 2013-03-07 2015-05-12 Dyson Technology Limited Fan
USD729925S1 (en) 2013-03-07 2015-05-19 Dyson Technology Limited Fan
USD729373S1 (en) 2013-03-07 2015-05-12 Dyson Technology Limited Fan
US9797414B2 (en) 2013-07-09 2017-10-24 Dyson Technology Limited Fan assembly
USD728769S1 (en) 2013-08-01 2015-05-05 Dyson Technology Limited Fan
USD728092S1 (en) 2013-08-01 2015-04-28 Dyson Technology Limited Fan
USD728770S1 (en) 2013-08-01 2015-05-05 Dyson Technology Limited Fan
US9410711B2 (en) 2013-09-26 2016-08-09 Dyson Technology Limited Fan assembly
US9903602B2 (en) 2014-07-29 2018-02-27 Dyson Technology Limited Humidifying apparatus
US9982677B2 (en) 2014-07-29 2018-05-29 Dyson Technology Limited Fan assembly
US9599356B2 (en) 2014-07-29 2017-03-21 Dyson Technology Limited Humidifying apparatus

Also Published As

Publication number Publication date
FR2224318B1 (en) 1979-02-16
GB1466795A (en) 1977-03-09
JPS49129032A (en) 1974-12-10
CA992409A1 (en)
DE2411225A1 (en) 1974-10-24
AU471444B2 (en) 1976-04-29
SE402322B (en) 1978-06-26
NL7404587A (en) 1974-10-08
DE2411225C3 (en) 1981-08-20
AU6756574A (en) 1975-10-09
DE2411225B2 (en) 1976-07-01
BR7402685D0 (en) 1974-11-19
IT1004094B (en) 1976-07-10
NL158255B (en) 1978-10-16
CA992409A (en) 1976-07-06
FR2224318A1 (en) 1974-10-31

Similar Documents

Publication Publication Date Title
US6863496B2 (en) Fan and shroud assembly
US4169501A (en) Airflow regulating apparatus for radiator
US5183382A (en) Low noise rotating fan and shroud assembly
JP4149655B2 (en) Self-cooling motor with axis fan
JP4964390B2 (en) Automotive fan apparatus having a projecting shroud and fan that matches the wing tip
US6749043B2 (en) Locomotive brake resistor cooling apparatus
CN1299011C (en) Inflow-adapted axial-flow fan
US3742705A (en) Thermal response shroud for rotating body
US7484925B2 (en) Rotary axial fan assembly
US4548548A (en) Fan and housing
EP0026997A1 (en) Shroud arrangement for engine cooling fan
US4836148A (en) Shrouding for engine cooling fans
US4840541A (en) Fan apparatus
KR0142413B1 (en) Fan stator assembly for a heat exchanger
US4685513A (en) Engine cooling fan and fan shrouding arrangement
EP0834022B2 (en) Axial fan assembly
US4396351A (en) Engine cooling fan
US6219242B1 (en) Apparatus for cooling a heat producing member
US4059080A (en) Engine compartment ventilating arrangement
US6951240B2 (en) Heat exchanger package
US7108482B2 (en) Centrifugal blower
US4398508A (en) Engine cooling fan construction
US5590624A (en) Engine cooling systems
US3937192A (en) Ejector fan shroud arrangement
US5881685A (en) Fan shroud with integral air supply

Legal Events

Date Code Title Description
AS Assignment

Owner name: FIDELITY UNION BANK, TRUSTEE

Free format text: SECURITY INTEREST;ASSIGNOR:INTERNATIONAL HARVESTER COMPANY;REEL/FRAME:003970/0963

Effective date: 19811101

Owner name: PATTERSON, LINDA L., TRUSTEE

Free format text: SECURITY INTEREST;ASSIGNOR:INTERNATIONAL HARVESTER COMPANY;REEL/FRAME:003970/0963

Effective date: 19811101

Owner name: FIDELITY UNION BANK, TRUSTEE, ILLINOIS

Free format text: SECURITY INTEREST;ASSIGNOR:INTERNATIONAL HARVESTER COMPANY;REEL/FRAME:003970/0963

Effective date: 19811101

Owner name: PATTERSON, LINDA L., TRUSTEE, ILLINOIS

Free format text: SECURITY INTEREST;ASSIGNOR:INTERNATIONAL HARVESTER COMPANY;REEL/FRAME:003970/0963

Effective date: 19811101

AS Assignment

Owner name: INTERNATIONAL HARVESTER COMPANY, 401 NORTH MICHIGA

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:FIRST FIDELTY BANK, NATIONAL ASSOCIATION PATTERSON, LINDA L.; TRUSTEES;REEL/FRAME:004357/0949

Effective date: 19850131

AS Assignment

Owner name: J.I. CASE COMPANY A DE CORP

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:INTERNATIONAL HARVESTER COMPANY A DE CORP;REEL/FRAME:004379/0536

Effective date: 19850131

AS Assignment

Owner name: CASE CORPORATION, A CORP. OF DELAWARE

Free format text: CHANGE OF NAME;ASSIGNOR:J. I. CASE COMPANY, A CORP. OF DELAWARE;REEL/FRAME:005741/0138

Effective date: 19891229