WO1982002575A1 - Buse pour pulverisation controlee - Google Patents

Buse pour pulverisation controlee Download PDF

Info

Publication number
WO1982002575A1
WO1982002575A1 PCT/US1981/000092 US8100092W WO8202575A1 WO 1982002575 A1 WO1982002575 A1 WO 1982002575A1 US 8100092 W US8100092 W US 8100092W WO 8202575 A1 WO8202575 A1 WO 8202575A1
Authority
WO
WIPO (PCT)
Prior art keywords
nozzle assembly
passage
passages
liquid
velocity
Prior art date
Application number
PCT/US1981/000092
Other languages
English (en)
Inventor
Tractor Co Caterpillar
Original Assignee
Clairmont Floyd H Jr
Graze Russell R Jr
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
Priority to JP50020680A priority Critical patent/JPS57502220A/ja
Application filed by Clairmont Floyd H Jr, Graze Russell R Jr filed Critical Clairmont Floyd H Jr
Priority to PCT/US1981/000092 priority patent/WO1982002575A1/fr
Priority to BR8108955A priority patent/BR8108955A/pt
Priority to CA000391213A priority patent/CA1167886A/fr
Priority to EP19810305805 priority patent/EP0057790B1/fr
Priority to DE8181305805T priority patent/DE3170439D1/de
Publication of WO1982002575A1 publication Critical patent/WO1982002575A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/14—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means with multiple outlet openings; with strainers in or outside the outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/06—Arrangements for cooling pistons
    • F01P3/08—Cooling of piston exterior only, e.g. by jets

Definitions

  • This invention relates generally to a nozzle assembly for controllably spraying a liquid in a substantially columnar form and, more particularly, to a nozzle assembly for spraying a stream of cooling liquid into a reciprocating piston passage.
  • a nozzle In using a nozzle to spray a liquid, the pattern of the stream leaving the nozzle is important to assure that the liquid is delivered to the precise location desired.
  • a nozzle is commonly used to spray a cooling liquid such as engine oil upwardly against the piston as it reciprocates in order to cool it.
  • the oil In longer stroke engines particularly, the oil must be sprayed a relatively long distance toward the piston v/hen it is at its top dead center position.
  • the pattern of the spray is therefore important so that the oil reaches the desired portion of the piston for direct cooling. The oil can then drip or be deflected downwardly to cool the remaining portion of the piston.
  • the nozzles in such engines have utilized a single opening having a sufficiently large cross-sectional area to deliver the desired volume of oil for a given period of time.
  • it tends to spread out or have an excessively wide spray pattern. This reduces the effectiveness of the cooling oil in that sufficient amounts do not reach the piston crown area.
  • the present invention is directed to overcoming one or more of the problems as set forth above.
  • a nozzle assembly for controllably spraying a liquid in a columnar form has substantially axially aligned inlet and outlet portions, with the inlet portion defining an opening therethrough.
  • First passage means is provided for communicating a first liquid flow from the opening through the outlet portion and outwardly thereof at a first velocity
  • second passage means is provided for communicating a second liquid flow from the opening through the outlet portion and outwardly thereof along a plurality of paths generally encircling the first passage means and individually having a second velocity less than the first velocity.
  • a nozzle assembly is provided for controllably spraying a cooling liquid toward a reciprocating engine piston in a precise spray pattern.
  • a straight passage is defined in the piston leading to an upper cooling chamber, and the nozzle assembly controllably sprays the cooling liquid in a columnar form into the passage and thereby to the chamber.
  • a method for spraying a liquid from a nozzle assembly. The steps of the method include initiating liquid flow through an opening in an inlet portion of the nozzle assembly, and controlling the liquid flow from the inlet portion at an outlet portion defining a primary, centrally located passage and a plurality of secondary, peripherally located passages such that the liquid exits from the primary passage at a first velocity and from the secondary passages at a second velocity to maintain a columnar spray pattern.
  • the liquid spray pattern of the present nozzle assembly is maintained in a columnar form rather than being widely dispersed. This is achieved by providing different liquid flow paths, such as centrally from a primary outlet passage and peripherally from a plurality of secondary outlet passages which cooperate to maintain the spraying pattern relatively compact and free from such dispersing effects.
  • Fig. 1 is a diagrammatic elevational view of an engine with a portion broken open and sectioned showing one embodiment of the nozzle assembly of the present invention for spraying a cooling liquid in columnar form into a passage in a piston of the engine;
  • Fig. 2 is a diagrammatic and greatly enlarged cross-sectional view of the nozzle assembly of Fig. 1;
  • Fig. 3 is a diagrammatic, outlet end elevational view of the nozzle assembly taken along line III-III of Fig. 2.
  • a nozzle assembly 10 is shown associated with an internal combustion engine 12.
  • the engine has a block 14 in which a cylinder liner 16 is carried.
  • a piston 18 is positioned in the cylinder liner and reciprocates, as is known in the art, within the cylinder liner.
  • the block 14 has a passageway 20, and a liquid distribution manifold 22 is releasably connected to the block in communication with the passageway.
  • the nozzle assembly 10 receives a cooling liquid, such as engine oil, under pressure from the passageway and the manifold, which is then sprayed upwardly toward the piston as it reciprocates in a liquid column as is illustrated and identified by the letter "A".
  • the piston 18 has a profiled downwardly facing and stepped opening 24 and a straight passage 26 connected to the opening which extends upwardly to an internal annular chamber 28 located at the crown area thereof.
  • a plurality of generally radially extending passages 30 serve to communicate cooling liquid in the annular chamber with a centrally disposed cavity 32. From the cavity the liquid can descend by gravity through a central port 34 to the region of the connection between the connecting rod 36 and pin 38 for lubrication thereof.
  • the nozzle assembly 10 generally includes an inlet portion 40 and an outlet portion 42 releasably secured thereon.
  • the inlet portion is an integral outlet part of the manifold 22 and has a substantially cylindrical inner wall 44 at the outlet thereof defining an opening 46 through which the cooling liquid flows generally along a first central axis 48 .
  • the inlet portion further has external connecting threads 50 and an end face 52, and the outlet portion has internal connecting threads 54 and a pocket 56 for screwthreadably receiving the inlet portion.
  • the outlet portion 42 of the nozzle assembly 10 includes a planar inner end face 58 and a planar outer end face 60 parallel thereto defining a preselected length "L" therebetween as is illustrated in Fig. 2. More specifically, a cylindrical outlet passage 62 having a preselected diameter "D,” is defined between the end faces and is disposed on a second central axis 64 generally aligned with the first central axis 48 of the inlet portion 40. Moreover, a plurality of cylindrical outlet passages 66 are also defined between the end faces and individually have a diameter "D-".
  • the passages 66 are preferably aligned along a plurality of individual axes 68 which are parallel to the central axis 64 and symmetrically located a rad-ial distance therefrom to establish a radial separation distance "S" between the central passage 62 and the surrounding passages 66 as is illustrated in Fig. 3. It is theorized that the minimal radial separation distance "S” should be about 1 mm, or one half the diameter "D-", whichever is greate .
  • the central outlet passage 62 constitutes a primary or first passage means 70 for communicating a first liquid flow from the opening 46 through the outlet portion 42
  • the encircling passages 66 constitute a secondary or second passage means 72 for communicating a second liquid flow from the opening 46 through the outlet portion.
  • the first liquid flow has a flow rate along the central axis 64 at a first velocity
  • the second liquid flow has a flow rate in the individual passages 66 at a second velocity less than the first velocity .
  • the velocities of the individual outward liquid flow paths from the nozzle assembly 10 are at least in part based upon a relationship to the boundary layer flow conditions adjacent the inner wall 44 of the opening 46 in the inlet portion 40.
  • the boundary layer flow through a pipe such as the manifold 22 might represent, is a region adjacent the wall of decreased liquid velocity owing to the viscous drag of the liquid thereat.
  • the primary outlet passage 62 is spaced radially inwardly of the axial extension of the boundary layer within opening 46 in order to achieve the first desired velocity.
  • first velocity will basically be the highest velocity through the inlet portion 40 and the highest velocity through the nozzle assembly.
  • the reduced second velocity desired from the secondary outlet passages 66 is established in the instant embodiment by locating them at least in part in substantial axial alignment with the boundary layer flow along the inner wall 44. This can be accomplished by positioning the radially outermost portion of the secondary outlet passages 66 in axial alignment with the inner wall 44 of the opening 30.
  • the radially outer edges of the peripherally grouped outlet passages are constructed axially flush with the inner wall such that liquid at a decreased velocity v/ill enter the secondary outlet passages.
  • the nozzle assembly 10, and particularly the outlet passages 62,66 can be of other configurations without departing from the invention.
  • the outlet passages can be formed of individual tubes, not shown, attached to the inlet portion 40.
  • the shape, orientation, number and size of the outlet passages can be varied as long as the cross-section thereof is basically symmetrical to assure columnar flow.
  • a plurality of arcuately shaped outlet passages, not shown, can be formed in an annular relationship about the primary outlet passage.
  • the illustrated configuration represents the most desirable and economical nozzle assembly contemplated.
  • the nozzle assembly 10 sprays a substantially columnar stream pattern "A" upwardly into the profiled opening 24 and the passage 26 formed in the reciprocating piston 18.
  • the oil enters the annular chamber 28 substantially at the same flow rate as it had leaving the nozzle assembly.
  • the oil stream makes substantially no contact with the walls of the opening 24 so that there is no loss of cooling oil before the stream enters the interior of the passage 26.
  • the outlet portion 42 of the nozzle assembly is telescopingly received in the profiled opening 24 in the piston with but a minimum of clearance. But when it is at top dead center as shown, the stream is delivered for the greatest distance in columnar form directly into the passage 26.
  • the L/D ratio for the outer passages 66 should preferable be in a range of from about 7.5 to about 13.0. It is further theorized that these two L/D ratios are related and should preferably not be less than 2:1 or greater than 3:1, and with the minimum individual ratio being above about 3.75.
  • the distance "L” was 15" m
  • D was 2.5 mm
  • D ⁇ was 1.15 mm
  • the radial distance "S" between the central passage and the eight peripherically located passages was 1 mm.
  • a sufficient quantity of oil must be available within a preselected pressure range above a minimum value of about 140 KPa in the inlet manifold 22.
  • oil under a pressure of about 480 KPa was available in the manifold sufficient for the subject nozzle assembly 10 to desirably supply about 18 liters/minute to the piston passage 26.
  • the plurality of relatively long straight passages 62,66 served to divide the swirling flow into a plurality of individual and straightened streams. Due to the viscosity of the air medium between the central stream and the plurality of encircling streams traveling at a lesser velocity than the central stream, the outlying streams have a tendency to be pulled radially inwardly toward the central axis 64 through a suction phenomena aided by atmospheric pressure, all of which factors maintain the liquid stream pattern "A" in columnar form for a substantially significant overall distance, for example about 400 mm.
  • the nozzle assembly of the present invention is relatively compact and simple in operation, and can advantageously direct a columnar stream of oil into a linear passage in a reciprocating piston so that it can cool the crown portion thereof. This is accomplished without resorting to a complicated series of pressurized oil passages through the crankshaft and connecting rod, which costly alternative also tends to weaken these components in relatively critical areas.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Nozzles (AREA)

Abstract

On utilise des buses pour pulveriser un liquide, par exemple de l'huile, afin de refroidir un piston d'un moteur. Jusqu'a present la pulverisation presentait une divergence indesirable et ceci s'est avere une source de problemes pour la pulverisation a longue distance. La buse (10) selon l' invention maintient une distribution de pulverisation sensiblement cylindrique en prevoyant une partie d'admission (40) definissant une ouverture (46), et une partie d'ejection (42) definissant un premier passage (62) faisant circuler un premier courant de liquide depuis l'ouverture (46) vers l'exterieur a une premiere vitesse, et une pluralite de passages (66) faisant circuler un deuxieme courant de liquide depuis l'ouverture (46) vers l'exterieur a une seconde vitesse qui est inferieure a la premiere. Les passages presentent de preference un rapport longueur/diametre important.
PCT/US1981/000092 1981-01-23 1981-01-23 Buse pour pulverisation controlee WO1982002575A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
JP50020680A JPS57502220A (fr) 1981-01-23 1980-12-15
PCT/US1981/000092 WO1982002575A1 (fr) 1981-01-23 1981-01-23 Buse pour pulverisation controlee
BR8108955A BR8108955A (pt) 1981-01-23 1981-01-23 Conjunto de bocal para pulverizacao controlada
CA000391213A CA1167886A (fr) 1981-01-23 1981-11-30 Buse d'arrosage controle
EP19810305805 EP0057790B1 (fr) 1981-01-23 1981-12-09 Assemblage d'ajutage
DE8181305805T DE3170439D1 (en) 1981-01-23 1981-12-09 Nozzle assembly

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
PCT/US1981/000092 WO1982002575A1 (fr) 1981-01-23 1981-01-23 Buse pour pulverisation controlee
WOUS81/00092810123 1981-01-23

Publications (1)

Publication Number Publication Date
WO1982002575A1 true WO1982002575A1 (fr) 1982-08-05

Family

ID=22161055

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1981/000092 WO1982002575A1 (fr) 1981-01-23 1981-01-23 Buse pour pulverisation controlee

Country Status (6)

Country Link
EP (1) EP0057790B1 (fr)
JP (1) JPS57502220A (fr)
BR (1) BR8108955A (fr)
CA (1) CA1167886A (fr)
DE (1) DE3170439D1 (fr)
WO (1) WO1982002575A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4442843A (en) * 1980-11-17 1984-04-17 Schering, Ag Microbubble precursors and methods for their production and use
DE102004057626A1 (de) * 2004-11-30 2006-06-01 Mahle International Gmbh Kolbenspritzdüse
EP1930578B1 (fr) 2006-11-28 2019-09-25 KS Kolbenschmidt GmbH Variantes de canal de ventilation pour piston

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2212074B (en) * 1987-11-13 1992-07-08 Wakefield Anthony W Jetting nozzle
GB8726688D0 (en) * 1987-11-13 1987-12-16 Wakefield A W Jetting nozzle
DE19514939C2 (de) * 1995-04-22 1997-09-18 Kamat Pumpen Gmbh & Co Kg Löschdüsenkopf
DE19633167A1 (de) * 1996-08-17 1998-02-19 Porsche Ag Spritzdüse für die Kolbenkühlung einer Brennkraftmaschine
GB0012356D0 (en) 2000-05-22 2000-07-12 Textron Automotive Company Lim Fluid spray nozzle
CN111120065A (zh) * 2019-11-19 2020-05-08 潍柴动力股份有限公司 冷却喷嘴及提高打靶效率的方法

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1790908A (en) * 1931-02-03 Nozzie tip
US2121948A (en) * 1935-05-11 1938-06-28 Western Electric Co Burner
US2321017A (en) * 1940-10-31 1943-06-08 Calle Antonio Fernando De La Fluid discharge nozzle
US4067307A (en) * 1973-08-30 1978-01-10 Motoren- Und Turbinen Union Friedrichshafen Gmbh Free-jet-nozzle
US4206726A (en) * 1977-07-18 1980-06-10 Caterpillar Tractor Co. Double orifice piston cooling nozzle for reciprocating engines

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT327418B (de) * 1974-01-17 1976-01-26 Voest Ag Strahlduse

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1790908A (en) * 1931-02-03 Nozzie tip
US2121948A (en) * 1935-05-11 1938-06-28 Western Electric Co Burner
US2321017A (en) * 1940-10-31 1943-06-08 Calle Antonio Fernando De La Fluid discharge nozzle
US4067307A (en) * 1973-08-30 1978-01-10 Motoren- Und Turbinen Union Friedrichshafen Gmbh Free-jet-nozzle
US4206726A (en) * 1977-07-18 1980-06-10 Caterpillar Tractor Co. Double orifice piston cooling nozzle for reciprocating engines

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4442843A (en) * 1980-11-17 1984-04-17 Schering, Ag Microbubble precursors and methods for their production and use
DE102004057626A1 (de) * 2004-11-30 2006-06-01 Mahle International Gmbh Kolbenspritzdüse
US7549402B2 (en) 2004-11-30 2009-06-23 Mahle International Gmbh Piston spray nozzle
DE102004057626B4 (de) * 2004-11-30 2014-02-06 Mahle International Gmbh Kolbenspritzdüse
EP1930578B1 (fr) 2006-11-28 2019-09-25 KS Kolbenschmidt GmbH Variantes de canal de ventilation pour piston

Also Published As

Publication number Publication date
CA1167886A (fr) 1984-05-22
EP0057790A1 (fr) 1982-08-18
DE3170439D1 (en) 1985-06-13
EP0057790B1 (fr) 1985-05-08
JPS57502220A (fr) 1982-12-16
BR8108955A (pt) 1982-12-14

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