CA1164729A - Marine drive water pump - Google Patents
Marine drive water pumpInfo
- Publication number
- CA1164729A CA1164729A CA000374910A CA374910A CA1164729A CA 1164729 A CA1164729 A CA 1164729A CA 000374910 A CA000374910 A CA 000374910A CA 374910 A CA374910 A CA 374910A CA 1164729 A CA1164729 A CA 1164729A
- Authority
- CA
- Canada
- Prior art keywords
- impeller
- water
- shroud
- impeller housing
- drive shaft
- 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
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 67
- 229910052751 metal Inorganic materials 0.000 claims abstract description 12
- 239000002184 metal Substances 0.000 claims abstract description 12
- 230000002093 peripheral effect Effects 0.000 claims description 13
- 229910001220 stainless steel Inorganic materials 0.000 claims description 5
- 239000010935 stainless steel Substances 0.000 claims description 5
- 239000000498 cooling water Substances 0.000 claims description 3
- 238000007789 sealing Methods 0.000 claims description 2
- 238000005260 corrosion Methods 0.000 description 5
- 230000007797 corrosion Effects 0.000 description 5
- 238000001816 cooling Methods 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 239000004033 plastic Substances 0.000 description 2
- 229920003023 plastic Polymers 0.000 description 2
- 239000004576 sand Substances 0.000 description 2
- KLYCPFXDDDMZNQ-UHFFFAOYSA-N Benzyne Chemical compound C1=CC#CC=C1 KLYCPFXDDDMZNQ-UHFFFAOYSA-N 0.000 description 1
- 229910001369 Brass Inorganic materials 0.000 description 1
- 229920002430 Fibre-reinforced plastic Polymers 0.000 description 1
- 229920000459 Nitrile rubber Polymers 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 239000010951 brass Substances 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 229920001971 elastomer Polymers 0.000 description 1
- 239000011151 fibre-reinforced plastic Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 239000002991 molded plastic Substances 0.000 description 1
- 229910052755 nonmetal Inorganic materials 0.000 description 1
- 239000005060 rubber Substances 0.000 description 1
- 238000005482 strain hardening Methods 0.000 description 1
- 229920003051 synthetic elastomer Polymers 0.000 description 1
- 239000005061 synthetic rubber Substances 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/40—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member
- F04C2/44—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member with vanes hinged to the inner member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B61/00—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing
- F02B61/04—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing for driving propellers
- F02B61/045—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing for driving propellers for marine engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C5/00—Rotary-piston machines or pumps with the working-chamber walls at least partly resiliently deformable
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Ocean & Marine Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Improved Marine Drive Water Pump Abstract An improved water pump (16) for a marine drive includes a base plate (22), a cup-shaped impeller housing (30) and a shroud (52). An impeller (40) having a plurality of flexible vanes (46) is positioned within the impeller housing (30). Water enters the pump (16) from a water inlet (28) in the base plate (22) and is forced by the rotating impeller (40) through a water outlet (38) to the marine drive. The impeller housing (30) and shroud (52) are formed of stamped metal parts and the impeller (40) includes long, flexible vanes (46).
Description
6472g Descri~ on Improved llarine Drive l,ater Pump Technical Field ~larine drives havinp water cooled enaines utilize a water pump mounted over the drive shaft and internal to the drive shaft housing to provide engine cooling.
Background Art One prior water pump used for cooling an outboard engine utilized a cast metal housing. The cast metal housina requires machining and is costly to manufacture Also the life of a cast brass or cast aluminum water pump is relatively low where the water contains sand and silt ~hich will cause internal wear on the moving parts.
Another prior water pump is formed of a molded plastic housing. A metal liner is used within the plastic housing to provide abrasion resistance l~ithout -the metal liner the plastic will wear through resulting in a water pump failure~ A water pump failure may also result in engine failure.
Disclosure of Invention The present invention provides an improved marine drive water pump that is simply and economically formed through the use of stamped metal parts. The parts are
Background Art One prior water pump used for cooling an outboard engine utilized a cast metal housing. The cast metal housina requires machining and is costly to manufacture Also the life of a cast brass or cast aluminum water pump is relatively low where the water contains sand and silt ~hich will cause internal wear on the moving parts.
Another prior water pump is formed of a molded plastic housing. A metal liner is used within the plastic housing to provide abrasion resistance l~ithout -the metal liner the plastic will wear through resulting in a water pump failure~ A water pump failure may also result in engine failure.
Disclosure of Invention The present invention provides an improved marine drive water pump that is simply and economically formed through the use of stamped metal parts. The parts are
2~ used without machining.
The improved water pUmD of the present invention includes:
a base Dlate mounted in the r,larine dr;ve the base plate having an eccentrically positioned drive shaft opening and a water inlet opening into the coolina water intake;
a cup-shaped impeller housing formed of deformed sheet metal having an end wall and a peripheral , ..~
~:, `I 1 64729 wall, the end wal:l havi.ncJ an ecce~ntrLccllly posltioned dr:ive shaft opening and a water outlet;
an impeller posi-tionecl in the lmpeller housing for propelling water received at the water inlet ou-t -the water outlet, the impeller having a central portion coupled to the drive shaft and a plurality of flexible impeller vanes extending outwardly from the central portion into con-tact with the peripheral wall oE the impeller housing; and a shroud formed of deformed sheet metal fi-t-ting over the impeller housing to embrace the end wall and peripheral wall of the housing, the shroud being secured to the base plate and forming an arcuate collecting chamber between the shroud and the impeller housing to connect the outlet with a water discharge opening for the pump angularly displaced from the water outlet about the axis of the drive shaft.
The improved water pump of the invention provides a water pump which has an increased service life and provides a superior silt resistance and dry running capability. The use of a metal stamping provides work hardening of the wear surfaces providing silt resistance and long flexible vanes on the impeller reduces wear on the impeller housing and results in longer impeller life.
The improved water pump of the invention provides in a single water pump all of the features necessary for a marine drive. These features are abrasion resistance, dry run survivability, reduced pressure loss with time, long flex life, excellent corrosion resistance, relatively low cost and excellent long-term adhesion of impeller rubber to its non-metal insert. In the improved water pump the long flexible vanes provide a low radial pressure thereby resulting in a reduced wear on the impeller housing, a longer flex life for the vanes, reduced pressure loss with respect to time and low friction. The low friction reduces the heat build up in the vanes and thereby permits better dry running of the water pump.
~.~
1 1 ~4729
The improved water pUmD of the present invention includes:
a base Dlate mounted in the r,larine dr;ve the base plate having an eccentrically positioned drive shaft opening and a water inlet opening into the coolina water intake;
a cup-shaped impeller housing formed of deformed sheet metal having an end wall and a peripheral , ..~
~:, `I 1 64729 wall, the end wal:l havi.ncJ an ecce~ntrLccllly posltioned dr:ive shaft opening and a water outlet;
an impeller posi-tionecl in the lmpeller housing for propelling water received at the water inlet ou-t -the water outlet, the impeller having a central portion coupled to the drive shaft and a plurality of flexible impeller vanes extending outwardly from the central portion into con-tact with the peripheral wall oE the impeller housing; and a shroud formed of deformed sheet metal fi-t-ting over the impeller housing to embrace the end wall and peripheral wall of the housing, the shroud being secured to the base plate and forming an arcuate collecting chamber between the shroud and the impeller housing to connect the outlet with a water discharge opening for the pump angularly displaced from the water outlet about the axis of the drive shaft.
The improved water pump of the invention provides a water pump which has an increased service life and provides a superior silt resistance and dry running capability. The use of a metal stamping provides work hardening of the wear surfaces providing silt resistance and long flexible vanes on the impeller reduces wear on the impeller housing and results in longer impeller life.
The improved water pump of the invention provides in a single water pump all of the features necessary for a marine drive. These features are abrasion resistance, dry run survivability, reduced pressure loss with time, long flex life, excellent corrosion resistance, relatively low cost and excellent long-term adhesion of impeller rubber to its non-metal insert. In the improved water pump the long flexible vanes provide a low radial pressure thereby resulting in a reduced wear on the impeller housing, a longer flex life for the vanes, reduced pressure loss with respect to time and low friction. The low friction reduces the heat build up in the vanes and thereby permits better dry running of the water pump.
~.~
1 1 ~4729
3-Brief Description_of Drawincls Figure 1 is a partially broken a~ay side view of an outboard engine illustrating the water pump of the present invention.
Figure 2 is a cross-sectional view of the ~later pump shown in Figure 1~
Figure 3 is an exploded view showing the components of the water pump shown in Figure 1 appearing with Figure 1.
Figure 4 is a plan view of the impeller of the water pump shown in Figure 1.
Figure 5 is a view from beneath showing the impeller in the impeller housing.
Best Mode for Carryinn Out the Invention The ~arine drive is shown as an outboard engine 10 in Figure 1 The outboard engine 10 includes a liquid cooled .power head 12 that powers the drive shaft 14 The en~ine is cooled by water supPlied by a pump 16.
The propulsion unit 18 of the outboard engine 10 contains a water intake 20 that is within water when the propul-sion unit 18 is in the onerating position. The waterpumn 16 also may be mounted in the outboard engine 10 so that it is below the ~/ater line when the propulsion unit 18 is submerged The water pump 16 includes a base plate 22 that is mounted in the outboard engine 10 above the water intake conduit 24 and within the oear case housing The base plate 22 is preferably formed of stainless steel sheet. The base plate 22 has an eccentrically positioned drive shaft opening 26. The base plate 22 includes a water inlet 28 snaced from the opening 26 and communicating with the water intake conduit 24.
A cup-shaped impeller housing 30 is positioned on the base plate 22 to connect ~Jith the water ;nlet 28.
In the preferred embodiment the impeller housing 30 is formed from a stainless steel sheet to- lend econo~y and corrosion resistance in the manufacture of the pump 1 and to provide hardening of desired areas of the ~, 1 16~729 resulting housing. The impeller housing 30 has a peripheral wall 32. An end wall 34 of the impeller housing 30 also contains an eccentrically posit.ioned drive shaft opening 36. The wall 34 also includes ~
water outlet 38 spaced from the opening 36 and about oppositely displaced as shown in the figures from the water inlet 28 after the pump 16 is assembled.
The impeller 40 is positioned in the impeller housing 30. The impeller 40 is formed of a flexible material such as synthetic rubber compounded for temperature resistance. The preferred flexible material is nitrile elastomer. The impeller 40 includes a hub 42. The hub 42 is partly formed of fiber reinforced plastic to increase the corrosion resistance of the ~ater pump 16 by avoiding a metal-to-metal contact between the impeller 40 and the drive shaft 14. The hub 42 is keyed to the drive shaft 14 by a key 44. A
plurality of long, flexible impeller vanes 46 extend from the hub 42 of the impeller 40. In the preferr~d embodiment, as shown in Figure 4, six such vanes are provided. The sealing rings 48 and 50 on either side of the hub 42 serve to seal the impeller housing 30 when the impeller 40 is located in the impeller housing 30 as shown in Figure 2. The length and flexural properties of the vanes 46 and the inside diameter of the impeller housing 30 are selected so that a low radial pressure is exerted by each vane 46 on the peripheral wall 32 and low flexural stresses result in vanes 46. In the preferred embodiment the vane length is about 0.64 inches, the vane width at the hub 42 is about 0.2 inches and the ratio of the vane length to width is about 3.2:1.
The hub outside diameter is about 1.04 inches and the inside diameter of the impeller housing 30 is about 2 inches and the ratio of the inside diameter of the impeller housing 30 to the outside diameter of the impeller hub 42 is greater than 1.9:1. The height o~ the vane parallel to drive shaft 41 is adjusted to 1 1 6~729 obtain the desired capacity or volume flow of the water pump. In an alternative embodiment the vane length is about .85 inches, the vane width at the hub 42 is about 0.26 inches and the ratio of the vane length to width is about 3~3:1. The hub outside diameter is about 1.2 inches and the inside diameter of the impeller housing 30 is about 2.5 inches and the ratio of the hub outside diameter to the impeller housing inside diameter is about 2.1:1.
In order to obtain the best flexure life of the vanes 46 it is required that the ratio of the vane length to width is equal to or greater than 3:1 and that the ratio of the inside diameter of the impeller housing 30 to the outside diameter of the impeller hub 42 is greater than 1.9:1. Since the impeller 40 is positioned in the impeller housing 30 eccentrically with the inside diameter of the housing 30 as previously described and as shown in Fig. 5 the outside diameter of the impeller 40 is larger than the inside diameter of the impeller housing 30. The ratio of the outside diameter of the impeller 40 to the inside diameter of the impeller housing 30 is in the range of 1.10:1 to 1.16:1. This is necessary to provide sealin~ between the end of the vanes and the peripheral wall 32.
It is also preferred that the tip width of the vanes be a minimum. In the preferred embodiment the tip width is about 0.12 inches and in the alternative embodiment the tip width i9 about 0.15 inches. The tip width is obtained by tapering the vane from its width at the hub to its extreme width at an included angle of about 8 to 9 degrees.
A shroud 52 fits over the impeller housing 30.
In the preferred embodiment the shroud 52 is formed from a stainless steel sheet. The shroud 52 includes a flange 54 which contacts the base plate 22. The shroud 52 and the base plate 22 are secured to the ~pulsion unit l~ by the bolts 56. The bolts 56 are . .
... :
also ~ormed of stainless steel to reduce corrosion.
Non-metallic sleeves 58 are positioned over the bolts 56 and between the flange 54 to improve corrosion resistance. The shroud 52 has a peripheral wall 60 press-fitted with the peripheral wall 32 of the im-peller housing 30. An 0-ring 62 at the edge of the wall 60 of the impeller housing 30 seals the base plate 22 from the impeller housing 30 and a separate gasket between the base plate 22 and the shroud 52 seals the base plate 22 from the outboard engine 10. The transi-tion between the wall 60 and the flange 54 may be suitably formed to accommodate an 0-ring 62. The shroud 52 has an end wall 64 containing an eccentric opening 66 for insçrting the drive shaft 14. A
rotary slinger 68 is positioned over the drive shaft 14 on top of the water pump 16 to prevent entry of dirt and sand. When press-fitted the end wall 60 of the impeller housing 30 and the end wall 64 of the shroud 52 form a collecting chamber in the form of anarcuate passage 70 that connects the water outlet 38 of the impeller housing 30 with the water discharge pipe 72 through the connector 74. A water discharge pipe 72 connects the cooling water from the water pump 16 to the heat producing portions of the outboard engine 10 for cooling.
In operation the i~peller housing 30 receives water through the water inlet 28 in the base plate 22.
As shown in Figure 5 the vanes 46 are sequentially flexed against the wall 32 of the impeller housing 30 by ~h~ ê~ O rotation of the drive shaft 14 first a~ lhQ~e~ng ~xtant and then to a decreasing extent ~u~ @a~h ~Qt~tl~n of the impeller 40. The flexing ~ ~h~ ~a~- 46 and the resulting reduction in the volume between them and the peripheral wall 32 of the impeller housing 30 forces the water in the impeller housing 30 out water outlet 38, then through the passage 70 and into the water discharge pipe 72.
~, ~ . .~. . .
Figure 2 is a cross-sectional view of the ~later pump shown in Figure 1~
Figure 3 is an exploded view showing the components of the water pump shown in Figure 1 appearing with Figure 1.
Figure 4 is a plan view of the impeller of the water pump shown in Figure 1.
Figure 5 is a view from beneath showing the impeller in the impeller housing.
Best Mode for Carryinn Out the Invention The ~arine drive is shown as an outboard engine 10 in Figure 1 The outboard engine 10 includes a liquid cooled .power head 12 that powers the drive shaft 14 The en~ine is cooled by water supPlied by a pump 16.
The propulsion unit 18 of the outboard engine 10 contains a water intake 20 that is within water when the propul-sion unit 18 is in the onerating position. The waterpumn 16 also may be mounted in the outboard engine 10 so that it is below the ~/ater line when the propulsion unit 18 is submerged The water pump 16 includes a base plate 22 that is mounted in the outboard engine 10 above the water intake conduit 24 and within the oear case housing The base plate 22 is preferably formed of stainless steel sheet. The base plate 22 has an eccentrically positioned drive shaft opening 26. The base plate 22 includes a water inlet 28 snaced from the opening 26 and communicating with the water intake conduit 24.
A cup-shaped impeller housing 30 is positioned on the base plate 22 to connect ~Jith the water ;nlet 28.
In the preferred embodiment the impeller housing 30 is formed from a stainless steel sheet to- lend econo~y and corrosion resistance in the manufacture of the pump 1 and to provide hardening of desired areas of the ~, 1 16~729 resulting housing. The impeller housing 30 has a peripheral wall 32. An end wall 34 of the impeller housing 30 also contains an eccentrically posit.ioned drive shaft opening 36. The wall 34 also includes ~
water outlet 38 spaced from the opening 36 and about oppositely displaced as shown in the figures from the water inlet 28 after the pump 16 is assembled.
The impeller 40 is positioned in the impeller housing 30. The impeller 40 is formed of a flexible material such as synthetic rubber compounded for temperature resistance. The preferred flexible material is nitrile elastomer. The impeller 40 includes a hub 42. The hub 42 is partly formed of fiber reinforced plastic to increase the corrosion resistance of the ~ater pump 16 by avoiding a metal-to-metal contact between the impeller 40 and the drive shaft 14. The hub 42 is keyed to the drive shaft 14 by a key 44. A
plurality of long, flexible impeller vanes 46 extend from the hub 42 of the impeller 40. In the preferr~d embodiment, as shown in Figure 4, six such vanes are provided. The sealing rings 48 and 50 on either side of the hub 42 serve to seal the impeller housing 30 when the impeller 40 is located in the impeller housing 30 as shown in Figure 2. The length and flexural properties of the vanes 46 and the inside diameter of the impeller housing 30 are selected so that a low radial pressure is exerted by each vane 46 on the peripheral wall 32 and low flexural stresses result in vanes 46. In the preferred embodiment the vane length is about 0.64 inches, the vane width at the hub 42 is about 0.2 inches and the ratio of the vane length to width is about 3.2:1.
The hub outside diameter is about 1.04 inches and the inside diameter of the impeller housing 30 is about 2 inches and the ratio of the inside diameter of the impeller housing 30 to the outside diameter of the impeller hub 42 is greater than 1.9:1. The height o~ the vane parallel to drive shaft 41 is adjusted to 1 1 6~729 obtain the desired capacity or volume flow of the water pump. In an alternative embodiment the vane length is about .85 inches, the vane width at the hub 42 is about 0.26 inches and the ratio of the vane length to width is about 3~3:1. The hub outside diameter is about 1.2 inches and the inside diameter of the impeller housing 30 is about 2.5 inches and the ratio of the hub outside diameter to the impeller housing inside diameter is about 2.1:1.
In order to obtain the best flexure life of the vanes 46 it is required that the ratio of the vane length to width is equal to or greater than 3:1 and that the ratio of the inside diameter of the impeller housing 30 to the outside diameter of the impeller hub 42 is greater than 1.9:1. Since the impeller 40 is positioned in the impeller housing 30 eccentrically with the inside diameter of the housing 30 as previously described and as shown in Fig. 5 the outside diameter of the impeller 40 is larger than the inside diameter of the impeller housing 30. The ratio of the outside diameter of the impeller 40 to the inside diameter of the impeller housing 30 is in the range of 1.10:1 to 1.16:1. This is necessary to provide sealin~ between the end of the vanes and the peripheral wall 32.
It is also preferred that the tip width of the vanes be a minimum. In the preferred embodiment the tip width is about 0.12 inches and in the alternative embodiment the tip width i9 about 0.15 inches. The tip width is obtained by tapering the vane from its width at the hub to its extreme width at an included angle of about 8 to 9 degrees.
A shroud 52 fits over the impeller housing 30.
In the preferred embodiment the shroud 52 is formed from a stainless steel sheet. The shroud 52 includes a flange 54 which contacts the base plate 22. The shroud 52 and the base plate 22 are secured to the ~pulsion unit l~ by the bolts 56. The bolts 56 are . .
... :
also ~ormed of stainless steel to reduce corrosion.
Non-metallic sleeves 58 are positioned over the bolts 56 and between the flange 54 to improve corrosion resistance. The shroud 52 has a peripheral wall 60 press-fitted with the peripheral wall 32 of the im-peller housing 30. An 0-ring 62 at the edge of the wall 60 of the impeller housing 30 seals the base plate 22 from the impeller housing 30 and a separate gasket between the base plate 22 and the shroud 52 seals the base plate 22 from the outboard engine 10. The transi-tion between the wall 60 and the flange 54 may be suitably formed to accommodate an 0-ring 62. The shroud 52 has an end wall 64 containing an eccentric opening 66 for insçrting the drive shaft 14. A
rotary slinger 68 is positioned over the drive shaft 14 on top of the water pump 16 to prevent entry of dirt and sand. When press-fitted the end wall 60 of the impeller housing 30 and the end wall 64 of the shroud 52 form a collecting chamber in the form of anarcuate passage 70 that connects the water outlet 38 of the impeller housing 30 with the water discharge pipe 72 through the connector 74. A water discharge pipe 72 connects the cooling water from the water pump 16 to the heat producing portions of the outboard engine 10 for cooling.
In operation the i~peller housing 30 receives water through the water inlet 28 in the base plate 22.
As shown in Figure 5 the vanes 46 are sequentially flexed against the wall 32 of the impeller housing 30 by ~h~ ê~ O rotation of the drive shaft 14 first a~ lhQ~e~ng ~xtant and then to a decreasing extent ~u~ @a~h ~Qt~tl~n of the impeller 40. The flexing ~ ~h~ ~a~- 46 and the resulting reduction in the volume between them and the peripheral wall 32 of the impeller housing 30 forces the water in the impeller housing 30 out water outlet 38, then through the passage 70 and into the water discharge pipe 72.
~, ~ . .~. . .
Claims (5)
1. In a marine drive having a water cooled engine rotating a drive shaft and having a cooling water intake, the improved water pump comprising:
a) a base plate mounted in said marine drive, said base plate having an eccentrically positioned drive shaft opening and a water inlet opening into the cooling water intake, b) a cup-shaped impeller housing formed of deformed sheet metal having an end wall and a peripheral wall, said end wall having an eccentrically positioned drive shaft opening and a water outlet, c) an impeller positioned in said impeller housing for propelling water received at said water inlet out said water outlet, said impeller having a central hub coupled to the drive shaft and a plurality of flexible impeller vanes extending outwardly from said central hub into contact with the peripheral wall of said impeller housing, and d) a shroud formed of deformed sheet metal fitting over said impeller housing to embrace the end wall and peripheral wall of said housing, said shroud being secured to said base plate, said shroud forming an arcuate collecting chamber between the shroud and the impeller housing to connect said outlet with a water discharge opening for said pump angularly displaced from said water outlet about the axis of the drive shaft.
a) a base plate mounted in said marine drive, said base plate having an eccentrically positioned drive shaft opening and a water inlet opening into the cooling water intake, b) a cup-shaped impeller housing formed of deformed sheet metal having an end wall and a peripheral wall, said end wall having an eccentrically positioned drive shaft opening and a water outlet, c) an impeller positioned in said impeller housing for propelling water received at said water inlet out said water outlet, said impeller having a central hub coupled to the drive shaft and a plurality of flexible impeller vanes extending outwardly from said central hub into contact with the peripheral wall of said impeller housing, and d) a shroud formed of deformed sheet metal fitting over said impeller housing to embrace the end wall and peripheral wall of said housing, said shroud being secured to said base plate, said shroud forming an arcuate collecting chamber between the shroud and the impeller housing to connect said outlet with a water discharge opening for said pump angularly displaced from said water outlet about the axis of the drive shaft.
2. The improved water pump according to Claim 1 wherein said shroud abuts said base plate and wherein said pump includes sealing means between said shroud and said base plate.
3. The improved water pump according to Claim 1 wherein said base plate, impeller housing, and shroud are formed of stainless steel.
4. The improved water pump according to Claim 3 wherein said impeller housing has a work hardened peripheral wall.
5. The improved water pump according to Claim 1 wherein said impeller vanes are dimensioned in length and width to create low flexural stresses in said impeller vanes, said length dimension being radial with respect to the drive shaft and said width dimension being normal to said length dimension and to the drive shaft; the ratio of the vane length to width being greater than 3:1 and the ratio of the inside diameter of the impeller housing to the outside diameter of the impeller hub is greater than 1.9:1.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US14652880A | 1980-05-05 | 1980-05-05 | |
| US146,528 | 1980-05-05 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1164729A true CA1164729A (en) | 1984-04-03 |
Family
ID=22517796
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000374910A Expired CA1164729A (en) | 1980-05-05 | 1981-04-08 | Marine drive water pump |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPS572490A (en) |
| AU (1) | AU542067B2 (en) |
| CA (1) | CA1164729A (en) |
| DE (1) | DE3117557A1 (en) |
| GB (1) | GB2075599B (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2120728A (en) * | 1982-04-29 | 1983-12-07 | Davall Moulded Gears | Rotary fluid meter or pump |
| EP0103720A1 (en) * | 1982-08-23 | 1984-03-28 | Itt Industries, Inc. | Vane-impeller arrangement for pumps |
| DE3239906A1 (en) * | 1982-10-28 | 1984-05-03 | Rolf 2000 Hamburg Niemann | DEVICE FOR PRODUCING A MIXTURE |
| US4512720A (en) * | 1983-04-12 | 1985-04-23 | Barry Wright Corporation | Pump impellers and manufacture thereof by co-injection molding |
| JPS6261U (en) * | 1985-06-17 | 1987-01-06 | ||
| JPH01179187U (en) * | 1988-06-09 | 1989-12-22 | ||
| DE4026618A1 (en) * | 1990-08-23 | 1992-02-27 | Pierburg Gmbh | LEAF CELL OR INTERNAL GEAR PUMP |
| RU2532455C1 (en) * | 2013-08-16 | 2014-11-10 | Закрытое Акционерное Общество "Новомет-Пермь" | Rotor pump |
| EP2985437B1 (en) * | 2014-07-09 | 2018-08-22 | Borgwarner Emissions Systems Spain, S.L.U. | Fixing bracket |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2436876A (en) * | 1943-07-29 | 1948-03-02 | Alfred L Stamsvik | Rotary sliding vane pump structure |
| US2712792A (en) * | 1950-06-28 | 1955-07-12 | Scott Atwater Mfg Co Inc | Pump structure |
| DE7909577U1 (en) * | 1979-04-03 | 1979-07-12 | Farymann - Diesel Farny & Weidmann Gmbh & Co Kg, 6840 Lampertheim | HOUSING FOR A DISPLACEMENT PUMP |
-
1981
- 1981-04-08 CA CA000374910A patent/CA1164729A/en not_active Expired
- 1981-04-24 JP JP6320481A patent/JPS572490A/en active Granted
- 1981-04-24 GB GB8112772A patent/GB2075599B/en not_active Expired
- 1981-04-30 AU AU70016/81A patent/AU542067B2/en not_active Ceased
- 1981-05-04 DE DE19813117557 patent/DE3117557A1/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| GB2075599A (en) | 1981-11-18 |
| DE3117557A1 (en) | 1982-03-11 |
| GB2075599B (en) | 1984-06-27 |
| JPS6336434B2 (en) | 1988-07-20 |
| JPS572490A (en) | 1982-01-07 |
| AU542067B2 (en) | 1985-02-07 |
| DE3117557C2 (en) | 1988-01-14 |
| AU7001681A (en) | 1981-11-12 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |