EP1208287A1 - Airless spray pump - Google Patents

Airless spray pump

Info

Publication number
EP1208287A1
EP1208287A1 EP00961390A EP00961390A EP1208287A1 EP 1208287 A1 EP1208287 A1 EP 1208287A1 EP 00961390 A EP00961390 A EP 00961390A EP 00961390 A EP00961390 A EP 00961390A EP 1208287 A1 EP1208287 A1 EP 1208287A1
Authority
EP
European Patent Office
Prior art keywords
pump
yoke
assembly
gear
housing
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.)
Granted
Application number
EP00961390A
Other languages
German (de)
French (fr)
Other versions
EP1208287B1 (en
EP1208287A4 (en
Inventor
Glen Davidson
Alexander Kapelevich
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.)
Graco Minnesota Inc
Original Assignee
Graco Inc
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=26848977&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1208287(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Graco Inc filed Critical Graco Inc
Priority to EP05077480A priority Critical patent/EP1635062B1/en
Priority to EP10184231.8A priority patent/EP2280169B1/en
Publication of EP1208287A1 publication Critical patent/EP1208287A1/en
Publication of EP1208287A4 publication Critical patent/EP1208287A4/en
Application granted granted Critical
Publication of EP1208287B1 publication Critical patent/EP1208287B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/166—Cylinder liners
    • F04B53/168—Mounting of cylinder liners in cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics

Definitions

  • Airless spray pumps for the spraying of paints and other coatings.
  • Airless spray pumps for the spraying of paints and other coatings via the airless method are well known and have traditionally been divided into two types, diaphragm pumps for the lower end of the market and reciprocating piston pumps for the higher end.
  • An airless spray pump is provided with a single-acting piston pump which allows the use of a low-cost yoke drive. Motor and pump shaft are offset for most efficient force utilization.
  • the main drive housing has a motor mounted to the rear thereof.
  • a gear assembly uses gear teeth which are formed with a 5° helical angle and have a 25° pressure angle. This geometry combines the higher efficiency of straight cut gears with the noise reduction typified in a helical design.
  • An eccentric is molded onto the front of the gear assembly and has located thereabout a bearing assembly which rides inside a yoke.
  • the yoke moves vertically on guide rods which are retained in pockets of the drive housing.
  • the yoke is molded of plastic as is the gear assembly leading to lower cost and easier manufacture.
  • the pump rod is provided with a cap over the top end thereof which has bearing.
  • Pump assembly is designed as a single acting pump, that is, the pump only pumps on the downward stroke and loads on the upward stroke. This allows the components of the drive train, including the yoke and gear, to be much lighter as the yoke ends up being more of a guidance device rather than a force-applying device.
  • the motor and pinion are offset from the centerline of the pump assembly. This arrangement does not have any significant cantilevering as the pump rod, pinion, yoke, eccentric and cap are all located in the same plane.
  • the location of the rod and the single acting pump with respect to the gear centerline reduces the thrust loads on the yoke.
  • the location of the pinion on the gear partially offsets and reduces the pump forces on the gear shaft and bearings.
  • the shaft packing assembly is comprised of a packing housing which screws into the pump housing and which contains a felt member which has been soaked with throat seal lubricant or other solvent or lubricant.
  • a stack of v-packings are compressed in place by wave spring which is tightened by tightening the seal housing into the pump housing .
  • the inlet check is provided with a check ball and a check seat which is pressed into a check housing and which is held in place by a retainer. These parts all press-fit into one another such that the complete assembly be merely screwed into main pump housing for replacement.
  • outlet check assembly is formed of an outlet check housing which is screwed into a pump housing and similarly is provided with a check ball held in place by a retainer. The outlet passageway is angled relative to the axis of the pump shaft.
  • FIG. 1 is a prospective exploded view showing the airless spray pump with the instant invention.
  • FIG. 2 is a simple front plan view of the drive assembly and pump of the instant invention.
  • FIG. 3 is a side plan view of the assembly shown in FIG. 1.
  • FIG. 4 is a detailed exploded view of the circled area in FIG. 3.
  • FIG. 5 is a cross-sectional view of the pump of the instant invention.
  • FIG. 6 shows more details of the drive assembly of the instant invention.
  • FIG. 7 is another cross-sectional view of the pump portion of the instant invention.
  • FIG. 8 is a cross-section of the outlet filter of the instant invention.
  • FIG. 9 is an exploded view of the outlet filter of the instant invention.
  • FIG. 10 is a perspective exploded view of the instant invention.
  • the instant invention generally designated 10 is comprised of a main drive housing 12 having a motor 14 mounted to the rear thereof.
  • a gear assembly 16 having a rear bearing 17 and gear teeth 22 is inserted into the bearing housing 20 of drive housing 12.
  • Gear teeth 22 on gear assembly 16 mate with the teeth on pinion 24 on the end of motor 14.
  • the teeth 22 and on pinion 24 are formed with a 5° helical angle and have a 25° pressure angle. This geometry combines the higher efficiency of straight cut gears with the noise reduction typified in a helical design.
  • An eccentric 25 is also molded onto the front of gear assembly 16 and has located thereabout a bearing assembly 28 which rides inside a yoke 30.
  • Yoke 30 moves vertically on guide rods 32 which are retained in pockets 34 of drive housing 12.
  • Yoke 30 is molded of plastic.
  • Gear assembly 16 is cast in ZA-12 with an integral counterweight leading to lower cost and easier manufacture.
  • Pump rod 36 is provided with a cap 38 over the top end thereof which has bearing upon it bearing 28.
  • Pump assembly 40 is designed as a single acting pump that is the pump only pumps on the downward stroke and loads on the upward stroke. In doing so this allows the components of the drive train, including the yoke and gear, to be much lighter as the yoke 30 ends up being more of a guidance device rather than a force- applying device.
  • motor and pinion 24 are offset from the centerline 42 of pump assembly 40 which also has offset therefrom bearing 20 in the opposite direction. Also, this arrangement does not have any significant cantilevering as the pump rod, pinion, yoke, eccentric and cap are all located in the same plane.
  • the location of the rod and the single acting pump with respect to the gear centerline reduces the thrust loads on the yoke.
  • the location of the pinion on the gear partially offsets and reduces the pump forces on the gear shaft and bearings.
  • the shaft packing assembly 44 shown in FIG. 4 is comprised of a packing housing 46 which screws into pump housing 48 and which contains a felt member 50 which has been soaked with throat seal lubricant or other solvent or lubricant.
  • a stack of v-packings is comprised of a packing housing 46 which screws into pump housing 48 and which contains a felt member 50 which has been soaked with throat seal lubricant or other solvent or lubricant.
  • wave spring 54 which is tightened by tightening seal housing 46 into pump housing 48.
  • inlet check 56 is provided with a check ball 58, a check seat 60 which is pressed into check housing 62 and which is held in place by retainer and integral ball guide 64. These parts all press-fit into one another such that the complete assembly be merely screwed into main pump housing 48 for replacement.
  • outlet check assembly is formed of an outlet check housing 60 which is screwed into pump housing 48 and similarly is provided with a check ball 62 held in place by ball seat 65.
  • the outlet passageway 66 is angled relative to the axis of pump shaft 36.
  • outlet check assembly 58 This allows the outlet check assembly 58 to operate essentially via gravity and yet requires only the drilling and provision of one passageway while maintaining an essentially vertical ball-seat relationship.
  • FIGs. 8 and 9 show the outlet filter assembly 80 which is comprised of a filter element 82 contained in passage 84 of pump assembly 40 and which is retained by fitting 86.
  • inlet tube 70 is provided with a female threaded end 70a.
  • Inlet filter screen assembly 72 has a male threaded end 72a for threaded engagement with end
  • Ends 70a and 72a use the same size and thread as a common garden hose such that a user need merely remove screen assembly 72, attach a garden hose to inlet tube 70, turn on the water and flush out the assembly.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

An airless spray pump (10) is provided with a single-acting piston pump which allows the use of a low-cost yoke (30) drive. Motor and pump shaft are offset for most efficient force utilization.

Description

AIRLESS SPRAY PUMP
TECHNICAL FIELD
Airless spray pumps for the spraying of paints and other coatings.
BACKGROUND ART
Airless spray pumps for the spraying of paints and other coatings via the airless method are well known and have traditionally been divided into two types, diaphragm pumps for the lower end of the market and reciprocating piston pumps for the higher end.
DISCLOSURE OF THE INVENTION
An airless spray pump is provided with a single-acting piston pump which allows the use of a low-cost yoke drive. Motor and pump shaft are offset for most efficient force utilization. The main drive housing has a motor mounted to the rear thereof. A gear assembly uses gear teeth which are formed with a 5° helical angle and have a 25° pressure angle. This geometry combines the higher efficiency of straight cut gears with the noise reduction typified in a helical design.
An eccentric is molded onto the front of the gear assembly and has located thereabout a bearing assembly which rides inside a yoke. The yoke moves vertically on guide rods which are retained in pockets of the drive housing. The yoke is molded of plastic as is the gear assembly leading to lower cost and easier manufacture.
The pump rod is provided with a cap over the top end thereof which has bearing.
Pump assembly is designed as a single acting pump, that is, the pump only pumps on the downward stroke and loads on the upward stroke. This allows the components of the drive train, including the yoke and gear, to be much lighter as the yoke ends up being more of a guidance device rather than a force-applying device.
The motor and pinion are offset from the centerline of the pump assembly. This arrangement does not have any significant cantilevering as the pump rod, pinion, yoke, eccentric and cap are all located in the same plane. The location of the rod and the single acting pump with respect to the gear centerline reduces the thrust loads on the yoke. The location of the pinion on the gear partially offsets and reduces the pump forces on the gear shaft and bearings. By locating the eccentric bearing directly on the end of the pump rod cap which is press-fit it eliminates the transfer of pumping force through an intermediate member such as the yoke which provides longer life, efficiency and allows the manufacture of a more inexpensive yoke assembly.
The shaft packing assembly is comprised of a packing housing which screws into the pump housing and which contains a felt member which has been soaked with throat seal lubricant or other solvent or lubricant. A stack of v-packings are compressed in place by wave spring which is tightened by tightening the seal housing into the pump housing .
The inlet check is provided with a check ball and a check seat which is pressed into a check housing and which is held in place by a retainer. These parts all press-fit into one another such that the complete assembly be merely screwed into main pump housing for replacement. Similarly, outlet check assembly is formed of an outlet check housing which is screwed into a pump housing and similarly is provided with a check ball held in place by a retainer. The outlet passageway is angled relative to the axis of the pump shaft.
This allows the outlet check assembly to operate essentially via gravity and yet requires only the drilling and provision of one passageway while maintaining an essentially vertical ball-seat relationship.
These and other objects and advantages of the invention will appear more fully from the following description made in conjunction with the accompanying drawings wherein like reference characters refer to the same or similar parts throughout the several views.
BRIEF DESCRIPTION OF DRAWINGS
FIG. 1 is a prospective exploded view showing the airless spray pump with the instant invention.
FIG. 2 is a simple front plan view of the drive assembly and pump of the instant invention.
FIG. 3 is a side plan view of the assembly shown in FIG. 1.
FIG. 4 is a detailed exploded view of the circled area in FIG. 3.
FIG. 5 is a cross-sectional view of the pump of the instant invention.
FIG. 6 shows more details of the drive assembly of the instant invention. FIG. 7 is another cross-sectional view of the pump portion of the instant invention.
FIG. 8 is a cross-section of the outlet filter of the instant invention.
FIG. 9 is an exploded view of the outlet filter of the instant invention.
FIG. 10 is a perspective exploded view of the instant invention.
BEST MODE FOR CARRYING OUT THE INVENTION
The instant invention generally designated 10 is comprised of a main drive housing 12 having a motor 14 mounted to the rear thereof. A gear assembly 16 having a rear bearing 17 and gear teeth 22 is inserted into the bearing housing 20 of drive housing 12. Gear teeth 22 on gear assembly 16 mate with the teeth on pinion 24 on the end of motor 14. The teeth 22 and on pinion 24 are formed with a 5° helical angle and have a 25° pressure angle. This geometry combines the higher efficiency of straight cut gears with the noise reduction typified in a helical design.
An eccentric 25 is also molded onto the front of gear assembly 16 and has located thereabout a bearing assembly 28 which rides inside a yoke 30. Yoke 30 moves vertically on guide rods 32 which are retained in pockets 34 of drive housing 12. Yoke 30 is molded of plastic. Gear assembly 16 is cast in ZA-12 with an integral counterweight leading to lower cost and easier manufacture.
Pump rod 36 is provided with a cap 38 over the top end thereof which has bearing upon it bearing 28. Pump assembly 40 is designed as a single acting pump that is the pump only pumps on the downward stroke and loads on the upward stroke. In doing so this allows the components of the drive train, including the yoke and gear, to be much lighter as the yoke 30 ends up being more of a guidance device rather than a force- applying device.
As can be seen more particularly in FIG. 2, motor and pinion 24 are offset from the centerline 42 of pump assembly 40 which also has offset therefrom bearing 20 in the opposite direction. Also, this arrangement does not have any significant cantilevering as the pump rod, pinion, yoke, eccentric and cap are all located in the same plane. The location of the rod and the single acting pump with respect to the gear centerline reduces the thrust loads on the yoke. The location of the pinion on the gear partially offsets and reduces the pump forces on the gear shaft and bearings. By locating the eccentric bearing directly on the end of the pump rod cap which is press-fit it eliminates the transfer of pumping force through an intermediate member such as the yoke which provides longer life, efficiency and allows the manufacture of a more inexpensive yoke assembly.
The shaft packing assembly 44 shown in FIG. 4 is comprised of a packing housing 46 which screws into pump housing 48 and which contains a felt member 50 which has been soaked with throat seal lubricant or other solvent or lubricant. A stack of v-packings
52 are compressed in place by wave spring 54 which is tightened by tightening seal housing 46 into pump housing 48.
Turning to FIG. 7, inlet check 56 is provided with a check ball 58, a check seat 60 which is pressed into check housing 62 and which is held in place by retainer and integral ball guide 64. These parts all press-fit into one another such that the complete assembly be merely screwed into main pump housing 48 for replacement. Similarly, outlet check assembly is formed of an outlet check housing 60 which is screwed into pump housing 48 and similarly is provided with a check ball 62 held in place by ball seat 65. As can also be seen in FIG. 7, the outlet passageway 66 is angled relative to the axis of pump shaft 36.
This allows the outlet check assembly 58 to operate essentially via gravity and yet requires only the drilling and provision of one passageway while maintaining an essentially vertical ball-seat relationship.
FIGs. 8 and 9 show the outlet filter assembly 80 which is comprised of a filter element 82 contained in passage 84 of pump assembly 40 and which is retained by fitting 86.
Turning to FIG. 10, inlet tube 70 is provided with a female threaded end 70a. Inlet filter screen assembly 72 has a male threaded end 72a for threaded engagement with end
70a. Ends 70a and 72a use the same size and thread as a common garden hose such that a user need merely remove screen assembly 72, attach a garden hose to inlet tube 70, turn on the water and flush out the assembly.
It is contemplated that various changes and modifications may be made to the airless spray pump without departing from the spirit and scope of the invention as defined by the following claims.

Claims

1. A spray pump powered by a rotary motor having a pinion thereon and comprising:
a housing;
a single-acting piston pump having a pump rod and connected to said housing;
a drive gear assembly comprising a gear and an eccentric located on said gear;
a bearing located about said eccentric;
a yoke reciprocatingly located in said housing and about said bearing; and
a relatively hard cap located on said pump rod and in said yoke so as to contact said bearing.
2. The spray pump of claim 1 wherein said pump rod, said pinion, said yoke, said eccentric and said cap are all located in generally the same plane.
3. The spray pump of claim 1 wherein the teeth on said gear are formed with about a 5° helical angle and about a 25° pressure angle.
4. The spray pump of claim 1 wherein said motor and pinion are offset from the centerline of said pump to reduce the thrust loads on the yoke and offset and reduce the pump forces.
5. An airless spray pump having an inlet tube and an inlet filter screen, the improvement comprising said inlet tube being provided with a female threaded end and said inlet filter screen assembly being provided with a male threaded end threaded engagement with female end, said ends having the same size and thread as a common garden hose such that a user need merely remove said screen assembly and attach a garden hose to said inlet tube to flush out the assembly.
EP00961390A 1999-08-31 2000-08-28 Airless spray pump Expired - Lifetime EP1208287B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP05077480A EP1635062B1 (en) 1999-08-31 2000-08-28 Airless spray pump
EP10184231.8A EP2280169B1 (en) 1999-08-31 2000-08-28 Airless spray pump

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
US15179499P 1999-08-31 1999-08-31
US151794P 1999-08-31
US16694699P 1999-11-22 1999-11-22
US166946P 1999-11-22
PCT/US2000/023613 WO2001016462A1 (en) 1999-08-31 2000-08-28 Airless spray pump

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP05077480A Division EP1635062B1 (en) 1999-08-31 2000-08-28 Airless spray pump

Publications (3)

Publication Number Publication Date
EP1208287A1 true EP1208287A1 (en) 2002-05-29
EP1208287A4 EP1208287A4 (en) 2005-05-11
EP1208287B1 EP1208287B1 (en) 2006-07-26

Family

ID=26848977

Family Applications (2)

Application Number Title Priority Date Filing Date
EP00961390A Expired - Lifetime EP1208287B1 (en) 1999-08-31 2000-08-28 Airless spray pump
EP10184231.8A Expired - Lifetime EP2280169B1 (en) 1999-08-31 2000-08-28 Airless spray pump

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP10184231.8A Expired - Lifetime EP2280169B1 (en) 1999-08-31 2000-08-28 Airless spray pump

Country Status (9)

Country Link
US (1) USRE42706E1 (en)
EP (2) EP1208287B1 (en)
JP (2) JP4668493B2 (en)
KR (1) KR100668583B1 (en)
CN (1) CN1171004C (en)
AU (1) AU7334800A (en)
DE (1) DE60029597T2 (en)
ES (3) ES2389607T3 (en)
WO (1) WO2001016462A1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1404432A4 (en) * 2001-06-05 2006-03-29 Graco Minnesota Inc Integrated filter housing
EP2457666A1 (en) * 2010-11-25 2012-05-30 Doriano Galassi Spray painting device
AU2017200180B2 (en) * 2016-01-12 2022-01-06 Graco Minnesota Inc. Integrated pump guard and control interlock
US12140140B2 (en) * 2016-07-29 2024-11-12 Wagner Spray Tech Corporation Aligning reciprocating motion in fluid delivery systems
US11007545B2 (en) * 2017-01-15 2021-05-18 Graco Minnesota Inc. Handheld airless paint sprayer repair

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2366237A (en) * 1943-09-23 1945-01-02 Lucien I Yeomans Inc Scotch yoke
US2366238A (en) * 1943-09-23 1945-01-02 Lucien I Yeomans Inc Scotch yoke
US3067624A (en) * 1959-04-16 1962-12-11 Norton Tool Company Ltd Pumps, compressors and engines
JPS4934631Y1 (en) * 1970-11-05 1974-09-19
JPS5583598U (en) * 1978-12-05 1980-06-09
US4416588A (en) * 1980-07-18 1983-11-22 Wagner Spray Tech Corporation Air compressor for paint pumps
JPS58129079U (en) * 1982-02-24 1983-09-01 日本電子株式会社 Feed pump
JPS61200829A (en) * 1985-03-04 1986-09-05 Mitsuo Yanagisawa Filter apparatus
US4768932A (en) 1986-07-25 1988-09-06 Geberth John Daniel Jun Hydraulic paint pump
EP0389716B1 (en) * 1989-03-31 1994-05-18 Japan Storage Battery Company Limited Cam crank mechanism and motor driven hydraulic tool
US5228842A (en) * 1991-07-30 1993-07-20 Wagner Spray Tech Corporation Quick-change fluid section for piston-type paint pumps
JPH0826851B2 (en) * 1991-10-04 1996-03-21 三菱重工業株式会社 Discharge method of residual viscous fluid
JP2640895B2 (en) * 1992-08-10 1997-08-13 株式会社岩本商会 A device that sucks and exhausts air inside the water suction pipe of a fire pump using the same vacuum pump
US5567323A (en) * 1995-04-06 1996-10-22 Harrison-Pipkin, L.L.C. Intake filter for a paint sprayer
US5769321A (en) * 1996-02-20 1998-06-23 Wagner Spray Tech Corporation Yoke support for piston paint pumps
US5842639A (en) 1997-07-25 1998-12-01 Walker; Willis Paint sprayer screen

Also Published As

Publication number Publication date
ES2424141T3 (en) 2013-09-27
CN1171004C (en) 2004-10-13
USRE42706E1 (en) 2011-09-20
DE60029597T2 (en) 2007-07-12
AU7334800A (en) 2001-03-26
EP1208287B1 (en) 2006-07-26
EP2280169A2 (en) 2011-02-02
KR20020047133A (en) 2002-06-21
ES2269176T3 (en) 2007-04-01
JP2010223234A (en) 2010-10-07
JP2003522870A (en) 2003-07-29
JP5060587B2 (en) 2012-10-31
ES2389607T3 (en) 2012-10-29
EP2280169B1 (en) 2013-05-01
JP4668493B2 (en) 2011-04-13
EP2280169A3 (en) 2011-12-07
WO2001016462A1 (en) 2001-03-08
KR100668583B1 (en) 2007-01-18
CN1377440A (en) 2002-10-30
EP1208287A4 (en) 2005-05-11
DE60029597D1 (en) 2006-09-07

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