US20090123311A1 - Plunger-slipper assembly of high-pressure pump - Google Patents
Plunger-slipper assembly of high-pressure pump Download PDFInfo
- Publication number
- US20090123311A1 US20090123311A1 US11/983,541 US98354107A US2009123311A1 US 20090123311 A1 US20090123311 A1 US 20090123311A1 US 98354107 A US98354107 A US 98354107A US 2009123311 A1 US2009123311 A1 US 2009123311A1
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- US
- United States
- Prior art keywords
- plunger
- slipper
- annular groove
- oil
- coaxial hole
- 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.)
- Abandoned
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Classifications
-
- 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
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
-
- 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
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
- F04B1/124—Pistons
Definitions
- the present invention relates to high-pressure pumps and, more particularly, to a to high-pressure pump equipped with a plurality of improved plunger-slipper assemblies.
- An oil diffusion pump as shown in FIG. 1 , comprises a rotary shaft 91 in a housing 90 and a plunger seat 92 which is connected with rotary shaft 91 .
- a plurality of plunger holes 921 are axially arranged as a circle and each of the plunger holes 921 has a plunger 93 deposited therein.
- Each said plunger 93 comprises a universal plunger head 931 which is retained in a plunger hole 991 of a rocking plate 99 .
- a tilting plate 94 can be provided in the housing 90 coaxially with the rotary shaft 91 , the tilting angle of which is adjustable.
- the tilting plate 94 has a contacting surface 941 and each plunger head 931 contacts with the contacting surface 941 along the direction parallel to the rotary shaft 91 .
- each said plunger 93 circles the rotary shaft 91 .
- each said plunger 93 performs a stroke having a predetermined length during each trip around the rotary shaft 91 .
- the rocking plate 99 rocks in harmony with the movement of each said plunger head 931 .
- oil can be injected into the plunger seat 92 through the oil inlet piping 95 that is communicated with the housing 90 and, after an expectative pressure boost is provided to the oil, the oil can be output through the oil outlet piping 96 that is communicated with the housing 90 .
- an accommodating space 933 provided on the plunger head 931 is sized to snugly receive yet allow rotational movement of a round joint 932 of the plunger 93 so as to enable an universal rotational movement of the plunger head 931 .
- the present invention has been accomplished under these circumstances in view. It is one objective of the present invention to provide a novel plunger-slipper assembly structure in a high-pressure pump as shown in FIG. 4 .
- the disclosed plunger-slipper assembly facilitates generating a relatively larger stroke length so as to significantly enhance the oil pressure of high-pressure pumps of such type.
- a particular lubrication solution is provided herein for retarding the abrasion of the disclosed plunger-slipper assembly that performs an enhanced stroke.
- the plunger-slipper structure of a high-pressure pump comprises a plunger and a slipper.
- the plunger has a first end and a second end, which are both spherical ends.
- the slipper comprises a coaxial hole for receiving the plunger and the coaxial hole has a spherical space formed at the extremity thereof for accommodating the second end of the plunger.
- the first end of the plunger juts out from the slipper.
- An oil-filling channel lengthwise penetrates the plunger through the first end to the second end thereof.
- An oil-guiding channel radially penetrates the wall of the slipper and connects with the extremity of the coaxial hole.
- a first annular groove is deposited at the identical peripheral position of the outer wall of the slipper where the oil-guiding channel is settled.
- a third annular groove is also deposited surrounding the outer wall of the slipper and is separated from the first annular groove with a predetermined distance. The location of the third annular groove is near the second end of the plunger. An annular stuff is settled in the third annular groove.
- FIG. 1 is a schematic cross sectional view of a conventional oil diffusion pump
- FIG. 2 is a schematic cross sectional view of the plunger-slipper assembly of the conventional oil diffusion pump
- FIG. 3 is an exploded view illustrating the plunger-slipper assemblies, a plunger seat and a rotary valve of the disclosed subject matter
- FIG. 4 is a schematic cross sectional view showing the assembled plunger-slipper assemblies, the plunger seat and the rotary valve of the disclosed subject matter settled in a housing of an oil pressure pump;
- FIG. 5 is a perspective view of the plunger-slipper assembly of the present invention.
- FIG. 6 is a plane view of the plunger-slipper assembly of the present invention.
- FIG. 7 is a lengthwise sectional view of the plunger-slipper assembly of the present invention.
- a plunger seat 10 a plurality of plunger-slipper assemblies 50 and a rotary valve 30 are illustrated.
- Each of the plural plunger-slipper assemblies 50 has a spherical end 52 received by a hemispheric recess 11 provided on the plunger seat 10 .
- a plunger retaining plate 12 is fixed on the extremity of the plunger seat 10 by a plurality of screws 16 .
- a plurality of holes 15 arranged on the plunger seat 10 is provided for engaging the spherical ends 52 respectively so as to prevent the plural plunger-slipper assemblies 50 from departing from the plunger seat 10 .
- the plunger seat 10 is assembled into a housing 40 with a plurality of bearing components 13 and can be rotated by a rotary shaft 14 .
- the rotary valve 30 is positioned in the housing 40 and is posed to tilt by a predetermined angle under the domination of an angle-setting device 70 .
- the rotary valve 30 also provides a plurality of plunger channels 31 for allowing the disclosed plunger-slipper assemblies 50 snugly slide therein.
- the rotary shaft 14 drives the plunger seat 10 to rotate, and in turn makes the plunger-slipper assemblies 50 and the rotary valve 30 rotate simultaneously.
- the inserting depth of each said plunger-slipper assembly 50 into the plunger channel 31 varies during the rotary valve 30 makes a circuit, and a simulate plunger stroke can be accomplished.
- the oil inlet piping not shown
- an expectative pressure boost is provided to the oil
- the oil can be output through the oil outlet piping (not shown) that is communicated with the housing 40 .
- the tilting angle of the rotary valve 30 and the stroke of the plunger-slipper assemblies 50 are subject to the setting of the aforementioned angle-setting device 70 . While the larger the tilting angle of the rotary valve 30 is, the larger length of the stroke of the plunger-slipper assemblies 50 is allowed and the larger pressure boost is achieved. Otherwise, the effects are contrary to the results above.
- the present invention aims at providing the structure of plunger-slipper assembly 50 operating in coordination therewith.
- the plunger-slipper assembly 50 facilitates generating a relatively larger stroke. Because of the larger stroke, the plunger-slipper assembly 50 requires a particular lubrication solution so as to retard the abrasion thereof.
- the plunger-slipper assembly 50 of the present invention comprises a plunger 51 and a slipper 55 .
- the aforesaid spherical end of the plunger 51 for being engaged by the plunger seat 10 is defined as a first end 52 while the opposite end, which is also a spherical one, is defined as a second end 53 .
- the slipper 55 comprises a coaxial hole 56 for receiving the plunger 51 and the coaxial hole 56 has a spherical space formed at the extremity thereof for accommodating the second end 53 of the plunger 51 .
- the inner diameter of the coaxial hole 56 is slightly larger than the outer diameter of the plunger 51 so that a slightly rotational movement of the plunger 51 in the coaxial hole 56 is attainable.
- the tilting angle between the plunger-slipper assembly 50 and the plunger 10 is augmented and adapted to the rotary valve 30 , which rotates with a sharp angle. Consequently, an enhanced plunger stroke distance is achieved.
- the plunger 51 is lengthwise penetrated by an oil-filling channel 54 .
- Lubricating oil can be infused into the oil filler oil-filling channel 54 and be guided to between the slipper 55 and the plunger channel 31 by way of an oil-guiding channel 58 provided at the extremity of the coaxial hole 56 .
- the present invention is characterized by an oil-distributing unit 60 , which comprises a first annular groove 61 and a second annular groove 62 .
- the first annular groove 61 is deposited at the identical peripheral position where the oil-guiding channel 58 is settled while the second annular groove 62 is separated from the first annular groove 61 with a predetermined distance.
- a third annular groove 63 is further separated from the second annular groove 62 with a predetermined distance therebetween.
- an intrusive flange 57 is formed at the inner periphery of the coaxial hole 56 corresponding to the third annular groove 63 .
- the flange 57 touches the second end 53 of the plunger 51 at a proper position so as to axially retain yet allow rotational movement of the plunger 51 .
- An annular stuff 64 such as a silicon ring, may be settled in the third annular groove 63 to fill up the vacancy between the slipper 55 and the rotary valve 30 so that the slipper 55 can move within the plunger channel 31 with improved stability.
- the released lubricating oil can therefore pervade the first annular groove 61 . Then, the lubricating oil can be smeared evenly on the contact surfaces of the slipper 55 and the plunger channel 31 as a result of the relative displacement therebetween. Consequently, the lubricating oil can further permeate the second annular groove 62 .
- first and second annular grooves 61 , 62 are both narrow channels, when the slipper 55 moves along the plunger channel 31 , the lubricating oil can be transitionally stored in the narrow channels and then exude from the first and second annular grooves 61 , 62 .
- the contact surfaces of the slipper 55 and the plunger channel 31 can be uniformly covered by the lubricating oil so as to generally reduce the friction between the contact surfaces and permit a smoother movement of the slipper 55 .
- the annular stuff 64 functions as a barricade to keep the lubricating oil on the surface of the slipper 55 therebelow.
- the lubricating oil can fill the first and second annular grooves 61 , 62 and then evenly distribute between the inner wall of the plunger channel 31 and the outer wall of the slipper 55 as a result of the movement of the slipper 55 with respect to the plunger channel 31 .
- the lubricating oil can efficiently function with the least sufficient amount that facilitates preventing the mess that an excessively great amount of oil congests between the inner wall of the plunger channel 31 and the outer wall of the slipper 55 and overflows from the plunger channel 31 .
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Abstract
A plunger-slipper assembly of a high-pressure pump is herein claimed. The plunger-slipper assembly comprises a plunger and a slipper. The plunger has a first end and a second end, which are both spherical ends. The slipper comprises a coaxial hole for receiving the plunger and the coaxial hole has a spherical space formed at the extremity thereof for accommodating the second end of the plunger. The first end of the plunger juts out from the slipper. Further, the diameter of the coaxial hole of the slipper is slightly larger than the diameter of the plunger. An oil-filling channel lengthwise penetrates the plunger through the first end to the second end thereof. An oil-guiding channel radially penetrates the wall of the slipper and connects with the extremity of the coaxial hole. A first annular groove is deposited at the outer wall of the slipper. A third annular groove is also deposited surrounding the outer wall of the slipper. An annular stuff is settled in the third annular groove. The disclosed plunger-slipper structure operates in a high-pressure pump to provide a relatively larger stroke and to retard the abrasion thereof.
Description
- 1. Technical Field
- The present invention relates to high-pressure pumps and, more particularly, to a to high-pressure pump equipped with a plurality of improved plunger-slipper assemblies.
- 2. Description of Related Art
- An oil diffusion pump, as shown in
FIG. 1 , comprises arotary shaft 91 in ahousing 90 and aplunger seat 92 which is connected withrotary shaft 91. A plurality ofplunger holes 921 are axially arranged as a circle and each of theplunger holes 921 has aplunger 93 deposited therein. Each saidplunger 93 comprises auniversal plunger head 931 which is retained in aplunger hole 991 of arocking plate 99. Atilting plate 94 can be provided in thehousing 90 coaxially with therotary shaft 91, the tilting angle of which is adjustable. Thetilting plate 94 has a contactingsurface 941 and eachplunger head 931 contacts with the contactingsurface 941 along the direction parallel to therotary shaft 91. When theplunger seat 92 is propelled by therotary shaft 91, each said plunger 93 circles therotary shaft 91. In virtue of the tilting angle of thetilting plate 94, each saidplunger 93 performs a stroke having a predetermined length during each trip around therotary shaft 91. Therocking plate 99 rocks in harmony with the movement of each saidplunger head 931. Thereby oil can be injected into theplunger seat 92 through theoil inlet piping 95 that is communicated with thehousing 90 and, after an expectative pressure boost is provided to the oil, the oil can be output through theoil outlet piping 96 that is communicated with thehousing 90. - Referring to
FIG. 2 , anaccommodating space 933 provided on theplunger head 931 is sized to snugly receive yet allow rotational movement of around joint 932 of theplunger 93 so as to enable an universal rotational movement of theplunger head 931. - It is known by skilled persons in the art that due to the design of the plungers, the plunger heads and the titling plate of the high-pressure pump as depicted in
FIG. 1 , the trip of the plunger within the plunger hole is relatively limited. Consequently, the expectative pressure boost of oil performed by the high-pressure pump is restricted from substantial increase. - The present invention has been accomplished under these circumstances in view. It is one objective of the present invention to provide a novel plunger-slipper assembly structure in a high-pressure pump as shown in
FIG. 4 . The disclosed plunger-slipper assembly facilitates generating a relatively larger stroke length so as to significantly enhance the oil pressure of high-pressure pumps of such type. Also, a particular lubrication solution is provided herein for retarding the abrasion of the disclosed plunger-slipper assembly that performs an enhanced stroke. - To achieve these and other objectives of the present invention, the plunger-slipper structure of a high-pressure pump comprises a plunger and a slipper. The plunger has a first end and a second end, which are both spherical ends. The slipper comprises a coaxial hole for receiving the plunger and the coaxial hole has a spherical space formed at the extremity thereof for accommodating the second end of the plunger. The first end of the plunger juts out from the slipper. An oil-filling channel lengthwise penetrates the plunger through the first end to the second end thereof. An oil-guiding channel radially penetrates the wall of the slipper and connects with the extremity of the coaxial hole. A first annular groove is deposited at the identical peripheral position of the outer wall of the slipper where the oil-guiding channel is settled. A third annular groove is also deposited surrounding the outer wall of the slipper and is separated from the first annular groove with a predetermined distance. The location of the third annular groove is near the second end of the plunger. An annular stuff is settled in the third annular groove.
- The invention as well as a preferred mode of use, further objectives and advantages thereof, will best be understood by reference to the following detailed description of an illustrative embodiment when read in conjunction with the accompanying drawings, wherein:
-
FIG. 1 is a schematic cross sectional view of a conventional oil diffusion pump; -
FIG. 2 is a schematic cross sectional view of the plunger-slipper assembly of the conventional oil diffusion pump; -
FIG. 3 is an exploded view illustrating the plunger-slipper assemblies, a plunger seat and a rotary valve of the disclosed subject matter; -
FIG. 4 is a schematic cross sectional view showing the assembled plunger-slipper assemblies, the plunger seat and the rotary valve of the disclosed subject matter settled in a housing of an oil pressure pump; -
FIG. 5 is a perspective view of the plunger-slipper assembly of the present invention; -
FIG. 6 is a plane view of the plunger-slipper assembly of the present invention; and -
FIG. 7 is a lengthwise sectional view of the plunger-slipper assembly of the present invention. - In
FIG. 3 , aplunger seat 10, a plurality of plunger-slipper assemblies 50 and arotary valve 30 are illustrated. Each of the plural plunger-slipper assemblies 50 has aspherical end 52 received by ahemispheric recess 11 provided on theplunger seat 10. Aplunger retaining plate 12 is fixed on the extremity of theplunger seat 10 by a plurality ofscrews 16. A plurality ofholes 15 arranged on theplunger seat 10 is provided for engaging thespherical ends 52 respectively so as to prevent the plural plunger-slipper assemblies 50 from departing from theplunger seat 10. - Referring to
FIG. 4 , theplunger seat 10 is assembled into ahousing 40 with a plurality ofbearing components 13 and can be rotated by arotary shaft 14. Therotary valve 30 is positioned in thehousing 40 and is posed to tilt by a predetermined angle under the domination of an angle-settingdevice 70. Therotary valve 30 also provides a plurality ofplunger channels 31 for allowing the disclosed plunger-slipper assemblies 50 snugly slide therein. - The
rotary shaft 14 drives theplunger seat 10 to rotate, and in turn makes the plunger-slipper assemblies 50 and therotary valve 30 rotate simultaneously. As therotary valve 30 is posed to tilt by the preset angle, the inserting depth of each said plunger-slipper assembly 50 into theplunger channel 31 varies during therotary valve 30 makes a circuit, and a simulate plunger stroke can be accomplished. Then after oil is injected into therotary valve 30 through the oil inlet piping (not shown) that is communicated with thehousing 40 and an expectative pressure boost is provided to the oil, the oil can be output through the oil outlet piping (not shown) that is communicated with thehousing 40. - The tilting angle of the
rotary valve 30 and the stroke of the plunger-slipper assemblies 50 are subject to the setting of the aforementioned angle-setting device 70. While the larger the tilting angle of therotary valve 30 is, the larger length of the stroke of the plunger-slipper assemblies 50 is allowed and the larger pressure boost is achieved. Otherwise, the effects are contrary to the results above. - As the above-discussed structure of the high-pressure pump is well known in the art, it is not in the scope of what the present invention claims for. The present invention, however, aims at providing the structure of plunger-
slipper assembly 50 operating in coordination therewith. The plunger-slipper assembly 50 facilitates generating a relatively larger stroke. Because of the larger stroke, the plunger-slipper assembly 50 requires a particular lubrication solution so as to retard the abrasion thereof. - As shown in
FIGS. 5 , 6 and 7, the plunger-slipper assembly 50 of the present invention comprises aplunger 51 and aslipper 55. The aforesaid spherical end of theplunger 51 for being engaged by theplunger seat 10 is defined as afirst end 52 while the opposite end, which is also a spherical one, is defined as asecond end 53. Theslipper 55 comprises acoaxial hole 56 for receiving theplunger 51 and thecoaxial hole 56 has a spherical space formed at the extremity thereof for accommodating thesecond end 53 of theplunger 51. Further, the inner diameter of thecoaxial hole 56 is slightly larger than the outer diameter of theplunger 51 so that a slightly rotational movement of theplunger 51 in thecoaxial hole 56 is attainable. Thus, the tilting angle between the plunger-slipper assembly 50 and theplunger 10 is augmented and adapted to therotary valve 30, which rotates with a sharp angle. Consequently, an enhanced plunger stroke distance is achieved. - The
plunger 51 is lengthwise penetrated by an oil-fillingchannel 54. Lubricating oil can be infused into the oil filler oil-fillingchannel 54 and be guided to between theslipper 55 and theplunger channel 31 by way of an oil-guidingchannel 58 provided at the extremity of thecoaxial hole 56. - The present invention is characterized by an oil-distributing
unit 60, which comprises a firstannular groove 61 and a secondannular groove 62. The firstannular groove 61 is deposited at the identical peripheral position where the oil-guidingchannel 58 is settled while the secondannular groove 62 is separated from the firstannular groove 61 with a predetermined distance. - A third
annular groove 63 is further separated from the secondannular groove 62 with a predetermined distance therebetween. Meantime, anintrusive flange 57 is formed at the inner periphery of thecoaxial hole 56 corresponding to the thirdannular groove 63. Theflange 57 touches thesecond end 53 of theplunger 51 at a proper position so as to axially retain yet allow rotational movement of theplunger 51. Anannular stuff 64, such as a silicon ring, may be settled in the thirdannular groove 63 to fill up the vacancy between theslipper 55 and therotary valve 30 so that theslipper 55 can move within theplunger channel 31 with improved stability. - In
FIG. 4 , as the lubricating oil is infused at the oil-fillingchannel 54 of theplunger 51 and released at the oil-guidingchannel 58, the released lubricating oil can therefore pervade the firstannular groove 61. Then, the lubricating oil can be smeared evenly on the contact surfaces of theslipper 55 and theplunger channel 31 as a result of the relative displacement therebetween. Consequently, the lubricating oil can further permeate the secondannular groove 62. Since the first and secondannular grooves slipper 55 moves along theplunger channel 31, the lubricating oil can be transitionally stored in the narrow channels and then exude from the first and secondannular grooves slipper 55 and theplunger channel 31 can be uniformly covered by the lubricating oil so as to generally reduce the friction between the contact surfaces and permit a smoother movement of theslipper 55. - The
annular stuff 64 functions as a barricade to keep the lubricating oil on the surface of theslipper 55 therebelow. Thus, the lubricating oil can fill the first and secondannular grooves plunger channel 31 and the outer wall of theslipper 55 as a result of the movement of theslipper 55 with respect to theplunger channel 31. Hence, the lubricating oil can efficiently function with the least sufficient amount that facilitates preventing the mess that an excessively great amount of oil congests between the inner wall of theplunger channel 31 and the outer wall of theslipper 55 and overflows from theplunger channel 31. - Although a particular embodiment of the invention has been described in detail for purposes of illustration, it will be understood by one of ordinary skill in the art that numerous variations will be possible to the disclosed embodiments without going outside the scope of the invention as disclosed in the claims.
Claims (2)
1. A plunger-slipper assembly of a high-pressure pump, comprising
a plunger having a first end and a second end, which are both spherical ends;
a slipper comprising a coaxial hole for receiving the plunger wherein the coaxial hole has a spherical space formed at the extremity thereof for accommodating the second end of the plunger and the first end of the plunger juts out from the slipper while the diameter of the coaxial hole of the slipper is slightly larger than the diameter of the plunger;
an oil-filling channel lengthwise penetrating the plunger through the first end to the second end thereof;
an oil-guiding channel radially penetrating the wall of the slipper and connecting with the extremity of the coaxial hole;
a first annular groove deposited at the identical peripheral position of the outer wall of the slipper where the oil-guiding channel is settled;
a third annular groove also deposited surrounding the outer wall of the slipper and is separated from the first annular groove with a predetermined distance wherein location of the third annular groove is near the second end of the plunger; an intrusive flange formed at the inner periphery of the coaxial hole corresponding to the third annular groove, wherein the flange touches the second end of the plunger at a proper position so as to axially retain the plunger; and
an annular stuff is settled in the third annular groove.
2. The plunger-slipper assembly of claim 1 , wherein a second annular groove is provided between the first annular groove and the third annular groove.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US11/983,541 US20090123311A1 (en) | 2007-11-09 | 2007-11-09 | Plunger-slipper assembly of high-pressure pump |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US11/983,541 US20090123311A1 (en) | 2007-11-09 | 2007-11-09 | Plunger-slipper assembly of high-pressure pump |
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Publication Number | Publication Date |
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US20090123311A1 true US20090123311A1 (en) | 2009-05-14 |
Family
ID=40623872
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Application Number | Title | Priority Date | Filing Date |
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US11/983,541 Abandoned US20090123311A1 (en) | 2007-11-09 | 2007-11-09 | Plunger-slipper assembly of high-pressure pump |
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US (1) | US20090123311A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107420296A (en) * | 2017-08-16 | 2017-12-01 | 潍柴动力股份有限公司 | Plunger and cam-type axial piston pump for cam-type axial piston pump |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2155455A (en) * | 1932-11-24 | 1939-04-25 | Thoma Hans | Hydraulic motor and pump |
US3173376A (en) * | 1957-03-21 | 1965-03-16 | United Systems Corp | Hydraulic pump or motor |
US4546692A (en) * | 1982-10-22 | 1985-10-15 | Hydromatik Gmbh | Radial bearing for drive plate of inclined-axis type axial piston machine |
US6557454B2 (en) * | 2000-07-12 | 2003-05-06 | Sanden Corporation | Compressor pistons |
-
2007
- 2007-11-09 US US11/983,541 patent/US20090123311A1/en not_active Abandoned
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2155455A (en) * | 1932-11-24 | 1939-04-25 | Thoma Hans | Hydraulic motor and pump |
US3173376A (en) * | 1957-03-21 | 1965-03-16 | United Systems Corp | Hydraulic pump or motor |
US4546692A (en) * | 1982-10-22 | 1985-10-15 | Hydromatik Gmbh | Radial bearing for drive plate of inclined-axis type axial piston machine |
US6557454B2 (en) * | 2000-07-12 | 2003-05-06 | Sanden Corporation | Compressor pistons |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107420296A (en) * | 2017-08-16 | 2017-12-01 | 潍柴动力股份有限公司 | Plunger and cam-type axial piston pump for cam-type axial piston pump |
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AS | Assignment |
Owner name: ACME BEST CORPORATION, TAIWAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:YU, LI-FU;REEL/FRAME:020158/0787 Effective date: 20071101 |
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STCB | Information on status: application discontinuation |
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