US20120156077A1 - Cam liner profile - Google Patents
Cam liner profile Download PDFInfo
- Publication number
- US20120156077A1 US20120156077A1 US12/973,349 US97334910A US2012156077A1 US 20120156077 A1 US20120156077 A1 US 20120156077A1 US 97334910 A US97334910 A US 97334910A US 2012156077 A1 US2012156077 A1 US 2012156077A1
- Authority
- US
- United States
- Prior art keywords
- vane
- cam surface
- profile
- pump according
- vane pump
- 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
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0007—Radial sealings for working fluid
- F04C15/0011—Radial sealings for working fluid of rigid material
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/104—Stators; Members defining the outer boundaries of the working chamber
- F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
-
- 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
- F04C2/34—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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C2/3441—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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
- F04C2/3442—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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
Definitions
- the subject matter disclosed herein relates to a vane pump having a unique cam liner profile.
- Vane pumps typically include a rotor carrying a plurality of radially movable vanes. The vanes are urged outwardly into contact with a cam surface.
- the cam surface may be formed within a liner, which is mounted within an outer housing and which has a profile such that the cam surface has a similar profile.
- the rotor is mounted eccentrically within the cam surface, such that the size of pump chambers increase and then decrease as the rotor moves from an inlet portion of a cycle toward a discharge portion. While the pump is moving through the inlet portion, fluid moves in through an inlet window and is then discharged through an outlet window after the pump cycle is completed.
- a vane pump includes a liner having an inlet window and a discharge window, the liner being formed to define a cam surface and a rotor carrying a plurality of radially extending vanes which are forced outwardly such that vane tips thereof contact with the cam surface, the rotor having a direction of rotation such that one end of the inlet window is an upstream end and an opposed end is a downstream end, a radius of each of the vane tips being approximately 0.114 inches (0.3 cm) and a profile of the cam surface being defined in accordance with the radius of the vane tips.
- a vane pump includes a liner having an inlet window and a discharge window, the liner being formed to define a cam surface and a rotor carrying a plurality of radially extending vanes which are forced outwardly such that vane tips thereof contact with the cam surface, the rotor having a direction of rotation such that one end of the inlet window is an upstream end and an opposed end is a downstream end, a radius of each of the vane tips being approximately 0.150 inches (0.4 cm) and a profile of the cam surface being defined in accordance with the radius of the vane tips.
- a vane pump includes a liner having an inlet window and a discharge window, the liner being formed to define a cam surface and a rotor carrying a plurality of radially extending vanes which are forced outwardly such that vane tips thereof contact with the cam surface, the rotor having a direction of rotation such that one end of the inlet window is an upstream end and an opposed end is a downstream end, a radius of each of the vane tips being within a range of approximately 0.114 inches (0.3 cm) to approximately 0.150 inches (0.4 cm), inclusively, and a profile of the cam surface being defined in accordance with the radius of the vane tips.
- FIG. 1A shows a vane pump
- FIG. 1B shows a liner from the FIG. 1A vane pump
- FIG. 1C shows a liner in accordance with further embodiments
- FIG. 2 shows an exemplary vane
- FIG. 3 shows exemplary vane and cam liner profiles.
- a pump 20 is illustrated in FIG. 1A having a rotor 22 carrying a plurality of vanes 23 with vane tips 231 .
- the vanes 23 are forced outwardly such that the vane tips 231 abut against a cam surface 26 , shown here as part of a liner 25 .
- the vanes 23 are oriented perpendicularly with respect to adjacent vanes 23 .
- the liner 25 has a substantially eccentric cylindrical shape with the rotor 22 disposed in the liner 25 substantially parallel with a longitudinal axis of the liner 25 .
- the liner 25 is typically mounted within a housing that has a supply of fluid to be pumped toward inlet window 28 .
- Pump chambers 24 are formed between the cam surface 26 , and adjacent ones of the vanes 23 . While not shown, the vanes 23 can move radially inwardly and outwardly of the rotor 22 .
- the rotor 22 is mounted eccentrically within the liner 25 and driven to rotate such that the volume of the pump chambers 24 increases as it moves through an inlet portion of a pump cycle, and over the inlet window 28 , and then begin to decrease in accordance with movement toward a discharge portion.
- a discharge window 30 is formed circumferentially spaced from the inlet window 28 .
- multiple discharge windows 30 may be formed circumferentially spaced from multiple inlet windows 28 .
- a profile of the liner 25 (i.e., the “cam liner profile”) has been determined in accordance with a modified trapezoidal cam profile of standard vane tips.
- contact stresses between the vane tips 231 and the liner 25 were found to be excessively high.
- reduction of the contact stresses is achieved by an increase of a radius, R T , of the vane tips.
- R T a radius
- the vanes 23 are no longer able to follow the standard cam liner profile due to geometric constraints and, as a result, the vanes are pinched and lock inside the liner prohibiting further rotation.
- the standard cam liner profile has been modified to allow for a larger vane tip radius and results in the reduced contact stress by as much as 26%.
- the “ ⁇ 4H”, the “ ⁇ 6” and the “ ⁇ 8” are all standard feature models and the “ ⁇ 6R114”, the “ ⁇ 4HR114” and the “ ⁇ 8R150” are modified with new tip radii and in some cases new vane lengths.
- the liner 25 of FIG. 1C may be used.
- one vane element is enough to meet the minimum flow requirement in the “ ⁇ 8R150” case and, as such, the liner 25 of FIG. 1B may be used.
- the radii, R T , of the vane tips 231 have been increased to between 0.114 inches (0.3 cm) to 0.150 inches (0.4 cm), inclusively.
- the profile of the liner 25 has been modified as well. With reference to FIG. 3 , the modification to the liner 25 profile is illustrated and, as shown in FIG.
- the liner profile i.e., r .cam ( ⁇ )
- the profile of the tracing defined by the vane tips 231 i.e., r .tip ( ⁇ )
- the profiles diverge from one another.
- the profiles re-converge at around the 135 and the 225 degree regions. This has the effect of fattening the liner 25 profile around the 45-135 and the 315-225 degree regions.
- the vanes 23 having increased vane tip 231 radii are removed from contact with the cam surface 26 . This removal from contact reduces the stresses and the PV values of the modified models that would otherwise be generated.
Abstract
A vane pump is provided and includes a liner having an inlet window and a discharge window, the liner being formed to define a cam surface and a rotor carrying a plurality of radially extending vanes which are forced outwardly such that vane tips thereof contact with the cam surface, the rotor having a direction of rotation such that one end of the inlet window is an upstream end and an opposed end is a downstream end, a radius of each of the vane tips being approximately 0.114 inches (0.3 cm) and a profile of the cam surface being defined in accordance with the radius of the vane tips.
Description
- The subject matter disclosed herein relates to a vane pump having a unique cam liner profile.
- Vane pumps typically include a rotor carrying a plurality of radially movable vanes. The vanes are urged outwardly into contact with a cam surface. The cam surface may be formed within a liner, which is mounted within an outer housing and which has a profile such that the cam surface has a similar profile.
- The rotor is mounted eccentrically within the cam surface, such that the size of pump chambers increase and then decrease as the rotor moves from an inlet portion of a cycle toward a discharge portion. While the pump is moving through the inlet portion, fluid moves in through an inlet window and is then discharged through an outlet window after the pump cycle is completed.
- There are stresses and forces on the vanes and the cam surface from the interacting movement and pressure differentials across the pump. There are particularly high contact stresses formed on the cam surface at areas associated with the inlet window and in particular at downstream ends of the inlet window.
- According to one aspect of the invention, a vane pump is provided and includes a liner having an inlet window and a discharge window, the liner being formed to define a cam surface and a rotor carrying a plurality of radially extending vanes which are forced outwardly such that vane tips thereof contact with the cam surface, the rotor having a direction of rotation such that one end of the inlet window is an upstream end and an opposed end is a downstream end, a radius of each of the vane tips being approximately 0.114 inches (0.3 cm) and a profile of the cam surface being defined in accordance with the radius of the vane tips.
- According to another aspect of the invention, a vane pump is provided and includes a liner having an inlet window and a discharge window, the liner being formed to define a cam surface and a rotor carrying a plurality of radially extending vanes which are forced outwardly such that vane tips thereof contact with the cam surface, the rotor having a direction of rotation such that one end of the inlet window is an upstream end and an opposed end is a downstream end, a radius of each of the vane tips being approximately 0.150 inches (0.4 cm) and a profile of the cam surface being defined in accordance with the radius of the vane tips.
- According to yet another aspect of the invention, a vane pump is provided and includes a liner having an inlet window and a discharge window, the liner being formed to define a cam surface and a rotor carrying a plurality of radially extending vanes which are forced outwardly such that vane tips thereof contact with the cam surface, the rotor having a direction of rotation such that one end of the inlet window is an upstream end and an opposed end is a downstream end, a radius of each of the vane tips being within a range of approximately 0.114 inches (0.3 cm) to approximately 0.150 inches (0.4 cm), inclusively, and a profile of the cam surface being defined in accordance with the radius of the vane tips.
- These and other advantages and features will become more apparent from the following description taken in conjunction with the drawings.
- The subject matter which is regarded as the invention is particularly pointed out and distinctly claimed in the claims at the conclusion of the specification. The foregoing and other features, and advantages of the invention are apparent from the following detailed description taken in conjunction with the accompanying drawings in which:
-
FIG. 1A shows a vane pump; -
FIG. 1B shows a liner from theFIG. 1A vane pump; -
FIG. 1C shows a liner in accordance with further embodiments; -
FIG. 2 shows an exemplary vane; and -
FIG. 3 shows exemplary vane and cam liner profiles. - The detailed description explains embodiments of the invention, together with advantages and features, by way of example with reference to the drawings.
- A
pump 20 is illustrated inFIG. 1A having arotor 22 carrying a plurality ofvanes 23 withvane tips 231. Thevanes 23 are forced outwardly such that thevane tips 231 abut against acam surface 26, shown here as part of aliner 25. Thevanes 23 are oriented perpendicularly with respect toadjacent vanes 23. Theliner 25 has a substantially eccentric cylindrical shape with therotor 22 disposed in theliner 25 substantially parallel with a longitudinal axis of theliner 25. Theliner 25 is typically mounted within a housing that has a supply of fluid to be pumped towardinlet window 28. -
Pump chambers 24 are formed between thecam surface 26, and adjacent ones of thevanes 23. While not shown, thevanes 23 can move radially inwardly and outwardly of therotor 22. Therotor 22 is mounted eccentrically within theliner 25 and driven to rotate such that the volume of thepump chambers 24 increases as it moves through an inlet portion of a pump cycle, and over theinlet window 28, and then begin to decrease in accordance with movement toward a discharge portion. - As shown in
FIG. 1B , adischarge window 30 is formed circumferentially spaced from theinlet window 28. As shown inFIG. 1C ,multiple discharge windows 30 may be formed circumferentially spaced frommultiple inlet windows 28. - In standard models, a profile of the liner 25 (i.e., the “cam liner profile”) has been determined in accordance with a modified trapezoidal cam profile of standard vane tips. For certain applications, however, contact stresses between the
vane tips 231 and theliner 25 were found to be excessively high. In accordance with aspects and, with reference toFIG. 2 , reduction of the contact stresses is achieved by an increase of a radius, RT, of the vane tips. Normally, when the tip radius, RT, becomes too large, thevanes 23 are no longer able to follow the standard cam liner profile due to geometric constraints and, as a result, the vanes are pinched and lock inside the liner prohibiting further rotation. Here, on the other hand, the standard cam liner profile has been modified to allow for a larger vane tip radius and results in the reduced contact stress by as much as 26%. - With reference to Table 1, these modifications are provided in the “−6R114”, the “−4HR114” and the “−8R150” columns and in comparison to current, standard designs (i.e., the “−6”, the “−4H” and the “−8” columns)
-
TABLE 1 where the major and minor radii refer to transverse radii of the cam liner profile and the displacement value is calculated in accordance with the following equation: Disp := [π · (R2 − r2) − 4 · (R − r) · t] · L Model −6 −4H −8 −6 R114 −4H R114 −8 R150 Major Radius 0.625 0.625 0.485 0.485 0.722 0.722 (inch) R Minor Radius 0.425 0.425 0.365 0.365 0.492 0.492 (inch) r Vane Thickness 0.093 0.093 0.093 0.093 0.093 0.093 (inch) t Vane Tip Radius 0.062 0.114 0.062 0.114 0.114 0.150 (inch) Displacement 0.5561 0.5561 0.4223 0.4223 1.21 1.21 (in3/rev) - That is, the “−4H”, the “−6” and the “−8” are all standard feature models and the “−6R114”, the “−4HR114” and the “−8R150” are modified with new tip radii and in some cases new vane lengths. For the “−6R114” and the “−4R114” cases, two vane elements are needed in order to meet minimum flow and, as such, the
liner 25 ofFIG. 1C may be used. By contrast, one vane element is enough to meet the minimum flow requirement in the “−8R150” case and, as such, theliner 25 ofFIG. 1B may be used. -
TABLE 2 Model −6 −6 R114 −4H −4H R114 −8 −8 R150 Maximum Hertzian 65.67 48.74 69.11 50.58 51.52 46.26 Stress (Ksi) Maximum PV Value 1.029E+08 7.33E+07 1.032E+08 7.14E+07 1.12E+08 9.51E+07 (psi-fpm) - In addition, with reference to Table 2, while the “−4H” and “−6” standard models exhibited high characteristic Hertzian stresses and high PV values, both the “−4HR114” and the “−6R114” modified models had acceptable Hertzian stresses and PV values. Further, while the “−8” standard model and the “−8R150” modified model both had acceptable Hertzian stresses but high PV values, the “−8R150” model can be employed with reduced operational speeds to drop the PV value.
- As described above and, in accordance with embodiments, the radii, RT, of the
vane tips 231 have been increased to between 0.114 inches (0.3 cm) to 0.150 inches (0.4 cm), inclusively. In addition, the profile of theliner 25 has been modified as well. With reference toFIG. 3 , the modification to theliner 25 profile is illustrated and, as shown inFIG. 3 , it may be seen that the liner profile (i.e., r.cam(θ)) is similar to the profile of the tracing defined by the vane tips 231 (i.e., r.tip(θ)) as therotor 22 rotates within theliner 25 up to about the 45 and the 315 degree regions, as measured from a top-dead center 251 of theliner 25. At the degree regions, the profiles diverge from one another. The profiles re-converge at around the 135 and the 225 degree regions. This has the effect of fattening theliner 25 profile around the 45-135 and the 315-225 degree regions. - With the profiles divergent from one another in the 45-135 and the 315-225 degree regions, the
vanes 23 having increasedvane tip 231 radii are removed from contact with thecam surface 26. This removal from contact reduces the stresses and the PV values of the modified models that would otherwise be generated. - While the invention has been described in detail in connection with only a limited number of embodiments, it should be readily understood that the invention is not limited to such disclosed embodiments. Rather, the invention can be modified to incorporate any number of variations, alterations, substitutions or equivalent arrangements not heretofore described, but which are commensurate with the spirit and scope of the invention. Additionally, while various embodiments of the invention have been described, it is to be understood that aspects of the invention may include only some of the described embodiments. Accordingly, the invention is not to be seen as limited by the foregoing description, but is only limited by the scope of the appended claims.
Claims (20)
1. A vane pump comprising:
a liner having an inlet window and a discharge window, the liner being formed to define a cam surface; and
a rotor carrying a plurality of radially extending vanes which are forced outwardly such that vane tips thereof contact the cam surface, the rotor having a direction of rotation such that one end of the inlet window is an upstream end and an opposed end is a downstream end,
a radius of each of the vane tips being approximately 0.114 inches (0.3 cm) and a profile of the cam surface being defined in accordance with the radius of the vane tips.
2. The vane pump according to claim 1 , wherein the plurality of the vanes comprises 4 vanes.
3. The vane pump according to claim 2 , wherein each vane is perpendicular to an adjacent vane.
4. The vane pump according to claim 1 , wherein the profile of the vane surface diverges from a profile of a tracing defined by each of the vane tips as the rotor rotates.
5. The vane pump according to claim 4 , wherein the divergence occurs between the 45-135 and the 315-225 degree positions as measured from a top-dead center of the cam surface profile.
6. The vane pump according to claim 1 , wherein the inlet window is formed as a plurality of inlet windows.
7. A vane pump comprising:
a liner having an inlet window and a discharge window, the liner being formed to define a cam surface; and
a rotor carrying a plurality of radially extending vanes which are forced outwardly such that vane tips thereof contact the cam surface, the rotor having a direction of rotation such that one end of the inlet window is an upstream end and an opposed end is a downstream end,
a radius of each of the vane tips being approximately 0.150 inches (0.4 cm) and a profile of the cam surface being defined in accordance with the radius of the vane tips.
8. The vane pump according to claim 7 , wherein the plurality of the vanes comprises 4 vanes.
9. The vane pump according to claim 8 , wherein each vane is perpendicular to an adjacent vane.
10. The vane pump according to claim 7 , wherein the profile of the vane surface diverges from a profile of a tracing defined by each of the vane tips as the rotor rotates.
11. The vane pump according to claim 10 , wherein the divergence occurs between the 45-135 and the 315-225 degree positions as measured from a top-dead center of the cam surface profile.
12. The vane pump according to claim 7 , wherein the inlet window is formed as a singular inlet window.
13. A vane pump comprising:
a liner having an interior facing cam surface and being formed to define an inlet window and a discharge window; and
a rotor disposed within the liner and carrying a plurality of radially extending vanes which are forced outwardly such that vane tips thereof contact the cam surface during rotor rotation, the rotor having a direction of rotation such that respective one ends of the inlet and outlet windows are upstream ends and that respective opposed ends are downstream ends,
a profile of the cam surface being defined in accordance with the radius of the vane tips such that the profile diverges from a profile of a tracing defined by each of the vane tips as the rotor rotates.
14. The vane pump according to claim 13 , wherein the plurality of the vanes comprises 4 vanes.
15. The vane pump according to claim 14 , wherein each vane is perpendicular to an adjacent vane.
16. The vane pump according to claim 13 , wherein a radius of each of the vane tips is approximately 0.114 inches (0.3 cm).
17. The vane pump according to claim 16 , wherein the divergence occurs between the 45-135 and the 315-225 degree positions as measured from a top-dead center of the cam surface profile.
18. The vane pump according to claim 13 , wherein the inlet window is formed as a plurality of inlet windows.
19. The vane pump according to claim 13 , wherein a radius of each of the vane tips is approximately 0.150 inches (0.4 cm).
20. The vane pump according to claim 19 , wherein the divergence occurs between the 45-135 and the 315-225 degree positions as measured from a top-dead center of the cam surface profile.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US12/973,349 US20120156077A1 (en) | 2010-12-20 | 2010-12-20 | Cam liner profile |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US12/973,349 US20120156077A1 (en) | 2010-12-20 | 2010-12-20 | Cam liner profile |
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US20120156077A1 true US20120156077A1 (en) | 2012-06-21 |
Family
ID=46234690
Family Applications (1)
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US12/973,349 Abandoned US20120156077A1 (en) | 2010-12-20 | 2010-12-20 | Cam liner profile |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN108591057A (en) * | 2018-05-25 | 2018-09-28 | 中国石油大学(华东) | A kind of single-chamber asymmetry sliding-vane-type vacuum pump |
US20190219144A1 (en) * | 2018-01-18 | 2019-07-18 | Hamilton Sundstrand Corporation | Cam liner for integrated drive generator |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5160252A (en) * | 1990-06-07 | 1992-11-03 | Edwards Thomas C | Rotary vane machines with anti-friction positive bi-axial vane motion controls |
US6364630B1 (en) * | 1999-03-06 | 2002-04-02 | Delphi Technologies, Inc. | Vane pump |
-
2010
- 2010-12-20 US US12/973,349 patent/US20120156077A1/en not_active Abandoned
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5160252A (en) * | 1990-06-07 | 1992-11-03 | Edwards Thomas C | Rotary vane machines with anti-friction positive bi-axial vane motion controls |
US6364630B1 (en) * | 1999-03-06 | 2002-04-02 | Delphi Technologies, Inc. | Vane pump |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20190219144A1 (en) * | 2018-01-18 | 2019-07-18 | Hamilton Sundstrand Corporation | Cam liner for integrated drive generator |
EP3514324A1 (en) * | 2018-01-18 | 2019-07-24 | Hamilton Sundstrand Corporation | Cam liner for integrated drive generator |
US10907718B2 (en) | 2018-01-18 | 2021-02-02 | Hamilton Sundstrand Corporation | Cam liner for integrated drive generator |
CN108591057A (en) * | 2018-05-25 | 2018-09-28 | 中国石油大学(华东) | A kind of single-chamber asymmetry sliding-vane-type vacuum pump |
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Legal Events
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AS | Assignment |
Owner name: HAMILTON SUNDSTRAND CORPORATION, CONNECTICUT Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:DEXTER, SARA;NI, WEISHUN;REEL/FRAME:025533/0873 Effective date: 20101214 |
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STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |