US3797977A - Slipper-type pumping element for a pump or motor - Google Patents

Slipper-type pumping element for a pump or motor Download PDF

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Publication number
US3797977A
US3797977A US00314861A US3797977DA US3797977A US 3797977 A US3797977 A US 3797977A US 00314861 A US00314861 A US 00314861A US 3797977D A US3797977D A US 3797977DA US 3797977 A US3797977 A US 3797977A
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United States
Prior art keywords
slipper
spring
pump
ratio
arc
Prior art date
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Expired - Lifetime
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US00314861A
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English (en)
Inventor
R Carlson
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Northrop Grumman Space and Mission Systems Corp
Original Assignee
TRW Inc
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Filing date
Publication date
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    • 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
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0827—Vane tracking; control therefor by mechanical means
    • F01C21/0845—Vane tracking; control therefor by mechanical means comprising elastic means, e.g. springs

Definitions

  • ABSTRACT A slipper vane sealed pump is proportioned in critical relationships between the pumping vane and the cam bore:
  • FIG. 1 of the drawings A typical prior art slipper is depicted in FIG. 1 of the drawings wherein is shown a slipper pumping vane which has been in widespread commercial usage since at least 1965.
  • a slipper pumping veane which has a substantial width to drive ratio (W/D).
  • W/D width to drive ratio
  • the lesser number of slipper pump vanes permits vanes to be utilized which have a large mass (M) and thus the centrifugal force (C.F.) acting on the pumping vanes is higher than for slippers having a smaller mass.
  • the slipper pumping vanes are also characterized by a so-called lift ramp provided for buoying the slipper pumping vane in a generally radially outward direction.
  • the slipper pump vane is perched on the edge of the rotor slot.
  • the pump of the present invention has a slipper construction which afiords a lower width to drive ratio (W/D). Moreover, since a larger number of slippers are utilized, the comparative mass of each respective slipper is reduced, thereby resulting in less centrifugal force (C.F.) being exerted on an individual slipper pumping vane element.
  • W/D width to drive ratio
  • a lift ramp is not required but a so-called plane-in notched in the rotor at the edge of the slot can be utilized.
  • the present invention also provides an underslipper surface curvature affording contact with a spring to avoid excessive column action, thereby reducing spring wear and avoiding increased slipper height.
  • FIG. 1 is a fragmentary cross-sectional view of a prior art arrangement showing a typical slipper pumping vane of the type used in a pump having tangent arc sealing.
  • FIG. 2 is a view similar to FIG. 1 but showing the novel slipper pumping vane of the present invention as embodied in a slipper seal pump as contemplated by the present invention.
  • FIG. 3 is a view similar to FIG. 2 but showing additional details and relationships between the various parts of the pump in accordance with the principles of the present invention.
  • FIG. 4 is an end elevational view of the slipper seal pumping element provided in accordance with the principles of the present invention.
  • FIG. 5 is a side elevational view of the slipper pumping vane element of FIG. 4.
  • FIG. 1 depicts a prior art arrangement which has been in widespread commercial usage since 1965.
  • a cam ring 10 having a cam bore 11 forming the outer wall of a pumping chamber formed with an inlet side and an outlet side, the respective sides being designated by legend.
  • Rotatable within the pumping chamber is a rotor 12 having a plurality of peripheral slots 13 each formed with a bottom wall 14 against which is bottomed one end of a coil spring 16.
  • the other end of the coil spring 16 is engaged against a curved surface or undersurface 17 of a slipper-type pumping element 18 having two outboard areas 19 and 20 on opposite sides of a center recess 21.
  • One of the side flanks of the slipper-type pumping element 18 is formed with a lift ramp 22.
  • the width of the slipper-type pumping element 18 is indicated at W and the depth of the working arc in the pumping chamber is indicated at D.
  • the legend C.F. is indicated to show the effects of centrifugal force and the center of gravity of the pumping vane is shown at C.G. It will be understood that the pump of FIG. 1 uses a tangent arc seal, i.e., the diameter of the rotor 12 seals against the bore wall 11 at a crossover point between the outlet and inlet ports.
  • the bore wall 11 can either be a single-lobed arrangement with a single inlet port and single outlet port or a double-lobed or multiple-lobed pumping chamber can also be provided so that there is more than a single pumping impulse on a single rotation of the rotor 12..By virtue of the prior art arrangement shown in FIG. 1, a lesser number of slippers permits a large mass indicated at M. The slipper of FIG. 1
  • W/D width-to-drive ratio
  • the slipper pumping vane of the present invention is shown generally at 30.
  • the forces acting on the slipper are depicted assuming direction of rotation in a counterclockwise direction, as shown by the arrow 31 applied at the edge of the slot or notch.
  • the driven slipper reacts virtually through a point designated in FIG. 3 at point which constitutes a pivot or rotation point at the front of the slipper pumping vane.
  • the stable case-moments acting on the slipper are:
  • the unstable case-moments are:
  • slipper width (W) measured from the maximum protuberance of each slipper flank to contact depth aspect ratio of W/D 2.6 to 2.8.
  • the slipper per se has a curved flank surface 32 on one side and a curved flank surface 33 on the other side. Further, there is an underslipper surface 34 and an upper slipper surface divided into two sections 36 and 37 separated by a center relieved recess 38. Thus, the upper surface sections 36 and 37 determine the circumferential contact are which is designated C.
  • the contact depth measured on the slipper is from the tangent to the top surface 36 and/or 37 and the center of the driving flank 32 and such depth is indicated at D.
  • slipper bottom contour vis-a-vis the life and operation of the support spring.
  • the wider slipper used in the tangent seal design such as the slipper 18 (FIG. 1) was substantially round, it has been discovered that a particular curve form, as provided by the present invention, is optimal to insure sufficient spring life.
  • the slipper surface or underslipper surface must contact at, or near, the center of the spring in order to avoid excessive column action. An arc is necessary so that surface, rather than point contact, is obtained. That relationship reduces spring wear.
  • the wider slipper used in the tangent seal design such as the slipper 18 (FIG. 1) was substantially round, it has been discovered that a particular curve form, as provided by the present invention, is optimal to insure sufficient spring life.
  • the slipper surface or underslipper surface must contact at, or near, the center of the spring in order to avoid excessive column action. An arc is necessary so that surface, rather than point contact, is obtained. That relationship reduces spring wear.
  • the slipper surface or underslipper surface
  • slipper geometry requires a flat curve to avoid increasing slipper height.
  • the height of the spring is indicated at S,, while the diameter of the spring is indicated at S
  • the underslipper surface curvature be formed as shown at 34 to allow unencumbered spring rock without attrition to the spring in its shrouding guide hole. Analytically, such relationship is defined as a curve whose curvature departs within a range of 2% to 5 percent of the spring radius measured from the spring center.
  • a spring ratio i.e., the ratio of the length of the spring S, to the diameter of the spring 5,, of 1.55/1 or less in the installed position provides the proper relationship for good spring geometry, pump geometry and the dynamic aspects, i.e., the rate of bore acceleration, etc. for a successful pump operation.
  • the pump of the present invention has a housing having a cam bore wall forming a pumping chamber for a pump of the expanding chamber type and specifically including a crossover are disposed between respective inlet and outlet portions of the pumping chamber and a rotor in said pumping chamber having a plurality of circumferentially spaced apart peripheral notches for carrying a corresponding plurality of slipper vanes and such notches and vanes being sufficient in number to position at least one such vane in the crossover arc at all times.
  • the essential relationship pertaining to the slipper cam bore will be established so that an effective slipper seal can be achieved in a pump capable of meeting the noise and high speed durability characteristics in a commercially feasible pump.
  • a pump comprising a housing having a cam bore wall forming a pumping chamber for a pump of the expanding chamber type and specifically includinga crossover are disposed between respective inlet and outlet portions of the pumping chamber,
  • a rotor in said pumping chamber having a plurality of circumferentially spaced apart peripheral notches for carrying a corresponding plurality of slipper vanes and such notches and vanes being sufficient in number to position at least one such vane in the crossover are at all times,
  • slipper width in specified dimension i.e., a slipper width measured from the maximum protuberance of each slipper flank to contact depth aspect ratio of W/D E 2.6 to 2.8
  • a circumferential contact are on the outer surface of said slipper of specified dimension, i.e., a circumferential contact are to contact depth ratio C /D 1.4 to 1.9, and
  • a slipper vane width (W) to contact depth aspect ratio in the order of about from 2.6 to 2.8, wherein W is measured at the maximum protuberance of the slipper vane flank and wherein the contact depth aspect ratio is W/D, D being the depth of the working arc;
  • the underslipper surface curvature is a curve whose curvature departs within a range of in the order of about 2% to 5 percent of the spring radius measured from the slipper center;
  • the spring has a spring ratio of no more than 1.55/1 in the installed position, wherein the spring ratio is the proportion of the length of the spring to the diameter thereof (S /S 3.
  • a slipper having a slipper width W, a contact depth D and a circumferential contact are C and wherein the slipper width measured from the maximum protuberance of each slipper flank to contact depth aspect ratio of W/D 2.6 to 2.8 and wherein the circumferential contact are to contact depth ratio C /D equals 1.4 to 1.9.
  • slipper pump a slipper having an underslipper surface curvature formed to allow unencumbered spring rock without attrition to the spring and its shrouding guide hole,
  • said curvature constituting a curve whose curvature departs within a range of 2% to 5 percent of the spring radius measured from the slipper center.
  • slipper pump as defined in claim 5 said slipper being further characterized by an underslipper surface curvature constituting a curve whose curvature departs within a range of 2% to 5 percent of the spring radius measured from the slipper center.
  • a spring biasing the slipper radially outwardly and having a spring ratio of 1.55/1 or less in the installed position wherein the spring ratio constitutes the proportion of the length of the spring to the diameter thereof.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US00314861A 1972-12-13 1972-12-13 Slipper-type pumping element for a pump or motor Expired - Lifetime US3797977A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US31486172A 1972-12-13 1972-12-13

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US3797977A true US3797977A (en) 1974-03-19

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US00314861A Expired - Lifetime US3797977A (en) 1972-12-13 1972-12-13 Slipper-type pumping element for a pump or motor

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US (1) US3797977A (en(2012))
JP (1) JPS5757633B2 (en(2012))
BR (1) BR7309741D0 (en(2012))
CA (1) CA1011166A (en(2012))
DE (1) DE2360608C3 (en(2012))
FR (1) FR2214339A5 (en(2012))
GB (1) GB1435026A (en(2012))
IT (1) IT1000830B (en(2012))

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4080124A (en) * 1974-11-04 1978-03-21 Trw Inc. Optimum porting configuration for a slipper seal pump
US4083664A (en) * 1976-11-08 1978-04-11 Trw Inc. Rotary hydraulic device with retaining means for pumping element biasing springs
US4201521A (en) * 1978-03-20 1980-05-06 Trw Inc. Pump and motor assembly
US4259044A (en) * 1979-05-15 1981-03-31 Trw Inc. Fuel pump assembly

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2473620A1 (fr) * 1980-01-16 1981-07-17 Sulzer Ag Palette coulissante de rotor de dispositifs hydrauliques ou electrohydrauliques rotatif
EP0065606B1 (fr) * 1981-05-22 1986-10-01 COMPAGNIE DE CONSTRUCTION MECANIQUE SULZER Société anonyme dite: Palette coulissante de rotor de dispositifs hydrauliques ou électrohydrauliques rotatifs

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3200752A (en) * 1963-05-16 1965-08-17 Thompson Ramo Wooldridge Inc Stack-up slipper pump with integral flow control valve
US3645647A (en) * 1970-01-14 1972-02-29 Ford Motor Co Positive displacement fluid pumps

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3081706A (en) * 1960-05-09 1963-03-19 Thompson Ramo Wooldridge Inc Slipper sealing means for a dual acting pump
FR1401709A (fr) * 1964-07-01 1965-06-04 Thompson Ramo Wooldridge Inc Ensemble de pompe à patins empilés et de soupape de forme ramassée

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3200752A (en) * 1963-05-16 1965-08-17 Thompson Ramo Wooldridge Inc Stack-up slipper pump with integral flow control valve
US3645647A (en) * 1970-01-14 1972-02-29 Ford Motor Co Positive displacement fluid pumps

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4080124A (en) * 1974-11-04 1978-03-21 Trw Inc. Optimum porting configuration for a slipper seal pump
US4083664A (en) * 1976-11-08 1978-04-11 Trw Inc. Rotary hydraulic device with retaining means for pumping element biasing springs
US4201521A (en) * 1978-03-20 1980-05-06 Trw Inc. Pump and motor assembly
US4259044A (en) * 1979-05-15 1981-03-31 Trw Inc. Fuel pump assembly

Also Published As

Publication number Publication date
IT1000830B (it) 1976-04-10
AU6302873A (en) 1975-05-29
DE2360608C3 (de) 1979-09-13
DE2360608B2 (de) 1979-01-18
FR2214339A5 (en(2012)) 1974-08-09
DE2360608A1 (de) 1974-07-04
JPS5757633B2 (en(2012)) 1982-12-06
BR7309741D0 (pt) 1974-08-29
JPS4989210A (en(2012)) 1974-08-26
GB1435026A (en) 1976-05-12
CA1011166A (en) 1977-05-31

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