US3790314A - Vane pump having extended undervane suction ports - Google Patents

Vane pump having extended undervane suction ports Download PDF

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US3790314A
US3790314A US00255580A US3790314DA US3790314A US 3790314 A US3790314 A US 3790314A US 00255580 A US00255580 A US 00255580A US 3790314D A US3790314D A US 3790314DA US 3790314 A US3790314 A US 3790314A
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Prior art keywords
vane
suction
undervane
vanes
suction port
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C Adams
J Swain
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Hagglunds Denison Corp
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Abex Corp
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    • 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
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • 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
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses
    • 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
    • F04C2/3446—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 more than one line or surface

Definitions

  • ABSTRACT Improved high speed operation of vane pumps is obtained by the provision of undervane suction ports that are positioned to establish continuing fluid communication with the inner end of each rotor vane slot, angularly beyond the end of the main suction port.
  • the undervane suction port 'advantageously extends in the direction of rotor rotation to a position just short of the point at which it would provide a short circuit connection between thepressure and suction zones.
  • the vanes are mounted in slots in a rotor. As the rotor turns, the tips of the vanes'engage and slide over a cam surface which is around the rotor. The sides of the rotor and the side edges of the vanes are in sliding, sealing engagement with cheek or port plates on opposite sides of the rotor.
  • the cam surface is contoured so that the spacing between it and the rotor periphery varies around'the rotor.
  • This so-called pumping space bounded by the rotor surface, the cheek plates, and the cam surface, is generally regarded as comprising four zones: the pressure zone, the suction zone, a transfer Zone (which lies between the suction zone and the pressure zone in the direction of rotation), and a sealing zone (whichlies between the pressure zone and the suction zone in the direction of rotation).
  • the variations in cam surfacerotor spacing in these zones cause vane movement and consequent changes in the volume of the intervane spaces or transfer pockets between the respective pairs of vanes.
  • a pocket increases in volume 'as it traverses the suction zone, and decreases in volume in the pressure zone.
  • the volume increase at the suction zone occurs because the cam surface recedes from the rotor surface there. This permits the vanes to extend from their rotor slots.
  • the recession of the cam surface from the rotor surface across the suctionzone is called the suction ramp, the term ramp being .used to designate an inclined surface, as opposed to an arc of fixed or constant diameter about the rotor axis.
  • the volume of the intervane is decreased in the pressure zone, where the cam surface has a so-called pressure ramp, which approaches the rotor surface.
  • One or more main suction ports open through each cheek plate, and fluid flows through such main suction ports into the transfer pockets between the pairs of vanes as the vanes sequentially move past it.
  • the front or leading vane of each pocket-defining pair seals and prevents pressure fluid in the pressure zone of the pump from short circuiting by escaping past it to the suction port.
  • the pocket transfers the fluid in it across a transfer zone to the pressure port 'in the pressure zone.
  • the trailing vane of the pocket pair closes or seals the pocket from the main suction port, before the leading vane of the pair has moved far enough to permit communication of the pressure zone with the pocket, in order to prevent internal pressure fluid loss by short circuiting.
  • each transfer pocket fill completely with fluid as it traverses the suction zone.
  • fluid can readily flow into the transfer pockets as they sequentially pass the main suction port, and
  • each vane slot has also provided supplementary means to connect the inner end of each vane slot to an intervane pocket, in .the form of a bore extending angularly from the rotor periphery to the respective vane slot inner end.
  • Such bores are shown in Pettibone U.S. Pat. No. 3,479,962, issued Nov. 25, 1969.
  • inward flow in such rotor bores is restricted by centrifugal force, and such rotor bores would more likely provide an outward flow if an adequate source of fluid were to be provided at the inner end of the rotor slot.
  • an adequate source of fluid were to be provided at the inner end of the rotor slot.
  • the angular dimension of the undervane suction port has been substantially the same as that of the main suction port. Communication between the main suction port and a given transfer pocket cuts off when the trailing vane of the pocket crosses the downstream edge of the main suction port. This occurs when to start its traverse of the major diameter portion or socalled pumping arc of the cam surface. Similarly, it has been the accepted practice in the industry to time the closing of the undervane port to occur (i.e., to cut off communication between the undervane port and the inner end of a vane slot which is passing it) very shortly after the vane has reached its most extended position.
  • main suction port close before the pocket it has been filling comes into communication with the pressure port. If the main suction port closed later with respect to that pocket, there would exist a short circuit path from the pressure port through the pocket, directly to the suction port. Hence, for a very practical reason the main suction port cannot be extended to provide a longer filling space.
  • the extended undervane suction port is preferably closed only just before it would provide a short circuit path for fluid from the pressure zone to escape through it toward the suction zone. Test data has confirmed that such elongation of the undervane ports will extend the linear part of the flow-speed curve, up to higher operating speeds than would otherwise be obtained.
  • the undervane suction port is extended almost to the position at which it would afford a bridge or path between the high pressure zone of the pump and the suction zone, and thereby short circuit the pump. Such short circuiting would be highly undesirable. Nonetheless, it has been found that closure of the undervane suction port only a few degrees ahead of the point of connection to the pressure zone is sufficient to maintain an adequate seal, while at the same time permitting the pump to be run on a lineal part of the flow versus speed curve, at speeds several hundred rpm greater than are possible with conventional undervane port timing.
  • the undervane slot volume is much smaller than the volume of the pocket between adjacent vanes, and it might therefore be thought that less difficulty would be encountered in filling it. It is theorized that cavitation in the under-vane slots has been severe and that an extended undervane fill period overcomes this effect. Also, some fluid in the under-vane slot can flow to the transfer pocket itself,
  • Bubbles arising from cavitation are believed to be most severe just behind the leading vane of a pocket, and these spaces can be filled by fluid from the leading vane slot flowing up from the slot through the vane grooves or balancing holes.
  • This type of bubble filling may be more efficient than filling via the main suction port, since fluid flowing to a moving bubble from the vane in front of it requires less acceleration to reach that space than fluid from the main suction port which must catch up to the bubble from behind.
  • the extended undervane ports enable this two way filling of a pocket (through the main port and the undervane port as well) to continue longer than previously, and this is believed to underlie the improvement in pump operation which the invention provides.
  • FIG. 1 is an axial section through one type of pump having undervane suction porting in accordance with a preferred embodiment of the invention, the pump being a balanced pump with piston actuated, double lip vanes, the section being taken through the suction ports;
  • FIG. 2 is a plan view of the front cheek plate, taken on the line 2-2 of FIG. 1;
  • FIG. 3 is a plan view of the opposite or rear cheek plate, taken on line 3-3 of FIG. 1;
  • FIG. 4 is .a developed section through the undervane suction port, taken on line 4-4 of FIG. 2;
  • FIG. 5 is a fragmentary plan, view of a portion of a rotor and cam ring of the pump shown in FIGS. 1-4, illustrating how the extended undervane suction port provides a longer filling period for the inner end of the vane slot;
  • FIG. 6 is a view similar to FIG. 5 but shows a pump having a conventionally timed undervane suction port in-accordance with the prior art
  • FIG. 7 is a diagrammatic illustration showing the effect of various types of suction zone filling on the maximum speed at which a pump can operate without cavitation.
  • FIG. 8 is a diagrammatic view illustrating the preferred timing as embodied in a pump having single lip vanes.
  • the invention described and claimed herein is broadly applicable to vane pumps in which both the inner and the outer ends of the wines are exposed to fluid at suction zone pressure as they traverse the suction zone of the pump, including pumps which have single lip vanes as well as those which have double lip vanes.
  • the vanes may be actuated by hydraulically operated means, including pistons, or by springs.
  • the invention is first described hereinafter in relation to a balanced pump having hydraulically operated vanes of the pressure balanced, two lip type, but it should be understood that this is by way of illustrationand not limitation.
  • the pump there shown includes a housing or casing formed by a body casting 1 having a generally cylindrical internal chamber, and an end cap 2 having a recessed shoulder 3 which telescopes into one end of the body and is sealed thereto by an O-ring 4.
  • the body and end cap are connected by bolts, not shown.
  • cap 2 has an opening through which the pump operating shaft 6 extends.
  • shaft 6 is supported for rotation by a ball bearing 7 which is secured against axial movement in the opening.
  • a seal 8 prevents the leakage of oil along shaft 6.
  • the shaft extends into body 1 from end cap 2, and at its rear or inner end is carried for rotation by a needle roller bearing 9 mounted within a central bore in the body 1.
  • the end cap 2 supports and is sealed around a front cheek plate 10, sometimes called a port plate, which has a smooth, flat inner surface 11 that bears against a side or radial face 13 of an annular cam ring or stator 14.
  • cam ring 14 On its opposite side surface 17, cam ring 14 bears against a smooth flat surface 18 of a rear cheek or port plate 19, and clamps the latter against an internal shoulder (not shown in FIG. 1) in body 1.
  • the cam ring itself, as well as the housing and cam ring together, are sometimes referred to in the art as a stator.
  • the cam ring 14 is clamped between the two cheek plates by four bolts, not shown, which pass through bolt holes in the cam ring that are aligned with holes in cheek plates 10 and 19.
  • a fluid intake passageway 22 extends radially into body 1 and communicates with a pair of annular channels 23, 24 which encircle the internal cavity within the body. These annular channels 23, 24 distribute fluid from the intake passageway 22 to the suction ports in the cheek plates, to be described.
  • the cam ring 14 is supported radially by an annular rib 26 formed in body 1 between the annular channels 23, 24.
  • the cam ring encircles a rotor 28 which is connected to and driven by shaft 6 through splines 29.
  • the spline joint permits proper running alignment of the rotor between the opposed flat surfaces 11 and 18 of the front and rear cheek plates 10 and 19 respectively. Both cheek plates have central openings through which shaft 6 passes.
  • the rotor has a plurality of radial vane slots 31 (see FIG. 5) in each of which a vane 32 is mounted.
  • the cam ring 14 has an inward facing cam surface 34 that is contoured to provide a balanced or symmetrical pump construction in which suction ramps 34a establishing pairs of diametrically opposite low pressure, inlet or suction zones (one of which is designated at 37 in FIG. 5) and or pressure ramp 34b establishing high pressure, outlet or-exhaust zones (one of which is designated at 38 in FIG. 5).
  • suction ramps 34a establishing pairs of diametrically opposite low pressure, inlet or suction zones (one of which is designated at 37 in FIG. 5) and or pressure ramp 34b establishing high pressure, outlet or-exhaust zones (one of which is designated at 38 in FIG. 5).
  • Each vane engages the cam surface 34 of cam ring 14, and the side edges of the vanes slide over the smooth flat surfaces 11 and 18 of the front and back cheek plates on opposite sides of the rotor.
  • the pairs of adjacent vanes divide the annular pumping space between the rotor, cam surface, and cheek plates into a series of transfer pockets or inter
  • Intake passageway 22 communicates via the annular channel 23, 24 around cam ring 14 through passages cored in the cheek plates 10 and 19, to paired main suction ports spaced 180 apart in surfaces 11 and 18 thereof.
  • Two main suction ports 43 and 44 are formed in front cheek plate 10, as seen in FIG. 2, and are fed through channel 24.
  • Two additional main suction ports 45 and 46 are formed in rear cheek plate 19 (see FIG. 3) and are fed through channel 23.
  • These four main suction ports are aligned with the corresponding suction zones 37 in the pumping space between the rotor periphery 36 and the cam surface 34.
  • Increased filling area for each suction zone may be provided by a bore 33 through the cam ring, for leading fluid from inlet 22 and the outer surface of the cam ring, directly into the suction zone. Such increased main suction area filling means are known in the art.
  • Each main suction port 43 and 44 of the front cheek plate 10 is connected by a branch passage 47, with an undervane suction port 50 in the cheek plate; similarly,
  • each suction port 45 and 46 in rear cheek plate 19 is connected by a passage 48 in the rear cheek plate with an undervane suction port 51.
  • the undervane suction ports 50 and 51 are radially positioned so that the inner ends 49 of the vane slots 31 will pass across them as the rotor turns. (In FIGS. 2 and 3 the inner ends 49 of the vane slots are superimposed in phantom on the cheek plates).
  • the opening of each undervane port 50 and 51 in its cheek plate surface 11 and 18 is sausage shaped, as viewed in plan.
  • Each port 50 and 51 is extended in the direction of rotor rotation (indicated by arrows), by a groove or channel at 58 (see FIG.
  • a shallow drain slot designated at 60 extends radially in the faces 11 and 18 of the respective cheek plates 10 and 19, from the under-vane ports 50 and 51, to the central shaft openings therein. The purpose of this is to provide for draining fluid from the cavity around shaft 6.
  • the front cheek plate 10 includes two diametrically opposed pressure ports 52, 52.
  • the pressure ports are centered substantially from the main suction ports 43 and 44, and they open to the pressure zones 38 between the rotor and the cam surface.
  • the pressure ports 52, 52 are connected through internal passageways (partly shown at 54 in FIG. 1) in cheek plate 10 and end cap 2, to a fluid outlet or delivery coupling 56. In use, coupling 56 connected to an external hydraulic circuit not shown.
  • the cam ring may be aligned with respect to the two cheek plates by dowel pins (not shown in the drawings) projecting from its faces 13 and '17.
  • the dowel pins are registrable in holes 62, 63 in the respective cheek plate surfaces 11 and 18, as is known in the art.
  • each vane 32 has grooved outer and side edges, as designated at 67 (see FIGS. 1 and 5).
  • the grooves 67 reflect the pressure act-- ing on the outer end of the vane into the inner end 49 of the vane slot.
  • Two lips are defined'on the outer end of each vane, on opposite sides of grooves 67.
  • the leading lip is designated at 64 and the trailing lip at 65. Only the front or leading lip 64 of a vane will engage the cam surface 34 in the pressure zone 38 by reason of the inward ramp on the cam surface there, while only the rear or trailing lip 65 will engage the cam surface in the suction zone 37, by reason of the outward direction of the suction ramp (see FIG. 5).
  • a radial bore or cylinder 69 is formed in rotor 28 (FIG. 1), extending inwardly from the inner end 49 of each vane slot 31.
  • the bores 69 are interconnected at their inner ends through an annular chamber 71. Fluid can flow into pressure chamber 71 only through the radial bores 69.
  • a generally cylindrical hollow piston valve element 72 slides in each radial bore 69, and includes an axial bore 73.
  • each piston 72 is conically tapered, and forms a valve with the inwardly facing end surface 68 of the vane.
  • the operation of such pistons is described in the above mentioned US. Pat. No. 3,481,276 andin US. Pat. No. 3,223,044, to which reference is hereby made.
  • vane surface 68 is exposed to the pressure of fluid in slot end 49 which together'with the piston urges the vane outwardly.
  • Fluid from the channels 23, 24 enters the transfer pockets 40 and the inner ends 49 of the vane slots as they sequentially traverse the suction zone 37.
  • This fluid is at low pressure, as designated by the letter S in FIG. 5. Fluid enters these spaces through the main suction ports 43-46, and through the associated under vane ports 50 and 51 as the vanes move outward of the suction ramp to expand the volume of the pocket.
  • FIG. shows two adjacent transfer pockets 40a and 40b.
  • the pocket 40a is bounded by a trailing vane 32a and a leading vane 32b, and is traversing the suction zone, while the preceding pocket 40b is bounded by a leading vane32c and the vane 32b which trails it and is approaching the pressure zone.
  • the inner ends 49 of the slots of vanes 32a, 32b are in communication with the undervane suction ports, one of which is visible at 50.
  • the slot of vane 320 is out of communication with the undervane ports and is almost in communication with the pressure zone.
  • Each pocket 40 is increasing its volumetric size or capacity while either of its adjacent vanes is traversing the suction ramp.
  • the volume increase continues until the trailing vane 32b reachesthe top of the suction ramp. This approximately coincides with the cut-ofi of direct communication between the main suction port and the pocket ahead of that vane. Fluid can flow directly into that pocket through the main suction port until its trailing vane has passed the port. This direct path will be closed when the leading edge of the trailing vane of that pocket has passed the downstream edge 76 of the main port.
  • Fluid can flow into the inner end 49 of the slot containing vane 32b through the undervane ports 50, 51 while they are in communication with it, that is, until the slot end passes beyond the trailing or downstream edge 78 of the undervane port.
  • the undervane suction ports 50 and 51 are extended by the groove 58 and bleed slot 59 in the direction of rotor rotation, past the conventional position shown in FIG. 6, toward but short of the point (indicated at 77 in FIG. 5 in phantom) at which they would act as a short circuit path for pressure fluid from the pressure zone designated by P.
  • the extension permits a longer undervane fill time continuing while the vane completely traverses the transfer zone. It is believed that, in addition to better filling of the vane slot inner end, fluid is slung outwardly by centrifugal force, from the slot inner end via groove 67 and into the pocket behind it through the gap between the trailing vane lip 65 and the cam surface, to insure filling of the pocket. We also believe that undervane cavitation may have been more serious'than was previously realized,and that the prolonged filling time permits filling of bubbles caused by undervane cavitation, as well as in the pocket itself.
  • the extended undervane suction ports can continue to supply fluid to the critical areas long after the leading portion of a pocket has passed the main suction port.
  • the optimum extension of the undervane port is to a point shortpreferably just by a few degrees, typically about 2-5-of the position at which fluid could flow from the pressure zone to the vane slot inner end and through the latter to the undervane suction port. If the undervane port extended beyond the short circuit point illustrated in FIG. 5 by dash-dot line 77, fluid would blow from the pressure zone past the leading edge of vane 32c through vane groove 67, the inner end slot, to the undervane port. Terminating the extension of the undervane-port somewhat prior to the short circuit point is necessary to provide an effective seal at the rotor side surface. The approximate. 2-5 spacing mentioned above has been found entirely adequate for this purpose.
  • the provision of the extended undervane ports demonstrably improves pump operation at high speed. This is illustrated in FIG. 7, which compares maximum speeds of operation without cavitation for four pumps which differ in the means .of filling in the suction zone.
  • a pump having standard suction porting (as illustrated in FIG. 6) fills without cavitating up to a maximum speed of about 2,300 rpm.
  • the provision of an increased main suction filling area (as shown at 33) raises the maximum fill speed by about 100 rpm, to about 2,400 rpm.
  • Inclusion of extended undervane ports, in accordance with the invention, in the standard pump (without use of an increased main suction filling area), provides a maximum filling speed of about 2,550 rpm.
  • Use of both extended undervane ports and the bores 33 raises the limit to about 2,650 rpm. Only then does the pump begin to depart from linear operation. This thus indicates the reduction in cavitation and the improvement in filling that the invention provides.
  • FIG. 8 shows diagrammatically a single lip vane pump having extended undervane porting.
  • the slot inner end 79 of the trailing vane of a pocket 83 remains in communication with the undervane port 80 as single lip vane 90 traverses the transfer zone.
  • the undervane port communication continues to a point just short of the position (indicated at 84 in phantom) at which pressure fluidfrom the pressure port 85 acting behind the leading vane 86 of-the pocket, could flow into it through the pressure balancing port 87 of the vane.
  • the invention can be utilized in two-lip vane type reversible pumps, provided the pump has a slight outward ramp on the minor diameter such as is described in the copending application of Adams, Swain and Wilcox, titled Vane Pump with Ramp on Minor Diameter, Ser. No. 246,774, filed Apr. 24, 1972, to which reference is hereby made.
  • the vanes may short circuit pressure fluid over the trailing vane lip, into the vane slot in the rotor, and on out to the suction port through the undervane port extensions. This can happen if the leading vane lip contacts an imperfect cam surface as described in the above copending application. Such a combination can cause vane blow down," resulting in noisy and rough operation. The proper ramp on the minor cam diameter can prevent this problem.
  • the port is formed so that an extension (which may be similar to that at 58 and 59) projects in both directions from the center of the port, rather than only in one direction as shown in FIG. 2.
  • the extension in the direction of rotor movement will function as described above.
  • the extension in the opposite direction will extend'under the minor diameter; it will help provide filling at the start of the suction ramp, and the outward ramp on the minor diameter will prevent pressure from blowing over the tip of the vanes and there will be no short circuiting or harmful effect.
  • bleed slots shown at 59 in the drawings are not essential to the invention, and they can be omitted in the extension of the undervane port.
  • a vane type hydraulic pressure energy translating device including a stator, a rotor rotatable with respect to said stator, said stator presenting a cam surface including a suction ramp, a pressure ramp spaced from said suction ramp, and a pumping are between said suction ramp and said pressure ramp in the direction of rotor rotation from said suction ramp, said rotor having vane slots with vanes mounted in the respective slots, said vanes having inner ends within the vane slots and outer ends which are held in sliding engagement against the said cam surface, a space between each pair of adjacent vanes comprising a transfer pocket, said cam surface in cooperation with the rotor and a pair of check plates defining a pumping space, a main suction port and a pressure port in said cheek plates, and an undervane suction port communicating with the main suction port for admitting fluid to the respective vane slots below the inner ends of the vanes therein,
  • said undervane suction port extends substantially beyond said suction ramp in the direction of rotor rotation to an angular position at which a vane whose slot is in communication with said undervane suction port is part way across said pumping arc,
  • vanes are double lip vanes.
  • vanes are single lip vanes.
  • passageways are provided in either the rotor or the vanes for establishing a fluid flow path from the undervane suction port into a transfer pocket while the leading vane of said pocket is on said pumping arc and said undervane suction port is in communication with the slot containing said leading vane.
  • passageways include grooves in the vanes connecting the inner ends of the vanes with the outer ends thereof.
  • vanes are double lip vanes having a leading lip and a trailing lip
  • said pumping arc has an inward slope so that the trailing lip of each vane is spaced from the pumping arc as the vane moves over said arc with the leading lip in engagement therewith
  • each vane provides fluid communication from the inner end of the vane in the vane slot to the outer end of the vane, the spacing'of the trailing lip from the pumping are thereby permitting flow across the trailing lip of the vane to the transfer pocket which follows the vane.
  • a vane type hydraulic pressure energy translating device including a stator, a rotor rotatable with respect to said stator, one of said stator or said rotor presenting a cam surface including a suction ramp, a pressure ramp spaced from said suction ramp, and a pumping arc between said suction ramp and said pressure ramp in the direction of rotor rotation from said suction ramp, the other of said stator and said rotor having vane slots with vanes mounted in'the respective slots, said vanes having inner ends within the vane slots and outer ends which are held in sliding engagement against the said cam surface, a space between each pair of adjacent vanes comprising a fluid pocket, said cam surface in cooperation with the rotor and a pair of check plates defining a pumping space, a main suction port and a pressure port in said cheek plates, said main suction port communicating with each fluid pocket sequentially to admit fluid thereinto and an undervane suction port communicating with the main suction port for admitting fluid to the respective vane slots below the inner ends
  • said undervane suction port extends substantially'beyond said suction ramp in the direction of rotor rotation to an angular position at which a vane whose slot is in communication with said undervane suction port is a substantial distance across said pumping are, thereby providing continuing suction port communication to the inner ends of the respective vanes while they are traveling on said pumping arc, said undervane suction port terminating short of a position at which pressure fluid could short circuit from said pressure port to said port.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4035115A (en) * 1975-01-14 1977-07-12 Sundstrand Corporation Vane pump
DE2946438A1 (de) * 1978-12-01 1980-06-12 Abex Corp Drehschieberpumpe
US4608002A (en) * 1982-02-08 1986-08-26 Hitachi, Ltd. Rotary vane compressor with hook-like suction passage
US4702684A (en) * 1981-10-07 1987-10-27 Hitachi, Ltd. Slide vane type compressor with increased suction part-cross-sectional area
US4746280A (en) * 1987-02-19 1988-05-24 Corken International Corporation Sliding vane pump
US4747764A (en) * 1985-01-14 1988-05-31 Frasca Joseph F Rotary fluid pump
US4869648A (en) * 1987-03-21 1989-09-26 Lucas Industries Public Limited Company Vane type rotary fuel pump
EP0816680A2 (de) * 1996-06-29 1998-01-07 LuK Fahrzeug-Hydraulik GmbH & Co. KG Flügelzellenpumpe
FR2834317A1 (fr) * 2001-12-27 2003-07-04 Luk Fahrzeug Hydraulik Pompe
US6589033B1 (en) 2000-09-29 2003-07-08 Phoenix Analysis And Design Technologies, Inc. Unitary sliding vane compressor-expander and electrical generation system
EP1818502A2 (de) * 2005-12-13 2007-08-15 Kayaba Industry Co., Ltd. Flügelzellenpumpe
US20100028181A1 (en) * 2006-06-02 2010-02-04 Norman Ian Mathers Vane pump for pumping hydraulic fluid
CN103842619A (zh) * 2011-09-29 2014-06-04 Zf操作系统有限公司 容积式泵
US10788112B2 (en) 2015-01-19 2020-09-29 Mathers Hydraulics Technologies Pty Ltd Hydro-mechanical transmission with multiple modes of operation
CN112648181A (zh) * 2020-12-04 2021-04-13 江苏湖润泵业科技有限公司 具有内凹式叶片的叶片泵
US10995757B2 (en) * 2016-06-22 2021-05-04 Pierburg Pump Technology Gmbh Dry-running gas vane pump having a first fluid outlet and a second fluid outlet associated with the pump chamber with the second fluid outlet permanently open to atmosphere without being impeded
US11085299B2 (en) 2015-12-21 2021-08-10 Mathers Hydraulics Technologies Pty Ltd Hydraulic machine with chamfered ring
US11168772B2 (en) 2009-11-20 2021-11-09 Mathers Hydraulics Technologies Pty Ltd Hydrostatic torque converter and torque amplifier
US11255193B2 (en) 2017-03-06 2022-02-22 Mathers Hydraulics Technologies Pty Ltd Hydraulic machine with stepped roller vane and fluid power system including hydraulic machine with starter motor capability

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CS260235B1 (en) * 1986-10-21 1988-12-15 Jiri Rybnicek Positive-displacement sliding-vane pump
JPH0393524U (de) * 1990-01-12 1991-09-24
CN102720630B (zh) * 2012-06-08 2014-09-24 燕山大学 双转子壳体转动凸轮连杆滚柱多速马达

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3025802A (en) * 1957-04-08 1962-03-20 Eaton Mfg Co Rotary pump
US3067831A (en) * 1960-08-15 1962-12-11 Peters Company Hydraulically driven motorized wheel
US3223044A (en) * 1963-07-18 1965-12-14 American Brake Shoe Co Three-area vane type fluid pressure energy translating devices
US3481276A (en) * 1967-11-27 1969-12-02 Abex Corp Vane tracking in hydraulic pumps

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3025802A (en) * 1957-04-08 1962-03-20 Eaton Mfg Co Rotary pump
US3067831A (en) * 1960-08-15 1962-12-11 Peters Company Hydraulically driven motorized wheel
US3223044A (en) * 1963-07-18 1965-12-14 American Brake Shoe Co Three-area vane type fluid pressure energy translating devices
US3481276A (en) * 1967-11-27 1969-12-02 Abex Corp Vane tracking in hydraulic pumps

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4035115A (en) * 1975-01-14 1977-07-12 Sundstrand Corporation Vane pump
DE2946438A1 (de) * 1978-12-01 1980-06-12 Abex Corp Drehschieberpumpe
US4242068A (en) * 1978-12-01 1980-12-30 Abex Corporation Vane pump with bypass for leakage of fluid when bottom of vane is connected to undervane suction port
US4702684A (en) * 1981-10-07 1987-10-27 Hitachi, Ltd. Slide vane type compressor with increased suction part-cross-sectional area
US4608002A (en) * 1982-02-08 1986-08-26 Hitachi, Ltd. Rotary vane compressor with hook-like suction passage
US4747764A (en) * 1985-01-14 1988-05-31 Frasca Joseph F Rotary fluid pump
US4746280A (en) * 1987-02-19 1988-05-24 Corken International Corporation Sliding vane pump
US4869648A (en) * 1987-03-21 1989-09-26 Lucas Industries Public Limited Company Vane type rotary fuel pump
EP0816680A2 (de) * 1996-06-29 1998-01-07 LuK Fahrzeug-Hydraulik GmbH & Co. KG Flügelzellenpumpe
EP0816680A3 (de) * 1996-06-29 1998-08-26 LuK Fahrzeug-Hydraulik GmbH & Co. KG Flügelzellenpumpe
US5975868A (en) * 1996-06-29 1999-11-02 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Vane pump precompression chamber
US6589033B1 (en) 2000-09-29 2003-07-08 Phoenix Analysis And Design Technologies, Inc. Unitary sliding vane compressor-expander and electrical generation system
WO2003056180A1 (de) * 2001-12-27 2003-07-10 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Pumpe
FR2834317A1 (fr) * 2001-12-27 2003-07-04 Luk Fahrzeug Hydraulik Pompe
EP1818502A3 (de) * 2005-12-13 2014-06-11 Kayaba Industry Co., Ltd. Flügelzellenpumpe
EP1818502A2 (de) * 2005-12-13 2007-08-15 Kayaba Industry Co., Ltd. Flügelzellenpumpe
US20100028181A1 (en) * 2006-06-02 2010-02-04 Norman Ian Mathers Vane pump for pumping hydraulic fluid
US8708679B2 (en) * 2006-06-02 2014-04-29 Mathers Hudraulics Pty. Ltd. Vane pump for pumping hydraulic fluid
US11168772B2 (en) 2009-11-20 2021-11-09 Mathers Hydraulics Technologies Pty Ltd Hydrostatic torque converter and torque amplifier
CN103842619A (zh) * 2011-09-29 2014-06-04 Zf操作系统有限公司 容积式泵
US10788112B2 (en) 2015-01-19 2020-09-29 Mathers Hydraulics Technologies Pty Ltd Hydro-mechanical transmission with multiple modes of operation
US11085299B2 (en) 2015-12-21 2021-08-10 Mathers Hydraulics Technologies Pty Ltd Hydraulic machine with chamfered ring
US10995757B2 (en) * 2016-06-22 2021-05-04 Pierburg Pump Technology Gmbh Dry-running gas vane pump having a first fluid outlet and a second fluid outlet associated with the pump chamber with the second fluid outlet permanently open to atmosphere without being impeded
US11255193B2 (en) 2017-03-06 2022-02-22 Mathers Hydraulics Technologies Pty Ltd Hydraulic machine with stepped roller vane and fluid power system including hydraulic machine with starter motor capability
CN112648181A (zh) * 2020-12-04 2021-04-13 江苏湖润泵业科技有限公司 具有内凹式叶片的叶片泵
CN112648181B (zh) * 2020-12-04 2022-04-01 江苏湖润泵业科技有限公司 具有内凹式叶片的叶片泵

Also Published As

Publication number Publication date
FR2186073A5 (de) 1974-01-04
CA969029A (en) 1975-06-10
JPS5332526B2 (de) 1978-09-08
GB1423545A (en) 1976-02-04
DE2326627B2 (de) 1980-03-06
DE2326627A1 (de) 1973-12-20
IT977190B (it) 1974-09-10
JPS4926806A (de) 1974-03-09
DE2326627C3 (de) 1980-10-30

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