US3827836A

US3827836A - Metering pump

Info

Publication number: US3827836A
Application number: US00360328A
Authority: US
Inventors: E Scheibe
Original assignee: Motors Liquidation Co
Current assignee: Motors Liquidation Co
Priority date: 1973-05-14
Filing date: 1973-05-14
Publication date: 1974-08-06
Anticipated expiration: 1991-08-06
Also published as: DE2422361A1; JPS5014910A; CA993723A; DE2422361B2; GB1436062A

Abstract

An internal combustion rotary engine is provided with an oil metering pump having an engine driven rotor with a cylindrical surface and a pressure control member with a cylindrical surface that is eccentric to the other cylindrical surface and cooperates therewith to provide an annular chamber of varying radial size with an inlet passage supplying oil to this chamber and an outlet port in the pressure control member that is movable about the chamber to receive pressure that increases with increasing rotor speed and also with decreasing radial size of the chamber and the rotor member also having a timing port for intermittently delivering fluid from the outlet port to an outlet passage to effect oil metering for engine seal lubrication at a rate which increases with increasing engine speed and also with increasing throttle opening.

Description

United States Patent [191 Scheibe [451 Aug. 6, 1974 METERING PUMP Inventor: Elias W. Scheibe, Grand Rapids,

Mich.

Assignee: General Motors Corporation,

Detroit, Mich.

Filed: May 14, 1973 Appl. No.: 360,328

References Cited UNITED STATES PATENTS 6/1962 Sternlicht 415/90 11/1973 Brumfield 415/90 Primary Examiner-Carlton R. Croyle Assistant Examiner-Michael Koczo, Jr. Attorney, Agent, or Firm-Ronald L. Phillips 5 7] ABSTRACT An internal combustion rotary engine is provided with an oil metering pump having an engine driven rotor with a cylindrical surface and a pressure control member with a cylindrical surface that is eccentric to the other cylindrical surface and cooperates therewith to provide an annular chamber'of varying radial size with an inlet passage supplying oil to this chamber and an outlet port in the pressure control member that is movable about the chamber to receive pressure that increases with increasing rotor speed and also with decreasing radial size of the chamber and the rotor member also having a timing port for intermittently delivering fluid from the outlet port to an outlet passage to effect oil metering for engine seal lubrication at a rate which increases with increasing engine speed and also with increasing throttle opening.

12 Claims, 17 Drawing Figures PAIENTEUMJB 61914 3.827.836

SHEEI 1 BF 4 my .1 J 2 t w T W; fi a; a \m w BER ANGULAR MENT EM VE PRESSURE CONTROL M MO PAIENTEU M99 same or 4 PRESSURE CONTROL MEMBER ANGULAR MOVEMENT PAIENIEnAus slam saw u or 4 This invention relates to fluid metering pumps and more particularly to a fluid metering pump that meters.

fluid at a rate that varies with varying speed and also constant speed.

In the lubrication of a rotary engines gas seals it is current practice to supply oil therefor at a rate that increases with engine load. As is well known, this may be accomplished by metering the oil at a rate that increases with increasing engine speed and torque demand as indicated by engine throttle opening. While there are commercial pumps that presently produce such oil metering operation, there is a continuing effort for simplification and reduction in size of the pump coupled with enhanced reliability and reduction in cost.

The metering pump according to the present invention is directed to such goals particularly to those of providing a low cost durable structure and comprises a pump body that is securable to the engines housing and has a bore in which a rotor with a cylindrical outer surface is rotatably mounted. The rotor is driven by the engine and has received thereabout a pressure control member which is mounted to turn through a limited angle in the pump body under the control of the engine throttle and has a cylindrical inner surface eccentric to that of the rotor member. These cylindrical surfaces cooperatively provide an annular chamber therebetween with a varying radial dimension such that on oil delivery to this chamber the rotor picks up this oil and carries it in the direction of decreasing radial chamber size thereby creating a pressure therein as in a journal bearing. The pressure thus developed increases with increasing rotor speed and also varies about the chamber increasing with decreasing radial chamber size in the direction of rotor rotation as the smallest clearance between the rotor and pressure control member is approached. An outlet port in the pressure control member connects with the chamber and as rotor speed increases the pressure increases at this port at some constant location to provide increasing flow therethrough. On the other hand, the outlet port is movable with the pressure control member to different locations along the pressure distribution profile of the chamber so that on turning the pressure control member the pressure at this point is varied to effect flow therethrough that increases with increasing engine throttle opening while engine speed remains constant. The rotor also has a timing port which periodically connects the outlet port with the pumps outlet discharge passage during rotor rotation so that oil is intermittently delivered therethrough for seal lubrication at a rate that increases with increasing throttle opening and increasing engine speed. It will also be obvious that this pump can be used for other applications where a variably controllable intermittent or continuous fluid supply is desired recognizing that the pump provides variable flow with constant speed and also variable flow with variable speed.

An object of the present invention is to provide a new and improved metering pump providing variable flow with constant speed.

Another object is to provide a new and improved metering pump providing variable flow with variable speed.

Another object is to provide a new and improved metering pump providing variable flow with constant speed and also variable speed.

Another object is to provide a metering pump providing variable flow with constant speed with journal bearing type pumping action.

Another object is to provide a new and improved metering pump for a rotary engine that meters oil for engine seal lubrication according to engine load.

Another object is to provide a metering pump with journal bearing type pumping action that meters oil for gas seal lubrication in a rotary engine at a rate that increases with increasing engine speed and increasing engine throttle opening.

Another object is to provide a rotary engine oil metering pump having throttle and engine speed controlled flow for gas seal lubrication with journal bearing type pumping action.

These and other objects of the present invention will become more apparent with reference to the following description and drawings in which:

FIG. 1 is an elevational view with parts in section and parts shown diagrammatically of a rotary combustion engine having an oil metering pump according to one embodiment of the present invention.

FIG. 2 is an enlarged longitudinal view with parts in section of the pump shown in FIG. 1.

FIG. 3 is a view of the pump taken along the line 3-3 in FIG. 2 with the engine housing removed.

FIGS. 4, 5 and 6 are views taken along the line 4-4 in FIG. 2 and show pressure distribution in the chamber of the pump in various positions of the pump s pressure control member.

FIG. 7 is an enlarged view similar to FIG. 4 of a modi fication of the pump in FIGS. 1 6 to provide varying geometrical relationship between the pumps rotor and pressure control member.

FIG. 8 is a view similar to FIG. 2 of a modification of the pump in FIGS. 1 6 to provide dual delivery.

FIG. 9 is a view similar to FIG. 2 of another modification of the pump in FIGS. 1 6 to provide dual delivery.

FIG. 10 is a partial view of a modification of the pumps in FIGS. 8 and 9 to provide internal venting.

FIG. 11 is a cross-sectional view showing a modification of the pumps in FIGS. 8 and 9 to provide three separate deliveries.

FIG. 12 shows a modification of the pump in FIG. 9 to provide different deliveries.

FIG. 13 shows a modification of the timing port of the pump in FIG. 12.

FIG. 14 shows another modification of the timing port of the pump in FIG. 12.

FIG. 15 shows a modification of the timing port and outlet passage of the pump in FIGS. 1 6.

FIG. 16 shows a modification of the pump in FIG. 15 to provide dual delivery.

FIG. 17 is a view similar to FIG. 2 of another embodiment of the pump according to the present invention with the pressure control member at the opposite end of the pump from the drive end.

Referring to FIG. 1, there is shown a rotary combustion engine 10 having an oil metering pump 12 according to one embodiment of the present invention that meters oil to lubricate the engines gas seals. The engine 10 comprises a stationary outer body or housing 13 having a rotor cavity that is defined by an inwardly facing peripheral wall 14 and a pair of opposed side walls 16, only one of which is shown. The peripheral wall 14 is in the shape of a two-lobed epitrochoid or a curve parallel thereto and a rotor 18 having the general shape of a triangle with three convex peripheral faces 20 is mounted within the rotor cavity on an eccentric 22 of a crankshaft 24 which is rotatably mounted outboard of the rotor cavity in the side walls 16. An annular externally toothed gear 26 is received about and concentric with the crankshaft 24 and is rigidly secured to the engine housing 13. The gear 26 meshes with an internally toothed gear 28 that is concentric with and fixed to one side of the rotor 18. The gear 28 has 1 /2 times the number of teeth as the gear 26 with the result that this gearing enforces a fixed cyclic relation between the rotor and the crankshaft such that the crankshaft which is the engines output shaft makes three complete revolutions for every one complete revolution of the rotor. The rotor faces 20 cooperate with the peripheral wall 14 and with the side walls 16 to define three variable volume working chambers 30 that are spaced around and move with the rotor within the housing as the rotor orbits within the rotor cavity.

A carburetor 32 supplied with fuel by a pump 34 from a fuel tank 36 delivers an air-fuel mixture to an intake manifold 38 under the control of the carburetor's throttle valve whose opening is controlled by a throttle lever 40 that is connected at one end to the throttle valves shaft 41. The other end of lever 40 is pivotally connected to a rod 42 that is linked to an accelerator pedal, not shown, for control by the vehicle operator, the throttle valve arrangement being such that it is opened when the throttle lever 40 is pivoted in a counterclockwise direction as viewed in FIG. 1. The intake manifold 38 is connected in the engine housing 13 to deliver the air-fuel mixture to opposed intake ports 44, only one of which is shown, in the side walls 16. On rotor rotation in the direction indicated by the arrow in FIG. 1, air-fuel mixture is sequentially periodically admitted to the chambers 30 by the traversing motion of the rotor relative to the intake ports 44 whereafter the air-fuel mixture is trapped and then compressed in readiness for ignition. Sequential ignition of the air-fuel mixture in the chambers 30 is effected by two

spark plugs

46 and 48 which receive timed ignition pulses from a distributor 50 whose shaft 52 is driven by the crankshaft 24, this drive being effected by a pinion 54 which is secured to a mid-portion of the distributor shaft 52 and meshes with a worm gear 56 formed or fixed on the crankshaft 24. The electrodes of the two

spark plugs

46 and 48 are open to the chambers 30 through the peripheral wall 14 and are peripherally spaced thereabout so that the plug 46 is said to trail the other plug 48. Th

spark plugs

46 and 48 may be tired together or only one fired according to certain engine operating conditions as is well known in the art.

With combustion, the peripheral wall 14 takes the reaction to force the rotor 18 to continue rotating and eventually each working chamber following the expansion phase is exhausted to an exhaust manifold 58 via an exhaust port 60 that is open to the rotor cavity through the peripheral wall 14 and is periodically traversed by the rotor apexes.

Sealing of the chambers 30 is effected by apex seals 62 each of which extends the width of the rotor and is mounted at a rotor apex, comer seals 64 each of which is mounted in a rotor side at each rotor apex, and side seals 66 each of which is mounted in a rotor side and extends between pairs of corner seals with the corner seals each providing a sealing link between the adjacent ends of two side seals and one apex seal. The apex seals 62 are urged radially outward by spring means, not shown, to continuously engage the peripheral wall 14 and both the corner seals 64 and side seals 66 on both rotor sides are urged axially outward by suitable spring means, not shown, to continuously engage the side walls 16. In addition, there is provided a circular oil seal 68 mounted in a concentric groove in each rotor side that is biased axially outward by suitable spring means, not shown, to continuously engage the opposite side wall 16 to prevent oil that is used for lubrication of the crankshaft and other rotating parts from moving radially outward to the gas seals.

The oil metering pump 12 according to the present invention is well suited to metering oil for delivery to the rotary engine of the above type via a gas seal lubrication system like that described in copending US. application Ser. No. 271,785, entitled Rotary Engine Gas Seal Lubrication System, filed July 14, 1972 by James M. Casey. In this type of gas seal lubrication system the metered oil is supplied to a pair of oil feed ports 70, only one of which is shown, that are located in the side walls 16. The oil feed ports 70 are located opposite each other at the same radial and angular locations relative to the crankshaft axis and close to and past the side wall intake ports 44 in the direction of rotor rotation so that they are traversed or wiped by the respective rotor side seals during rotor motion the same as the side wall intake ports 44. With this arrangement the side wall oil feed ports 70 feed oil onto the side walls as the side seals sequentially wipe past after having wiped past the side wall intake ports. Most of the oil thus delivered is wiped across the side walls and the remainder is thrown by centrifugal force to lubricate the peripheral wall. For further details of such a gas seal lubrication system reference should be made to the aforementioned Casey patent application.

Describing now the embodiment of the oil metering pump whose details are shown in FIGS. 2 6, there is a one-piece pump body 72 which is secured by a pair of bolts 74 to the underside of the engine housing 13.

, As shown in FIG. 2, the pump body 72 has a bore 75 which is bored from the upper end of the pump body 72 and is closed at the other end and is axially aligned with the distributor shaft 52. An elongated rotor member 76 having an external cylindrical surface 77 is rotatably mounted in the bore 75 and at its upper end extends through an aperture 78 in the engine housing 13 and has a reduced diameter portion 79 having a tongue 80 which is received in a slot 81 in the lower end of the distributor shaft 52 whereby the rotor member 76 is driven by the engine. A ring-shaped pressure control member 82 having concentric outer and inner

cylindrical surfaces

83 and 84 is mounted in the upper end of the pump body 72 with the outer cylindrical surface 83 received in a pump body bore 85 that is contiguous with and eccentric to the bore 75. The inner cylindrical surface 84 is radially opposite and eccentric with respect to the outer cylindrical surface 77 of the rotor member 76 and the pressure control member 82 further has a bore 86 concentric with its other cylindrical surfaces through which the rotor portion 79 extends to make connection with the distributor shaft 52.

Referring to FIGS. 2 and 3, pressure control member 82 is turnable in bore 85 by a control lever 87 which has a hub 88 with a partially circular, partially flat aperture 89 received on a correspondingly-shaped peripheral portion 90 of the upper end of the pressure control member 82 whereby relative rotation between these members is prevented. As shown in FIG. 2, the upper end of the pressure control member 82 has a reduced diameter cylindrical portion 91 which is concentric with the pressure control member's other cylindrical surfaces and fits in the aperture 78 in the engine housing 13 to pilot the pump body 72 on the engine housing for engagement of the pump rotor member 76 with the distributor shaft 52 while permitting turning of the pressure control member 82. With the pump bolted to the engine, the pressure control member 82 is trapped by the engine housing in the pump body 72 with some end clearance being provided to allow radial movement of the pressure control member 82 while preventing leakage between this members lower annular end 92 and step 93 in the pump body between bores 75 and 85. Thus, while the rotor member 76 is being driven by the engine, the pressure control member 82 may be turned about its axis 94 which is spaced from axis 95 of the rotor member 76 by turning the lever 87 with the pressure control member 82 being journaled at its upper end for such movement in the engine housing 13 and at its lower end in the bore 85 which is eccentric by the same amount with respect to the rotor axis 95. O-ring seals 96 and 97 are mounted in accommodating external annular grooves in the

cylindrical surfaces

91 and 83 of the pressure control member 82 to prevent leakage between the pressure control member and the engine housing 13 and between the pressure control member and the pump body 72, respectively, the former sealing being to prevent leakage from the engine and the latter being to prevent leakage from the pump assembly.

The pump 12 has a pump chamber 98 that is defined by the eccentric

cylindrical surfaces

84 and 77 of the pressure control member 82 and rotor member 76, the step 93 of the pump body 72, and a step 99 in the interior of the pressure control member 82 between

bores

84 and 86 against which a shoulder 100 on rotor member 76 runs. The chamber 98 thus formed between the rotor member 76 and the pressure control member 82 is annular and has a varying radial dimension whose minimum is indicated as l0lin FIG. 4 measured along a line drawn through the axes of these two members with this dimension gradually increasing in either direction about the chamber and reaching a maximum which is indicated as 102 directly opposite the minimum radial dimension of the chamber. Engine lubricating oil is drained from the engine lubrication system in the bottom of the engine housing 13 via bore 86 and then a drilled passage 103 in the pressure control member 82 through step 99 to chamber 98 in the vicinity where the clearance is largest between rotor member surface 77 and pressure control member surface 84, this chamber region being in effect the pumps internal sump which is indicated as 107. With the structure thus far described and on supply of oil to chamber 98 as rotor member 76 rotates at constant speed in the direction indicated by the arrow in FIGS. 4 6, there will result an oil pressure distribution against a constant head as in a journal bearing as indicated by the curve 104 in these figures wherein the pressure starts increasing rapidly in the direction of rotor member rotation at a point about midway between maximum radial chamber size 102 and minimum radial chamber size 101 with this pressure peaking just before the minimum radial chamber size and thereafter decreasing at a faster rate until the minimum radial chamber size or clearance is reached whereafter pressure goes slightly negative before returning to the inlet or supply pressure level. According to journal bearing pumping theory. oil may be drawn off from some fixed location in this pressure distribution region and there will result a pumped flow which increases in almost direct proportion to increasing speed. Utilization of this pressure distribution to provide variable pump pressure and thus variable flow at constant speed in addition to the ability to provide increasing flow with increasing speed is effected by an outlet port 106 drilled through the pressure control member 82 at or near the smallest radial section thereof to open through cylindrical surface 84 to the chamber 98 in the pressurized region. Then as the rotating rotor member 76 picks up oil from the pump chambers sump region 107 and carries it in the direction of decreasing clearance creating an increasing pressure distribution therealong, oil may be trapped off anywhere along this pressure distribution region through the outlet port 106 with the result that as the speed of the rotor member 76 increases with the outlet port 106 at any location along the pressure distribution region, the pressure at this port location increases resulting in increased flow through the outlet port and in addition for any constant speed of the rotor member 76 the pressure at the outlet port 106 increases resulting in increased flow through-this port as it is moved by turning of the pressure control member 82 in the direction of locating this port at higher pressure along the pressure distribution region. In the latter operation, turning the pressure control member 82 about its axis effects no change in the minimum clearance between the pump chambers two cylindrical surfaces so that the chamber 98 and thus the pressure distribution location does not in effect turn while the fluid receiving port 106 is moved relative thereto to locations of higher or lower pressure with turning of the pressure control member 82. For example, when the pressure control member 82 is turned to locate the fluid receiving port 106 at the peak of the pressure distribution curve 104 which depicts the case when there is no oil pressure tap, there occurs maximum flow from the chamber to the outlet port 106 with the pressure distribution then assuming an upstream and downstream profile as indicated by the curve 108. The flow is reduced by turning the pressure control member 82 counterclockwise to locate the outlet port 106 at a lower pressure that effects such flow as shown in FIG. 5 with minimum flow occurring on continued turning of the pressure control member 82 to locate the outlet port 106 at the lowest pressure in the chamber that will produce flow as indicated in FIG. 6. Thus, by simply turning the pressure control member 82 the pressure and thus the flow to the outlet port 106 may be varied from a maximum as indicated in FIG. 4 to some intermediate pressure and flow as indicated in FIG. 5 and then to a minimum pressure and flow as indicated in FIG. 6.

Oil is delivered by the outlet port 106 to an annular channel 113 formed by an annular groove on the lower outer corner of the pressure control member 82 cooperating with the lower outer comer of the pump body bore 85 as shown in FIG. 2. Oil in the channel 113 is then transmitted in the pump body 72 via a longitudinally extending drilled passage 117 and then a radially drilled passage 118 which intersects at its inner end with the bore 75 near the latters closed end, the passage 118 being plugged at its outer end by a press-fitted ball 119. A rotary timing port 120 provided by a slot in the cylindrical surface 77 of the rotor member which slot extends through the lower end thereof is located to periodically register with the passage 118 during rotor member rotation and on such registry provides connection between the passage 1 l8 and a chamber 121 which is formed by an enlarged diameter portion of the pump body bore 75 at the closed end and the pointed lower end of the rotor member 76 which bears thereagainst as shown in FIG. 2. Thus, the timing port 120 receives oil from the pump section at a rate which can increase with constant pump speed and/or increasing pump speed and acts as a valve to provide intermittent delivery of such flow to the chamber 121. An outlet nipple 122 formed integral with the pump body 72 has an outlet passage 124 therethrough that is open to the chamber 12] and is connected via a hose 126 fitted to the nipple to deliver the intermittent outlet flow from the pump to the oil metering ports 70 in the engines side walls 16 as shown in FIG. 1.

The pressure control member 82 is made throttle responsive by its lever 87 being linked with the engine throttle so that the outlet port 106 is located at higher chamber pressure locations with increasing engine throttle opening. This is accomplished by the lever 87 having a swivel 128 secured thereto that slidably receives a rod 129 which after it passes through the swivel has a retaining ring 130 clamped or otherwise secured thereto and receives a coil spring 131 between the swivel and the retaining ring as shown in FIGS. 1 and 3. The rod 129 is connected by a Bowden wire 132 to a lever 134 which is pivotally supported on the carburetors throttle valve shaft 41 and is engaged by a tang 136 on the throttle lever 40 to pivot counterclockwise to pull the cable as the throttle is opened as shown in FIG. I. The pressure control lever 87 is limited to a pivotal range determined by engagement with angularly spaced stops 138 and 139 formed on the pump body 72 with this range selected to permit positioning of the outlet port anywhere along but not past the pressure distribution range of the pump. The pressure control member 82 is normally biased against stop 139 to position outlet port 106 in its minimum flow position shown in FIG. 6 by a torsion spring 140. Spring 140 is arranged about the pump body and engages at its opposite ends the pump body 72 and the lever 87 so that its force urges counterclockwise movement of this lever and thus pressure control member 82 as viewed in FIGS. 3 6. The linkage coil spring 131 maintains the lever 134 at the carburetor against the throttle lever tang 136 and also yields to permit the pulled rod 129 to slide in the swivel 128 when the control lever 87 engages the other stop 138 in the vicinity of full throttle.

Describing now a typical oil metering operation provided by the oil metering pump 12, the pumps rotor member 76 is driven from the engine crankshaft 24 via the distributor shaft 52 at a speed proportional to engine speed and with the engine throttle closed and the engine idling, the pressure control member 82 is biased by spring 140 to position outlet port 106 at the minimum flow position on the pressure distribution curve as indicated in FIG. 6. In this condition, the outlet port 106 experiences the lowest chamber pressure available to it and the timing port 120 when it opens to the outlet port 106 during each rotor member revolution delivers a shot of oil for seal lubrication according to this pressure and the interval of time it is open. The quantity of oil delivered for seal lubrication is determined to meet the minimum oil requirements which occur at engine idle with no load demand noting that simply varying the width of the timing port 120 and thus its open period will adjust the flow from the pump to meet the requirement. At idle or any constant increased speed of the rotor member 76 and then on an increase in throttle opening, the outlet port 106 is located at a higher pres sure zone of the chamber so that proportionately more oil is forced to flow therethrough for seal lubrication. On the other hand, at idle or any constant increased throttle opening and then on an increase in engine speed, the pressure at outlet port 106 builds proportionately so that proportionately more oil is forced to flow therethrough for seal lubrication. Thus, the oil is metered for seal lubrication at a rate which increases with both increasing engine speed and increasing throttle opening. Furthermore, this outlet flow from the pump is intermittent and can be timed as desired by locating the timing port 120 angularly with respect to the drive tongue 80 so that such flow occurs at the desired time.

The pump according to the present invention is versatile in that various effects on pressure control member movement, magnitude and location of the pressure distribution curve, and the smallest clearance between rotor and pressure control member can be obtained by simply varying the relationship between the cylindrical surfaces of the rotor member and the pressure control member. A simple modification of the FIG. 1-6 embodiment to obtain various effects is shown in FIG. 7 wherein parts similar to those in FIGS. 2 6 are designated by the same numerals but with the suffix letter A added and added matter identified with new numerals. It will be recalled that in the FIG. 1 6 embodiment the outer and inner

cylindrical surfaces

83 and 84 of the pressure control member are concentric. In the FIG. 7 embodiment, the outer cylindrical surface 83A with its axis 94A remains unchanged but the inner cylindrical surface 84A is made eccentric thereto with a center line 142 intermediate axes 94A and 95A. Thus, the center line 142 of the inner cylindrical surface 84A moves in a circular are when the pressure control member 82 is turned about axis 94A with the result that there is an angular shift in the chamber 98A with the minimum clearance 101A instead of remaining constant as in the FIG. 1 6 embodiment now varying. This has the effect of varying pressure and thus flow which will increase with decreasing clearance. This is illustrated in FIG. 7 wherein the pressure control member 82A and the outlet port 106A are shown in solid line with the outlet port 106A positioned relative to the pressure profile 104A for maximum flow and are shown in dash line after counterclockwise movement with the outlet port 106A positioned relative to the pressure profile 104A for minimum flow. The pressure profile 104A after the shift is shown in dash line with peak pressure having increased because of the accompanying decrease in minimum clearance 101A between the chambers cylindrical surfaces 77A and 84A. Be-

cause of this rise in pressure which has the effect of producing more flow for the same angular movement as that in the FIG. 1 6 embodiment, the FIG. 7 embodiment requires less adjustment or angular movement of the pressure control member for the same pressure and flow variation range which may be desirable for certain applications. This substantial reduction is observable by comparison of the pressure control member angular movement indicated in FIGS. 3 and 7.

In the pump structure thus far described, there is single fluid delivery from the pump which will readily meet lubrication requirements for a single rotor engine. While this pump flow may be divided to provide supply for a dual rotor engine it may be desirable to have separate deliveries from the pump to assure evenly divided flow to the two rotor arrangement. A simple modification of the previously described pump structure to provide two separate outlet flows for use with a dual rotor is shown in FIG. 8 wherein parts similar to those in FIGS. 1 6 are designated by the same numerals but with the suffix letter B added and added matter designated by new numerals. In the FIG. 8 embodiment, the outlet nipple 1228 is moved from the end to the side of the pump body 72B so that its outlet passage 1248 now intersects the pump body bore 758 at an intermediate location with the length of the transfer passage 1178 now shortened and the lower end of the timing port 120B in the rotor member 76B now closed so that during rotor member rotation the timing port 1208 is effective to open passage 118B and 1248 as before. It is also shown that there can be added a wave washer 199 to urge pressure control member 828 against the pump body 728 to prevent leakage between channel 1138 and chamber 98B. A second outlet is provided by adding drilled

passages

200 and 201 in the pump body 728 which are similar to and diametrically opposite the passages 117B and 118B, respectively, to form another periodic connection between channel 113B that receives oil from outlet port 1068 and the timing port 1208 as the rotor member 76B rotates. In addition, there is provided another nipple 202 on the pump body 728 with a passage 203 diametrically opposite the other nipple passage 124B and thus at the same angular location as the added radial passage 201 so that the timing port 1208 opens the passage 201 to the outlet passage 203 during each rotor member revolution in addition to opening passage 1188 to outlet passage 1248. Thus, the two

outlet passages

1248 and 203 each receive the same amount of oil delivery from the pump section.

It has also been found possible to deliver oil from the outlet port to a second outlet passage in the pump body without adding additional passages to the pump body as in FIG. 8. This is accomplished by simple modification of the rotor member as shown in FIG. 9 wherein parts .similar to those in FIGS. 1 8 are designated by the same numerals but with the suffix letter C added and added matter designated by new numerals. In the FIG. 9 pump structure, the arrangement of the

passages

117C, 118C, 124C and the timing port 120C is not changed from that in FIG. 8. However, instead of the

additional passages

200 and 201 in the FIG. 8 modification, there is provided an annular groove 204 in the surface 77C of the rotor member 76C that is axially located to continuously remain open to the radial passage 118C as the rotor member 76C turns. Thus, as the rotor member 76C rotates, the timing port 120C will provide direct connection between the passage 118C and the outlet'passage 124C as before but the connection between the passage 118C and the other outlet passage 203C is now provided via the annular passage 204 and then the timing port 120C.

In the FIG. 8 and 9 pump modifications, the chamber at the lower end of the rotor member is closed and it may be desirable to assure venting thereof. This can be accomplished by a simple modification as shown in FIG. 10 wherein parts similar to those in FIGS. 8 and 9 are designated by the same numerals but with the suffix letter D added and added matter designated by new numerals. In FIG. 10, venting of the chamber 121D is simply effected by providing a longitudinally extending vent port 206 in the surface 77D of the rotor member 76D. Vent port 206 is angularly spaced from timing port 120D and extends to the lower end of the rotor member 76D so that it is always open to chamber 121D and extends sufficiently in the other direction so that it periodically opens chamber 121D to the outlet passages 124D and 203D for venting when these outlets are not receiving oil from the timing port 120D.

It may also be desirable to have more than two separate outlets from the pump and this may be accomplished as shown in FIG. 11 with a simple modification such as to the dual outlet pump arrangement in FIG. 9. In FIG. 11, parts similar to those in FIG. 9 are designated by the same numerals but with the suffix letter E added and added matter designated by new numerals. As shown in FIG. 11, the rotor member 76E with its timing port 120E remain unchanged from that in FIG. 9 and the previously provided two

outlet nipples

122E and 202E with their respective outlet passages 124E and 203E are now located on the same side of the pump for ease of usage in a particular application instead of being diametrically opposite each other. With fluid supply from the outlet port continuously available to the timing port 120E additional outlets are possible by simply adding other nipples such as nipple 208 with a passage 209 to the pump body bore E at the same axial location as the other outlet passages and angularly spaced therefrom more than the width of the timing port E. Then as the rotor member 76E rotates the timing port 120E delivers a shot of oil to all such outlet passages to which it periodically opens during each turn.

In the pump structure with two or more outlets thus far disclosed the quantity of oil delivered to these outlets is the same. However, there are applications where it is desirable to have different flows from the different outlets and this may be accomplished by simple modification of the FIG. 9 embodiment as shown in FIG. 12 wherein parts similar to those shown in FIG. 9 are designated by the same numerals but with the suffix letter F added and added matter is designated by new numerals. In FIG. 12, it is shown that the timing port 120F instead of having a constant cross-section along its length as in the previous embodiments is provided with a small constant width 210 in the area where it is openable to the outlet passage 124F and is provided with a large constant width 212 in the area where it is openable to the other outlet passage 203F. Thus, during rotation of the rotor member 76F, the timing port 120F will be open to the two outlet passages 124F and 203E for different periods of time during the same revolution of the rotor member, i.e., the timing port 120F remaining open to the outlet passage 203F for a time longer than it is open to the other outlet passage 124F whereby the outlet passage 203F receives more oil than the other outlet passage 124F in proportion to the port width or time ratio thus provided. Knowing the particular application, the differences in width are determined to provide the desired different flows.

The timing port may have other configurations that also provide a desired uneven division of oil to different outlets as shown in FIGS. 13 and 14 wherein parts similar to those shown in FIG. 12 are designated by the same numerals but with the suffix letters G and H added in the respective views. In the FIG. 13 modification, the timing port 120G is broadest where it is open to the annular groove 2046 and then tapers as it extends axially from the region of the closest outlet passage to that of the other. Thus, the timing port 120G is open longer and thus delivers more oil to the outlet passage closest to the annular groove 2046 than to the remote outlet passage. In the FIG. 14 modification, the timing port l20I-I tapers in the opposite direction so that for the same installation it is open longer and thus delivers more oil to the outlet passage farthest from groove 204H.

Rather than have the timing port in the rotor member cooperate with the pump body bore to produce valving action for intermittent oil delivery, it is also possible to effect such valving operation for single and multiple outlet delivery by using the end of the rotor member operating against the closed end of this bore as shown in FIGS. 15 and 16 wherein parts similar to previously described structure are designated by the same numerals but with the suffix letters I and J and added matter is designated by new numbers. Referring first to FIG. 15, the lower end of the rotor member 76l instead of being pointed is provided with a flat surface 216 which bears against the closed flat end of the pump body bore 75I. The longitudinal drilled passage 1171 that is open at its upper end to the outlet port is extended downward to intersect with the chamber 121] which is annular and extends about the lower end of rotor member 76I. The outlet nipple 122I is formed on the lower end of the pump body with its passage 124] located opposite the flat end 216 of the rotor member 76l. The timing port 120I is located to extend through the lower edge of the rotor member 76] so that as the rotor member rotates, the timing port 120I periodically connects chamber 121] to the outlet passage l24l and throughout the remainder of a rotor member revolution the flat lower end 216 of the rotor member closes this outlet passage. In the FIG. 16 modification, it is shown that with the valving in FIG. 15 it is possible to provide multiple outlets by simply adding other nipples such as nipple 202] with its passage 203] at the same radial location but angularly spaced from the other outlet passage 124] so that as the rotor rotates the timing port 120J connects the chamber 121.] to the outlet 124.] and then to the other outlet passage 203.1 during each revolution.

In the pump structures thus far described, the pressure control member and connected lever are located close to the engine housing. It is also possible to locate the pressure control member and connected lever at the other end of pump housing remote from the engine housing as shown in FIG. 17 wherein parts similar to those previously disclosed are designated by the same numerals but with the suffix letter K added and added matter is identified by new numerals. In FIG. 17, pump body 72K rather than the pressure control member 82K has a piloting cylindrical land 218 for locating the pump housing on the engine housing. The rotor member 76K is rotatably mounted in the bore K which now extends completely through the pump body and the pressure control member 82K is mounted in the counterbore 85K which is now located in the lower end of the pump body with its cylindrical inner surface 84K eccentric to the cylindrical outer surface 77K of the rotor member 76K. The pressure control member 82K is retained in the pump body by a cover 220 which is secured to the lower end of the pump body 72K by screws 221 and the control lever 87K is secured to the closed outer end of the pressure control member 82K by a bolt 222. Oil from the engine flows through a longitudinal hole 223 in the pump body to the sump region of the pump chamber 98K and with the rotor member 76K rotating it picks up oil from this area and carries it to the close clearance area creating pressure as previously described. Oil under pressure is taken from this region via the outlet port 106K in the pressure control member 82K. The outlet port 106K connects to the annular groove K which is now formed in the upper flat face of the pressure control member 82K and maintains connection of the outlet port 106K with a passage 224 in the pump body as the pressure control member 82K is turned to effect change in flow. The passage 224 intersects with the pump body bore 75K in a region where timing port K will periodically open thereto as the rotor member 76K rotates. The timing port 120K is open at its upper end to an annular groove 225 in the surface of the rotor member 76K which groove is located opposite the outlet passage 124K. Outlet passage 124K thus remains continuously open to the groove 225 but is only open intermittently to the passage 224 and thus outlet port 106K by operation of timing port 120K.

While the pump structure described above uses gravity supply, it will be understood that pressurized oil supply can also be used to maintain the pump chamber filled with oil for efficient operation. It is also apparent that the above described pump structure provides intermittent flow to the one or more outlets but a continuous flow thereto from the outlet port where such operation is desired is possible by simply providing an open passage thereto instead of through the valving provided by the timing port. Furthermore, while the pump is capable of providing variable flow with variable and constant speed, it is also capable of providing variable flow with variable speed alone or with constant speed alone.

It is also apparent that the pump according to the present invention is of very simple construction and thus of low cost yet is durable with a projected long life since there are no highly loaded wear areas. Furthermore, the pump can be made economically with either single or multiple outlets and can be simply tailored to provide different flows for different applications.

The above described embodiments are illustrative of the invention which may be modified within the scope of the appended claims.

I claim:

1. A fluid metering pump comprising a pump body, a rotor member having a cylindrical surface with a rotor axis mounted in said pump body for rotation about said rotor axis, a pressure control member having a cylindrical surface with a control axis mounted in said pump body for turning about said control axis, said control axis spaced from and parallel to said rotor axis, said cylindrical surfaces arranged opposite each other and cooperating with each other and with said pump body to define an annular chamber between said rotor member and said pressure control member with a radial dimension that varies thereabout, an inlet passage in said pump body for supplying fluid to said chamber whereby on rotation of said rotor member relative to said pressure control member there is developed fluid pressure in said chamber that increases with increasing rotor member speed and also increases about said cylindrical surface of said pressure control member with decreasing radial size of said chamber, and an outlet port through said cylindrical surface of said pressure control member for receiving fluid from said chamber so that on turning of said pressure control member about said control axis the pressure of the fluid at said outlet port increases as said outlet port is moved with said pressure control member in the direction of decreasing radial size of said chamber whereby fluid flow through said outlet port increases with increasing rotor member speed and also increases as said outlet port is turned in the direction of decreasing radial size of said chamber.

2. A fluid metering pump comprising a pump body, a rotor member having a cylindrical surface with a rotor axis mounted in said pump body for rotation about said rotor axis, a pressure control member having an external cylindrical surface with a control axis mounted in said pump body for turning about said control axis, said control axis spaced from and parallel to said rotor axis, said pressure control member having an internal cylindrical surface arranged opposite said cylindrical surface of said rotor member and cooperating therewith and with said pump body to define an annular chamber between said rotor member and said pressure control member, said internal cylindrical surface having a center line spaced from and parallel to said rotor axis and said control axis so that said chamber has a radial dimension that varies thereabout, an inlet passage in said pump body for supplying fluid to said chamber whereby on rotation of said rotor member relative to said pressure control member there is developed fluid pressure in said chamber that increases with increasing rotor member speed and also increases about said cylindrical surface of said pressure control member with decreasing radial size of said chamber, and an outlet port through said internal cylindrical surface of said pressure control member for receiving fluid from said chamber so that on turning of said pressure control member about said control axis the pressure of the fluid at said outlet port increases as said outlet port is moved with said pressure control member in the direction of decreasing radial size of said chamber whereby fluid flow through said outlet port increases with increasing rotor member speed and also increases as said outlet port is turned in the direction of decreasing radial size of said chamber.

3. A fluid metering pump comprising a pump body having a bore, a rotor member having a cylindrical surface with a rotor axis mounted in said bore in said pump body for rotation about said rotor axis, a pressure control member having a cylindrical surface with a control axis mounted in said pump body for turning about said control axis, said control axis spaced from and parallel to said rotor axis, said cylindrical surfaces arranged opposite each other and cooperating with each other and with said pump body to define an annular chamber between said rotor member and said pressure control member with a radial dimension that varies thereabout, an inlet passage in said pump body for supplying fluid to said chamber whereby on rotation of said rotor member relative to said pressure control member there is developed fluid pressure in said chamber that increases with increasing rotor member speed and also increases about said cylindrical surface of said pressure control member with decreasing radial size of said chamber, an outlet port through said cylindrical surface of said pressure control member for receiving fluid from said chamber so that on turning of said pressure control member about said control axis the pressure of the fluid at said outlet port increases as said outlet port is moved with said pressure control member in the direction of decreasing radial size of said chamber whereby fluid flow through said outlet port increases with increasing rotor member speed and also increases as said outlet port is turned in the direction of decreasing radial size of said chamber, passage means in said pump body connected to said outlet port and open to said bore, an outlet passage in said pump body open to said bore, and passage means including a timing port in said cylindrical surface of said rotor member for periodically connecting said passage means and said outlet passage during each revolution of said rotor member.

4. A fluid metering pump comprising a pump body having a bore, a rotor member having a cylindrical surface with a rotor axis mounted in said bore in said pump body for rotation about said rotor axis, a pressure control member having a cylindrical surface with a control axis mounted in said pump body for turing about said control axis, said control axis spaced from and parallel to said rotor axis, said cylindrical surfaces arranged opposite each other and cooperating with each other and with said pump body to define an annular chamber between said rotor member and said pressure control member with a radial dimension that varies thereabout, an inlet passage in said pump body for supplying fluid to said chamber whereby on rotation of said rotor member relative to said pressure control member there is developed fluid pressure in said chamber that increases with increasing rotor member speed and also increases about said cylindrical surface of said pressure control member with decreasing radial size of said chamber, an outlet port through said cylindrical surface of said pressure control member for receiving fluid from said chamber so that on turning of said pressure control member about said control axis the pressure of the fluid at said outlet port increases as said outlet port is moved with said pressure control member in the direction of decreasing radial size of said chamber whereby fluid flow through said outlet port increases with increasing rotor member speed and also increases as said outlet port is turned in the direction of decreasing radial size of said chamber, a plurality of passage means in said pump body connected to said outlet port and open to said bore at different angular locations, an outlet passage in said pump body open to said bore corresponding to and at the same angular location of each of said passage means, and a timing port in said cylindrical surface of said rotor member for periodically connecting said corresponding passage means and outlet passage during each revolution of said rotor member.

5. A fluid metering pump comprising a pump body having a bore, a rotor member having a cylindrical surface with a rotor axis mounted in said bore in said pump body for rotation about said rotor axis, a pressure control member having a cylindrical surface with a control axis mounted in said pump body for turning about said control axis, said control axis spaced from and parallel to said rotor axis, said cylindrical surfaces arranged opposite each other and cooperating with each other and with said pump body to define an annular chamber between said rotor member and said pressure control member with a radial dimension that varies thereabout, an inlet passage in said pump body for supplying fluid to said chamber whereby on rotation of said rotor member relative to said pressure control member there is developed fluid pressure in said chamber that increases with increasing rotor member speed and also increases about said cylindrical surface of said pressure control member with decreasing radial size of said chamber, an outlet port through said cylindrical surface of said pressure control member for receiving fluid from said chamber so that on turning of said pressure control member about said control axis the pressure of the fluid at said outlet port increases as said outlet port is moved with said pressure control member in the direction of decreasing radial size of said chamber whereby fluid flow through said outlet port increases with increasing rotor member speed and also increases as said outlet port is turned in the direction of decreasing radial size of said chamber, single passage means in said pump body connected to said outlet port and open to said bore, a plurality of outlet passages in said pump body open to said bore at different angular locations, and passage means including a timing port in said cylindrical surface of said rotor member for periodically connecting said outlet passages to said pump body passage means during each revolution of said rotor member.

6. A fluid metering pump comprising a pump body having a bore closed at one end, a rotor member having a cylindrical surface with a rotor axis mounted in said bore in said pump body for rotation about said rotor axis, a pressure control member having a cylindrical surface with a control axis mounted in said pump body for turning about said control axis, said control axis spaced from and parallel to said rotor axis, said cylindrical surfaces arranged opposite each other and cooperating with each other and with said pump body to define an annular chamber between said rotor member and said pressure control member with a radial dimension that varies thereabout, an inlet passage in said pump body for supplying fluid to said chamber whereby on rotation of said rotor member relative to said pressure control member there is developed fluid pressure in said chamber that increases with increasing rotor member speed and also increases about said cylindrical surface of said pressure control member with decreasing radial size of said chamber, an outlet port through said cylindrical surface of said pressure control member for receiving fluid from said chamber so that on turning of said pressure control member about said control axis the pressure of the fluid at said outlet port increases as said outlet port is moved with said pressure control member in the direction of decreasing radial size of said chamber whereby fluid flow through said outlet port increases with increasing rotor member speed and also increases as said outlet port is turned in the direction of decreasing radial size of said chamber, passage means in said pump body connected to said outlet port and open to said bore, an outlet passage in said pump body open to said closed bore end, and a timing port in said rotor member for cooperating with said closed bore end to periodically open said outlet passage to connect via said bore with said passage means during each revolution of said rotor member.

7. A fluid metering pump comprising a pump body, a rotor member having a cylindrical surface with a rotor axis mounted in said pump body for rotation about said rotor axis, a pressure control member having a cylindrical surface with a control axis mounted in said pump body for turning about said control axis, said control axis spaced from and parallel to said rotor axis, said cylindrical surfaces arranged opposite each other and cooperating with each other and with said pump body to define an annular chamber between said rotor member and said pressure control member with a radial dimension that varies thereabout, an inlet passage in said pump body for supplying fluid to said chamber whereby on rotation of said rotor member relative to said pressure control member there is developed fluid pressure in said chamber that increases with increasing rotor member speed and also increases about said cylindrical surface of said pressure control member with decreasing radial size of said chamber, an outlet port through said cylindrical surface of said pressure control member for receiving fluid from said chamber so that on turning of said pressure control member about said control axis the pressure of the fluid at said outlet port increases as said outlet port is moved with said pressure control member in the direction of decreasing radial size of said chamber whereby fluid flow through said outlet port increases with increasing rotor member speed and also increases as said outlet port is turned in the direction of decreasing radial size of said chamber, passage means in said pump body connected to said outlet port and open to said bore, a plurality of outlet passages in said pump body open to said bore at different angular and axial locations, and passage means including an axially extending timing port of varying width in said cylindrical surface of said rotor member for periodically connecting said outlet passages to said pump body passage means for different time intervals during each revolution of said rotor member so that said outlet passages receive different amounts of fluid.

8. A fluid metering pump comprising a pump body, a rotor member having a cylindrical surface with a rotor axis mounted in said pump body for rotation about said rotor axis, a pressure control member having a cylindrical surface with a control axis mounted in said pump body for turning about said control axis, said control axis spaced from and parallel to said rotor axis, said cylindrical surfaces arranged opposite each other and cooperating with each other and with said pump body to define an annular chamber between said rotor member and said pressure control member with a radial dimension that varies thereabout, an inlet passage in said pump body for supplying fluid to said chamber whereby on rotation of said rotor member relative to said pressure control member there is developed fluid pressure in said chamber that increases with increasing rotor member speed and also increases about said cylindrical surface of said pressure control member with decreasing radial size of said chamber, an outlet port through said cylindrical surface of said pressure control member for receiving fluid from said chamber so that on turning of said pressure control member about said control axis the pressure of the fluid at said outlet port increases as said outlet port is moved with said pressure control member in the direction of decreasing radial size of said chamber whereby fluid flow through said outlet port increases with increasing rotor member speed and also increases as said outlet port is turned in the direction of decreasing radial size of said chamber, passage means in said pump body connected to said outlet port and open to said bore, an outlet passage in said pump body open to said bore, and passage means in said cylindrical surface of said rotor member including an annular groove open to said outlet passage and means for periodically connecting said pump body passage means via said timing port and then said groove to said outlet passage during each revolution of said rotor member.

9. An oil metering pump for metering oil to lubricate a rotary engine having gas seals, an output shaft and a throttle comprising a pump body, a rotor member having a cylindrical surface with a rotor axis mounted in said pump body for rotation about said rotor axis, means drivingly connecting said output shaft to rotate said rotor member, a pressure control member having a cylindrical surface with a control axis mounted in said pump body for turning about said control axis, said control axis spaced from and parallel to said rotor axis, said cylindrical surfaces arranged opposite each other and cooperating with each other and with said pump body to define an annular chamber between said rotor member and said pressure control member with a radial dimension that varies thereabout, an inlet passage in said pump body for supplying oil to said chamber whereby on rotation of said rotor member relative to said pressure control member there is developed oil pressure in said chamber that increases with increasing rotor member speed and also increases about said cylindrical surface of said pressure control member with decreasing radial size of said chamber, an outlet port in said pressure control member for receiving oil from said chamber, outlet passage means in said pump body for delivering oil from said outlet port to lubricate said gas seals, said outlet port extending through said cylindrical surface of said pressure control member so that on turning of said pressure control member about said control axis the pressure of the oil at said outlet port increases as said outlet port is moved with said pressure control member in the direction of decreasing radial size of said chamber, and means operatively connecting said throttle to turn said pressure control member to move said outlet port in the direction of decreasing radial size of said chamber with increasing throttle opening so that oil flow through said outlet port for gas seal lubrication increases with increasing engine speed and also increases with increasing throttle opening.

10. An oil metering pump for metering oil to lubricate a rotary engine having gas seals, an output shaft and a throttle comprising a pump body, a rotor member having an external cylindrical surface with a rotor axis mounted in said pump body for rotation about said rotor axis, means drivingly connecting said output shaft to rotate said rotor member, a pressure control member having an internal cylindrical surface with a control axis mounted in said pump body for turning about said control axis, said control axis spaced from and parallel to said rotor axis, said cylindrical surfaces arranged opposite each other and cooperating with each other and with said pump body to define an annular chamber between said rotor member and said pressure control member with a radial dimension that varies thereabout, an inlet passage in said pump body for supplying oil to said chamber whereby on rotation of said rotor member relative to said pressure control member there is developed oil pressure in said chamber that increases with increasing rotor member speed and also increases about said internal cylindrical surface of said pressure control member with decreasing radial size of said chamber, an outlet port in said pressure control member for receiving oil from said chamber, outlet passage means in said pump body for delivering oil from said outlet port to lubricate said gas seals, said outlet port extending through said internal cylindrical surface of said pressure control member so that on turning of said pressure control member about said control axis the pressure of the oil at said outlet port increases as said outlet port is moved with said pressure control member in the direction of decreasing radial size of said chamber, and means operatively connecting said throttle to turn said pressure control member to move said outlet port in the direction of decreasing radial size of said chamber with increasing throttle opening so that oil flow through said outlet port for gas seal lubrication increases with increasing engine speed and also increases with increasing throttle opening.

11. An oil metering pump for metering oil to lubricate a rotary engine having gas seals, an output shaft and a throttle comprising a pump body, a rotor member having a cylindrical surface with a rotor axis mounted in said pump body for rotation about said rotor axis, means drivingly connecting said output shaft to rotate said rotor member, a pressure control member having an external cylindrical surface with a control axis mounted in said pump body for turning about said control axis, said control axis spaced from and parallel to said rotor axis, said pressure control member also having an internal cylindrical surface opposite said cylindrical surface of said rotor member and cooperating therewith and with said pump body to define an annular chamber between said rotor member and said pres sure control member, said internal cylindrical surface having a center line spaced from and parallel to said rotor axis and said control axis so that said chamber has a radial dimension that varies thereabout, an inlet passage in said pump body for supplying oil to said chamber whereby on rotation of said rotor member relative to said pressure control member there is developed oil pressure in said chamber that increases with increasing rotor member speed and also increases about said internal cylindrical surface of said pressure control member with decreasing radial size of said chamber, an outlet port in said pressure control member for receiving oil from said chamber, outlet passage means in said pump body for delivering oil from said outlet port to lubricate said gas seals, said outlet port extending through said cylindrical surface of said pressure control member so that on turning of said pressure control member about said control axis the pressure of the oil at said outlet port increases as said outlet port is moved with said pressure control member in the direction of decreasing radial size of said chamber, and means operatively connecting said throttle to turn said pressure control member to move said outlet port in the direction of decreasing radial size of said chamber with increasing throttle opening so that oil flow through said outlet port for gas seal lubrication increases with increasing engine speed and also increases with increasing throttle opening.

12. An oil metering pump for metering oil to lubricate a rotary engine having gas seals, an output shaft and a throttle comprising a pump body having a bore, a rotor member having a cylindrical surface with a rotor axis mounted in said bore in said pump body for rotation about said rotor axis, means drivingly connecting said output shaft to rotate said rotor member, a pressure control member having a cylindrical surface with a control axis mounted in said pump body for turning about said control axis, said control axis spaced from and parallel to said rotor axis, said cylindrical surfaces arranged opposite each other and cooperating with each other and with said pump body to define an annular chamber between said rotor member and said pressure control member with a radial dimension that varies thereabout, an inlet passage in said pump body for supplying oil to said chamber whereby on rotation of said rotor member relative to said pressure control member there is developed oil pressure in said chamber that increases with increasing rotor member speed and also increases about said cylindrical surface of said pressure control member with decreasing radial size of said chamber, an outlet port in said pressure control member for receiving oil from said chamber, passage means in said pump body connected to said outlet port and open to said bore, a plurality of outlet passages in said pump body open to said bore at different angular locations for delivering oil to lubricate said gas seals, passage means including a timing port in said cylindrical surface of said rotor member for periodically separately connecting said pump body passage means to said outlet passages during each revolution of said rotor member, said outlet port extending through said cylindrical surface of said pressure control member so that on turning of said pressure control member about said control axis the pressure of the oil at said outlet port increases at said outlet port is moved with said pressure control member in the direction of decreasing radial size of said chamber, and means operatively connecting said throttle to turn said pressure control member to move said outlet port in the direction of decreasing radial size of said chamber with increasing throttle opening so that oil flow through said outlet port for gas seal lubrication increases with increasing engine speed and also increases with increasing throttle opening.

' 533 5 3 UNITED STATES ?ATENT OFFICE CERTIFICATE OF CORRECTION Pacent'No- 3.827.836 at August 6, 1974 mo-W It is certified that error appeafs in the. above identified patent and that said Letters Patent are hereby corrected. as shown below:

' Column 3, line 54," "Th"' should read ---.The

Column 6, line 24; "trapped? should read tapped Column 9, line 31., "and" should read to column 14, line 36, "turing" should read turning Column .20, line 17. "at" should read as Signed and sealedgthie .19th'day of- November 1974.

(SEAL) Attest:

McCOY GIBSON R. e c. MARSHALL DANN. Attesting Officer 1 Comissioner of Patents

Claims

7. A fluid metering pump comprising a pump body, a rotor member having a cylindrical surface with a rotor axis mounted in said pump body for rotation about said rotor axis, a pressure control member having a cylindrical surface with a control axis mounted in said pump body for turning about said control axis, said control axis spaced from and parallel to said rotor axis, said cylindrical surfaces arranged opposite each other and cooperating with each other and with said pump body to define an annular chamber between said rotor member and said pressure control member with a radial dimension that varies thereabout, an inlet passage in said pump body for supplying fluid to said chamber whereby on rotation of said rotor member relative to said pressure control member there is developed fluid pressure in said chamber that increases with increasing rotor member speed and also increases about said cylindrical surface of said pressure control member with decreasing radial size of said chamber, an outlet port through said cylindrical surface of said pressure control member for receiving fluid from said chamber so that on turning of said pressure control member about said control axis the pressure of the fluid at said outlet port increases as said outlet port is moved with said pressure control member in the direction of decreasing radial size of said chamber whereby fluid flow through said outlet port increases with increasing rotor member speed and also increases Pg,45 as said outlet port is turned in the direction of decreasing radial size of said chamber, passage means in said pump body connected to said outlet port and open to said bore, a plurality of outlet passages in said pump body open to said bore at different angular and axial locations, and passage means including an axially extending timing port of varying width in said cylindrical surface of said rotor member for periodically connecting said outlet passages to said pump body passage means for different time intervals during each revolution of said rotor member so that said outlet passages receive different amounts of fluid.

11. An oil metering pump for metering oil to lubricate a rotary engine having gas seals, an output shaft and a throttle comprising a pump body, a rotor member having a cylindrical surface with a rotor axis mounted in said pump body for rotation about said rotor axis, means drivingly connecting said output shaft to rotate said rotor member, a pressure control member having an external cylindrical surface with a control axis mounted in said pump body for turning about said control axis, said control axis spaced from and parallel to said rotor axis, said pressure control member also having an internal cylindrical surface opposite said cylindrical surface of said rotor member and cooperating therewith and with said pump body to define an annular chamber between said rotor member and said pressure control member, said internal cylindrical surface having a center line spaced from and parallel to said rotor axis and said control axis so that said chamber has a radial dimension that varies thereabout, an inlet passage in said pump body for supplying oil to said chamber whereby on rotation of said rotor member relative to said pressure control member there is developed oil pressure in said chamber that increases with increasing rotor member speed and also increases About said internal cylindrical surface of said pressure control member with decreasing radial size of said chamber, an outlet port in said pressure control member for receiving oil from said chamber, outlet passage means in said pump body for delivering oil from said outlet port to lubricate said gas seals, said outlet port extending through said cylindrical surface of said pressure control member so that on turning of said pressure control member about said control axis the pressure of the oil at said outlet port increases as said outlet port is moved with said pressure control member in the direction of decreasing radial size of said chamber, and means operatively connecting said throttle to turn said pressure control member to move said outlet port in the direction of decreasing radial size of said chamber with increasing throttle opening so that oil flow through said outlet port for gas seal lubrication increases with increasing engine speed and also increases with increasing throttle opening.