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Publication numberUS2743674 A
Publication typeGrant
Publication dateMay 1, 1956
Filing dateAug 26, 1952
Priority dateAug 26, 1952
Publication numberUS 2743674 A, US 2743674A, US-A-2743674, US2743674 A, US2743674A
InventorsEdwin L Shaw
Original AssigneeDenison Eng Co
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Supercharged aircraft pump
US 2743674 A
Abstract  available in
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Claims  available in
Description  (OCR text may contain errors)

W L 1956 E. SHAW SUPERCHARGED AIRCRAFT PUMP Filed Aug. 26,- 1952 IN VEN TOR.

SUPERCHARGED AIRCRAFT PUMP Edwin L. Shaw, Columbus, Ohio, assignor to The Denison Engineering Company, Columbus, Uhio, a corporation of Ohio Application August 26, 1952, Serial No. 336,399 2 Claims. (Cl. 103--162) This invention relates to hydraulic apparatus and is more particularly directed to fluid pressure energy translating devices of the type used in aircraft.

Still more particularly the invention is directed to a fluid pump of the character illustrated in the copending application of Cecil E. Adams et 211., Serial No. 234,634, filed June 30, 1951, now Patent No. 2,737,899, dated March 13, 1956, this pump having a booster or supercharger section which operates simultaneously with the main pumping section.

An object of this invention is to improve the efficiency and operating characteristics of thepump shown in such application.

Another object of this invention is to provide a supercharged aircraft pump having means incorporated therein to minimize the required size of lines supplying fluid to and conducting fiuid from the pump.

it is also an object of the invention to provide a supercharged pump in which the supercharger operates simultaneously with the main section of the pump and means are provided to dissipate the excess fluid under pressure supplied by the supercharging apparatus.

Another object is to provide a pump of the character mentioned in which a relief valve controlled passage extends from the outlet or" the supercharger to the inlet of the pump, this passage providing for the dissipation of excess supercharging pressure yet permitting the employment of a supply line of minimum size.

A further object of the invention is to provide a pump having fluid inlet and outlet ports, a supercharger pumping section which communicates with the inlet port and discharges fluid into an intermediate pressure manifold, the pump having a main pumping section which transfers fluid from the intermediate pressure manifold to the outlet port, the pump being further provided with a relief valve between the intermediate pressure manifold and the inlet port whereby excessive pressure in the intermediate manifold will bedischarged to the. inletport to be recirculated through the pumping device.

Further objects and advantages of the present invention will be apparent from the following description, reference being had to the accompanying drawings wherein a preferred form of embodiment of the invention is clearly shown.

In the drawings:

Fig. l is a longitudinal sectional View taken through a fluid pressure translating device formed. in accordance with the present invention.

Fig. 2 is an enlarged detail sectional view taken through the passage which establishes communication between an intermediate pressure manifold and the inlet port; this section also being taken through a relief valve provided in such passage.

Referring more particularly to the drawings, the numeral 29 designates the pump in its entirety. This pump includes a casing 21 which may be formed of a plurality of parts including an end cover 22 in which inlet and exhaust ports 23 and 24, respectively, are formed. The

nite States Patent casing provides a chamber 25 for the pumping mechanism. At the end of the casing opposite the cover 22, there is provided a bearing mechanism 26 for rotatably supporting a drive shaft section 27. This section includes a plurality of pieces which are splined together to provide flexibility in the drive shaft, the outer end of this section being formed for connection with a prime mover, not shown. The drive shaft extends through a packing 28 which prevents the escape of fluid from the interior of the pump casing. The inner end of the drive shaft has a splined connection as at 30 with a cylinder barrel 31, this member being formed also from a plurality of pieces and including piston chambers with sections 32 and 33 of different sizes.

The cylinder barrel is disposed in engagement at one end with a port plate 34, this member being pinned or otherwise secured to the cover 22 and having ports 35 and 36 formed therein, the former being designated as an intermediate pressure port and the latter the exhaust port, this port communicating with port 24 in the cover 22. The cover 22 has a pintle member 37 secured to the central portion thereof, this member 3'7 being hollow and communicating directly with the inlet port 23. The menu her 37 projects through the center of the port plate 34 and into a central opening formed in the cylinder barrel 3i.- Adjacent the inner end of the member 37, there is provided a laterally directed port 38, this port being disposed for registration with ports 4% formed in the cylinder barrel and communicating with the larger sections 33 of the piston chambers. The ports also communicate with groove means ll formed on the exterior of the pintle' member 37, the grooves cooperating with the cylinder barrel to provide an intermediate pressure manifold which communicates with the port- 35 formed in the port plate 34. The small sections of the piston chambers 32 co1nmunicate by way of ports 42 with the exhaust port 36 formed in the cylinder barrel, these ports also cornmuni= eating with the intermediate pressure port 35 as the cylinder barrel revolves. It will be obvious that the communication between the ports in the cylinder barrel and the ports in the pintle and port plate 34- is intermittent due to the rotation of the cylinder barrel relative to the other members. The cylinder barrel is supported for rotation at the end opposite that engaging the port plate by radial bearings 43, these bearings being disposed between the cylinder barrel and a bearing race carried by the casing 21.

The piston chambers receive for recipr-ocatory movement therein piston elements having sections 44 and 45 corresponding in size to and received by the sections 32 and 33, respectively, of the piston chambers. These piston members are each provided with a spherical head to which is secured bearing shoe 47 and which is formed for engagement with the flat surface of a cam plate 4%, the bearing shoes being held in engagement with the cam surface by a retainer plate 50. This plate is suitably secured to a pivoted hanger 51 through the adjustment of which the angle of the cam may be varied. The hanger 51 is supported by hearing elements 5.2 which are, in turn, suitably supported by studs 53 threaded into the casing 21.-

Valve plate iid and cover 22 are provided with passage means 54 which establishes communication between the intermediate pressure port 35, and the manifold connected therewith, and the inlet port 23. This passage is formed by a plurality of drilled openings which communicate with a chamber 55 formed in the cover 223. This chamber receives a valve seat insert 576, the latter having a central opening communicating with the portion of the passage 54 extending from the intermediate pressure port. The outer end of the chamber 55 is closed by a plug 57 having a socket 558 formed therein for the reception of a stem 60 provided on a relief valve element 61. The socket 58 cooperates with the opening in the valve seat insert to guide the valve 61 in its movement toward and away from the valve seat. As shown in Fig. 2, the end of the valve disposed in the opening in the insert is pro vided with an internal opening and transversely extending ports 62 which, when the valve is moved toward the plug 57, will be exposed to establish communication between the intermediate pressure port and the inlet port 23. The valve is normally urged toward a closed position by a coil spring 63 disposed between a flange 64 formed on the valve stem and the inner end of the valve plug 57. The tension of the spring will determine the pressure at which the valve will open to establish fluid flow from the intermediate pressure port to the inlet port.

In the operation of the pump, the driving shaft 27 is revolved by the prime mover and, in turn, transmits such motion to the cylinder barrel. Due to'the inclination of the cam 48, the pistons will-be reciprocated in the piston chambers, the cam being so inclined that, as the larger sections of the piston chambers communicate with the port 38, the pistons will move in an outward direction. Then, when the larger sections of the piston chambers communicate with the port 40, the pistons will be moved into the piston chambers. This action of the pistons will suck fluid into the piston chambers from the port 38 and expel this fluid through port 40 to the intermediate pressure manifold. Also as the cylinder barrel revolves, the

smaller sections of the piston chambers will communicate with the intermediate pressure port while the pistons are being moved outwardly of the piston chambers and with the exhaust port 36 when the pistons are being returned into the piston chambers. pistons will transfer fluid from the intermediate pressure port to the exhaust port 36.

Since .the volumetric capacity of the larger piston chambers is greater than the capacity of the smaller piston chambers, the latter will not be capable of utilizing all of the fluid delivered by the larger piston sections. The fluid pressure will, therefore, increase in the intermediate pressure zone and fluid under pressure will be supplied to the smaller piston chambers. Since an excess volume of fluid is supplied by the supercharging section of the pump, some means must be provided to dissipate this excess fluid and prevent the generation of excessive pressures in the intermediate pressure zone. For this purpose, the passage 54 and relief valve 61 have been provided. When the pressure in the intermediate pressure port increases sufficiently, the relief valve will be caused to move to an open position and some of the fluid may then flow from intermediate pressure port through the passage 54 to the inlet port 23. In the pump illustrated, the supercharging pump section has a capacityto deliver a volume of fluid substantially 25 in excess of the capacity of the main pumping section. With the bypass passage shown in the drawings and described, this,

25% excess capacity of the supercharger is recirculated.

. By this recirculation, the supply line extending to the inlet port 23 may be made smaller. If this excess fluid were discharged into a drain line, the inlet or supply line would necessarily be required to have 25% more capacity. It should be obvious that, by providing a by-pass passage between the intermediate pressure port and the inlet port, and controlling fluid flow therethrough by a relief valve, the operatingcharacteristics of the device are improved.

This action of thefor rotation in said'casing, said cylinder'barrel having piston chambers with'sections of diflerent sizes; valving means disposed between the portion of said casing containing said inlet and outlet ports and said cylinder barrel,

said valving means having a cavity formed therein which cooperates with said cylinder barrel to form an intermediate pressure manifold, 21 high pressure port in said valving means communicating with said outlet port, means connecting the larger sections of said piston chambers alternately with said inlet port and said intermediate pressure manifold and the smaller sections of said piston chambers alternately with said intermediate pressure manifold and said high pressure port upon rotation of said cylinder barrel; piston elements with sections corresponding in sizes to the sections of said piston chambers disposed for reciprocation therein; cam means for controlling the reciprocation of said pistons; a passage extending from said intermediate pressure manifold to said inlet port; and a relief valve in said passage.

2. In a-fluid pressure energy translating device, a casing having inlet and outlet ports; a cylinder barrel disposed for rotation in said casing, said cylinder barrel having piston chambers with sections of different sizes; valving means disposed'between the portion of said casing consure manifold and said high pressure port upon rotation of said cylinder barrel; piston elements with sections corresponding in sizes to the sections of said piston chambers disposed for reciprocation therein; cam means for controlling the reciprocation of said pistons; a passage extending from said intermediate pressure manifold to said inlet port; a valve supported in said passage for movement toward open position in response to pressure in said intermediate pressure zone; and spring means between said valve and a portion of said casing, said spring means tending to resist opening movement of said valve.

References Cited in the file of this'patcnt UNITED STATES PATENTS 2,270,263 Butler Ian. 20, 1942 2,494,606 Anderson Jan. 17, 1950 2,522,890 Peterson Sept. 19, 1950 2,604,047 Beaman et al. July 22, 1952 2,608,933 Ferris Sept. 2, 1952 FOREIGN PATENTS Australia 1946

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US2270263 *Jun 19, 1940Jan 20, 1942Butler Frank DavidFuel measuring and distributing pump for oil engines
US2494606 *Sep 21, 1944Jan 17, 1950United Aircraft CorpHydraulic pump for propeller pitch changing mechanisms
US2522890 *Aug 22, 1945Sep 19, 1950Peterson Adolphe CFuel metering, distribution, and control means
US2604047 *Sep 19, 1945Jul 22, 1952HulmanTwo-stage hydraulic pressure pump
US2608933 *Sep 24, 1945Sep 2, 1952Oilgear CoHydrodynamic machine
AU121688B * Title not available
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3169488 *Nov 3, 1961Feb 16, 1965New York Air Brake CoRotary cylinder barrel and method of making same
US3241495 *Aug 12, 1963Mar 22, 1966American Brake Shoe CoConstruction for axial piston pump or motor
US4025238 *Apr 17, 1975May 24, 1977Messier HispanoApparatus for eliminating the effects of cavitation in a main pump
US4722672 *Nov 5, 1985Feb 2, 1988Rinneer Arthur EHydraulic energy-conversion device
Classifications
U.S. Classification417/252, 417/268, 417/311
International ClassificationF04B1/20, F04B49/24, F02M41/08
Cooperative ClassificationF04B1/2064, F02M41/08, F02M2700/1329, F04B49/24
European ClassificationF02M41/08, F04B49/24, F04B1/20C5