US2773452A

US2773452A - Pump control system

Info

Publication number: US2773452A
Application number: US320797A
Authority: US
Inventors: Kenneth L Berninger; William A Weis
Original assignee: Motors Liquidation Co
Current assignee: Motors Liquidation Co
Priority date: 1952-11-15
Filing date: 1952-11-15
Publication date: 1956-12-11
Anticipated expiration: 1973-12-11

Description

Dec. 1l, 1956 K BERNlNGr-:R ET Al. 2,773,452

PUMP CONTROL SYSTEM Filed NOV. 15, 1].952 5 SlfnetS-Sheeil 1 Mill '""w IN V EN TORS Dec. 11, 1956 K. L.. BERNINGER ET AL 2,773,452

PUMP CONTROL SYSTEM Filed Nov. 15, 1952 3 Sheets-Sheet 2 Dec. 1l, 1'956 K.| .BERN1NGER r-:TAL 2,773,452

PUMP CONTROL SYSTEM v Filed Nov. 15, 1952 3 Sheets-Sheet 3 J ENToRs t fem/f .5m/MGM wuz/An A. wf/.s

United States Patent O PUMP CONTROL SYSTEM Kenneth L.v Berninger and William A. Weis, Dayton,lhio, assignors to General Motors Corporation, Detroit, Mich., a corporation of Delaware' Application November 1S, 1952, Serial No. 320,797

Claims. (Cl. 10S-11) The present invention relates to uid pressure systems and more particularly to pump control mechanism for automatically activating auxiliary pumps when the system, associated therewith, requires additional flow.

In pumping systems wherein the rate of flow varies substantially, resort must either be had to the use ofvariable displacement pumps, or some means, in a system employing constant displacement pumps, for activating and deactivating auxiliary pumps automatically in response to the flow requirements of the system. The in-' auxiliary pump or pumps when additionall flow is re-V quired.

The aforementioned and other objects are accomplished in the present invention by providing clutch meansv actuated by the ilow requirements of the system for automatically engaging and disengaging the driving means for thel auxiliary pumps. Specifically, the fluid pressure supply system includes a pair of continuously operable pumps, a plurality of auxiliary pumps which are normally inoperative, a pressure control valve for anticipating the system ow requirements, a servo valve mechanism, and a servo actuated clutch for activating the auxiliary pumps in response to conditions prevalent in the system.

The structural component of the pressure fluid system herein disclosed comprises a servo actuated brake mechanism. The brake mechanism is enclosed by a rotatable structure as are the several pumps. The rotating structure is adapted to revolve about a xed shaft to which a power gear, constituting one of the brake members, is operatively connected. The power gear projects into the rotatablel casing and has operative engagement with the driving means for the continuously operable pumps whereby krelative rotation between the driving means and the power gear actuates the continuously'operable pumps. A second gear, constituting the second brake member, is disposed within the regulator and adapted for axial and rotative movement relative to the power gear. One of the gears has a suitable friction facing thereon. The auxiliary pumps have driving means in operative engagement with the second gear. Accordingly, when pressure fluid is admitted to the brake servo chamber, the auxiliary gear will be moved axially into engagement with the power gear whereby rotation thereof will cease and the auxiliary pumps will be activated.

Further objects and advantages of the present invention will be apparent from the following description, reference being had to the accompanying drawings wherein preferred embodiments of the present invention l are clearly shown.

2,773,452 Patented Dec,l 1 1, l1956 In the drawings:

Fig. l is a schematic diagram of the supply system.

Fig. 2 is a fragmentary section,`partly in elevation and partly in section of the variable pitch propeller unit.

Fig. 3 is an enlarged view, partly in section and partly in v elevation of the rotatable structure enclosing the fluid pressure system.

Fig. 4 is a sectional View taken in the direction of line 4--4'of Fig. 3.

The present invention is exemplified in conjunction with a variable pitch propeller only by way of example, as it is apparent that the novel features of'this invention could be employed in a number of capacities. With particular reference to Fig. 1, the fluid pressure supply system includes a pair of continuously operable pumps 10 and 11 which discharge through check valves 12 and 13 into trunk line 14. Trunk line 14 communicates with aservo actuated load device 15 of any suitable character and with a chamber 16 of a pressure control valve 17. Four

auxiliary pumps

18, 19, 20 and 21, when activated, discharge through

check valves

22, 23, 24 and 25, respectively, into trunk line 14. The driving means for the auxiliary pumps includes

gears

26, 27, 23 and 29, each of which has operative driving engagement with a gear 3i).

As will appear more fully hereafter, the auxiliary pumps are activated when the gear 30 is restrained from rotation. ln Fig. l, the means for restraining the rotation of the gear Sil is shown schematically as comprising a shoe member 32 on one end of a plunger 33, the plunger 33 being movably mounted within a servo cylinder 34. Pressure uid is admitted to the servo cylinder 34 from the line 35 which is connected to a port 36 of a ow valve 37. 4The operation and functions of the pressure control valve i7 and the ow valve 37 are more fully described in copending application Serial No. 284,169,

led April 24, 1952, in the name of Kenneth L. Bernin' ger, et al. For the purposes of the instant invention, it is deemed sufficient to refer to these component parts of the system in a general way as the valve structures, per se, form no part of the present invention. As heretofore mentioned, the pressure control valve anticipates the iiow requirements of the system and the load device 15 and when the continuously operable system pumps 1@ and l1 are unable to supply the requisite ow, the pressure control valve will no longer divert pressure liuid through port 38 and line 39 to servo chamber 40 of the flow valve 37. Disposed within the casing of the ow control valve is a spring loaded piston 41. Accordingly when ow is no longer diverted to servo chamber 40, the piston 41 will move upwardly thereby interconnecting

ports

42 and 36 of the ow valve whereby pressure uid will flow from trunk line 14 through line 43,

ports

42 and 36, line 35 and into the cylinder 34 whereupon the plunger 33 is moved to the left as viewed in Fig. l. Movement of plunger 33 to the left will effect engagement between the shoe 32 and gear 3d whereupon rotation of gear 30 will be positively restrained, and the auxiliary pumps will be activated to meet the additional ow requirements of the system. When the ilow requirements of the system decrease, excess iiow will again be diverted by the pressure control valve 17 to the pressure chamber 4b whereupon the plunger 33 will move to the position shown in Fig. l thereby connectingy servo cylinder 34 to drain and release the gear 30 for` rotation.

A structural embodiment of the brake mechanism will now be described in connection with a variable pitch propeller of the type generally shown in the Blanchard et al Patents Nos. 2,307,101Y and 2,307,102. With particular reference to Figs. 2, 3 and 4, the variable pitcbr` propeller unit includes a hub 50 having a plurality of radially extending sockets within which propeller blades are journaled for rotation about their longitudinal` axes. The hub 50 is connected by coupling member 51 toa prime mover 52. Attached to the opposite end of thel hub 50 and rotatable therewith is a housing 53 hereinafter referrerd to as a regulator.- The regulator 53 encloses component parts of the fluid pressure system, shown schematically in Fig. l, and shown in its entirety in the aforementioned application.

As it is seen in Fig. 3, the regulator structure rotates about a fixed hollow shaft 54 which extends through the hub and the regulator for supporting the same. The regulator structure S3 is journaled 'for rotation about the fixed shaft 54 by bearing means 5'5. Attached to the peripheral surface of the fixed shaft by means of straight splines 56 is a pump power gear 57 constituting one of the brake members. The outer periphery of the member 57 is toothed as is shown at S8. The member 57 has a pair of oppositely extending

annular fianges

59 and 60 integral therewith. A sleeve member 61, which constitutes a partof the servo chamber to be described, is attached at one end to a rotatable portion of the regulator 53 and at the other end has a running joint with a flanged portion of the member '7. Coaxially disposed about the sleeve 61 is an annular piston 62 having sealing engagement at 63 and 64 `with portions of the sleeve. The piston 62 forms the other part of the servo chamber to be described. The member 62 is stepped to form a servo chamber 65 between the members 61 and 62, the servo chamber 65 being connected by passage means 66 in the member 61 to the ow control valve port 36 shown in Fig. l. The structural embodiment of the fiow control valve is not disclosed in Fig. 3 as, per se, it forms no part of this invention.

A portion of the external periphery of the annular piston 62 has an integral race-way 67 therein within which a plurality of ball bearings 68, mounted in a cage 69, are disposed. The ball bearings 68 also engage `an integrally formed race-way 70 in an annular member 71. The peripheral surface of the annular member 71 is toothed at 72 and constitutes the second brake member. By reason of the bearing connection between members 71 and 62, movement of the member 62 will be transmitted to the member 71 which will then be moved relative to the brake member 57. Brake member 57 has a friction facing 73 of any suitable character attached to one of its side surfaces by means of rivets 74 or the like.

With particular reference to Fig. 4, driving gears 75 and 76 for the continuously operable pumps 10 and 11 are shown `in driving engagement with toothed portions of the brake member 57. The clutch members 57 and 71 are located in spaced parallel planes and, as shown, the auxiliary pumps 18, 19, 2G and 21 have their driving gears 26, 27, 2S and 29 in engagement with the toothed portions of the clutch member 71.

The operation of the brake mechanism for activating the auxiliary pumps is as follows: When the flow requirements of the system with which the pumps are associated can be supplied by continuously operable pumps` and 11, brake member 71 will not be in driving engagement with the friction facing 73 of the brake member 57. It is to be understood that the system pumps 10 and 11 are rendered operative by reason of relative rotation occurring between the driving gears 75' and 76 and the fixed clutch member 57. When these conditions prevail, the brake member 71 may rotate freely by reason of the driving engagement between this member and the

gears

26, 27, 28 and 29 of the auxiliary pumps. In this instance, the ball bearings 68 serve to journal brake member 71 for rotation relative to brake member 57.

Upon the pressure control valve anticipating a need for greater fiow, pressure fluid will be admitted to the servo chamberGS whereupon piston 62 will be moved axially to the left as viewed in Fig. 3. The piston 62, in so moving, moves the clutch member 71 axially into engagemerit with the friction facing 73 on the brake member 57 through the ball bearings 68. Accordingly, relative rotation will now ensue between the driving gears of the auxiliary pumps and the brake member 71 whereupon the auxiliary pumps will be activated. It is to be understood that the brake member 71 will only be restrained from rotation relative to the brake member 57 as long as a predetermined pressure is maintained within the servo chamber 65. As soon as the pressure within servo chamber falls below a predetermined potential by reason of excess ow again being diverted by the pressure control valve, schematically shown in Fig. l, the member '71 will no longer be restrained from rotation. In this manner, the auxiliary pump will be deactivated as soon as the liow requirements of the system can be supplied by the continuously operable pumps 10 and 11.

From the foregoing, it is apparent that the present invention discloses a pump control mechanism capable of diversified use. The component parts of the pump and control mechanism are simple in design, and can easily be modified and adapted to the needs of any variable ow pressure system.

While the embodiments of the present invention as hereindisclosed, constitute preferred forms, it is to be understood that other forms might be adopted.

What is claimed is as follow:

l. In a fluid pressure system, the combination including, a continuously operable pressure developing source discharging into the system, a normally inactive auxiliary pressure developing source connected to said system, activating mechanism operatively associated with said auxiliary pressure developing source and including a servo actuated brake for activating said auxiliary pressure developing source, and pressure responsive means connected with said system for actuating said brake.

2. In a fluid pressure system, the combination including, a continuously operable pressure developing source discharging into the system, a normally inactive auxiliary pressure developing source connected to said system, means operatively connected to said auxiliary pressure developing source for activating the same including a servo actuated brake for rendering said activating means operative, and pressure responsive means connected with said system for activating said brake which, in turn, renders the activating means operative whereby the auxiliary pressure developing source will be activated.

3. In combination with a structure rotatable about a fixed shaft, a first brake member attached to said shaft, a second brake member journaled for rotation about said shaft, said brake members having co-engaging faces, first pump means attached to said rotating structure and having driving means operatively engaging said first brake member whereby relative movement therebetween will activate said first pump means, second pump means attached to said rotating structure and having driving means operatively engaging said second brake member, and means operatively connected with said second brake member for effecting engagement of said brake members whereby relative rotation will ensue between the driving means of said second pump means and the second brake member to activate said second pump means.

4. In combination with a structure rotatable about a fixed shaft, a rst brake member attached to said shaft, a second brake member journaled for rotation about said shaft, said brake members having co-engaging faces, first pump means attached to said rotating structure and having driving means operatively engaging said first brake member whereby relative movement therebetween will activate said first pump means, second pump means attached to said rotating structure and having driving means operatively engaging said second brake member, said brake members having toothed peripheries, and

means operatively connected with said second brake member for effecting engagement of said brake members whereby relative rotation will ensue between the driving means or said second pump means and the second brake member to activate said second pump means.

5. In combination with a structure rotatable about a xed shaft, a rst brake member attached to said shaft, a second brake member journaled for rotation about said shaft, said brake members having co-engaging faces, first pump means attached to said rotating structure and having driving means operatively engaging said rst brake member whereby relative movement therebetween will activate said rst pump means, second pump means attached to said rotating structure and having driving means operatively engaging said second brake member, means including an axially movable annular piston member operatively associated with said second brake member for effecting movement thereof into engagement with said first brake member to activate said second pump means.

6. In a fluid pressure system, the combination including, a housing rotatable about a fixed shaft, primary pressure developing means carried by said housing and having operative engagement with said ixed shaft, Said primary pressure developing means being continuously operative upon relative rotation between said housing and said shaft to supply liuid under pressure to said system, auxiliary pressure developing means carried by said housing, activating means operatively connected with said auxiliary pressure developing means and operatively engageable with said fixed shaft for activating said auxiliary pressure developing means, and pressure responsive means connected with said system for effecting operative engagement with said activating means and said xed shaft to activate said auxiliary pressure developing means.

7. In a fluid pressure System, the combination including, a housing rotatable about a lixed shaft, primary pressure developing means carried by said housing and having operative engagement with said fixed shaft, said primary pressure developing means being continuously operative upon relative rotation between said housing and said shaft to supply uid under pressure to said system, normally inactive auxiliary pressure developing means carried by said housing, means operatively connected with said auxiliary pressure developing means and rotatable therewith for activating said auxiliary pressure developing means, and pressure responsive means connected with said system for restraining rotation of said activating means so as to render said auxiliary pressure developing means operative.

8. In a iluid pressure system, the combination including, a housing rotatable about a fixed shaft, primary pressure developing means carried by said housing and having operative engagement with said fixed shaft, said primary pressure developing means being continuously operative upon relative rotation between said housing and shaft to supply iluid under pressure to said system, normally inactive auxiliary pressure developing means carried by said housing, means operatively connected to said auxiliary pressure developing means and normally rotatable therewith for activating said auxiliary pressure developing means, means for restraining rotation of said activating means, and pressure responsive means connected With the system for actuating said restraining means which, in turn, renders the activating means operable whereby the auxiliary pressure developing means will be activated.

9. In 'a fluid pressure system, the combination including, a housing rotatable about a fixed shaft, primary pressure developing means carried by said housing for supplying fluid under pressure to said system, a gear attached to said iixed shaft, means interconnecting said gear and said primary developing means for rendering said primary pressure developing means continuously operative during relative rotation between said housing and Said shaft, normally inactive auxiliary pressure developing means carried by said housing, and pressure responsive means connected with said system for activating said auxiliary pressure developing means.

l0. In a uid pressure system, the combination including, a housing rotatable about a fixed shaft, primary pressure developing means carried by said housing for supplying tluid under pressure to said system, a rst gear attached to said iixed shaft, means interconnecting said first gear and said primary pressure developing means for rendering said primary pressure developing means continuously operative during relative rotation between said housing and said shaft, normally inactive auxiliary pressure developing means carried by said housing, a second gear journaledfor rotation about said fixed shaft and movable axially relative thereto, means interconnecting said second gear and said auxiliary pressure developing means, said first and second gears having coengaging friction surfaces, and means operatively connected with said second gear and operable to effect axial movement of said second gear so that the frictional surfaces of said gears are in engagement thereby restraining rotation of said second gear and activating said auxiliary pressure developing means.

References Cited in the le of this patent UNITED STATES PATENTS 960,249 Beaudette June 7, 1910 1,047,328 Sundh Dec. 17, 1912 2,042,247 Blood May 26, 1936 2,147,334 De Boysson Feb. 14, 1939 2,194,054 Peterson Mar. 19, 1940 2,458,452 Vanni Ian. 4, 1949 2,526,646 Ericsson Oct. 24, 1950 2,595,618 Vogt et al May 6, 1952 2,626,669 Moore et al. Jan. 27, 1953 2,695,070 Geyer et al Nov. 23, 1954 FOREIGN PATENTS 747,282 France Mar. 8, 1933