US3070025A - Injector discharge pressure regulator for pumps - Google Patents

Injector discharge pressure regulator for pumps Download PDF

Info

Publication number
US3070025A
US3070025A US718742A US71874258A US3070025A US 3070025 A US3070025 A US 3070025A US 718742 A US718742 A US 718742A US 71874258 A US71874258 A US 71874258A US 3070025 A US3070025 A US 3070025A
Authority
US
United States
Prior art keywords
pressure
sleeve
chamber
inlet
pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US718742A
Inventor
Cliborn Robert
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Northrop Grumman Space and Mission Systems Corp
Original Assignee
Northrop Grumman Space and Mission Systems Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Northrop Grumman Space and Mission Systems Corp filed Critical Northrop Grumman Space and Mission Systems Corp
Priority to US718742A priority Critical patent/US3070025A/en
Application granted granted Critical
Publication of US3070025A publication Critical patent/US3070025A/en
Anticipated expiration legal-status Critical
Application status is Expired - Lifetime legal-status Critical

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/66Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/688Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for liquid pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0005Control, e.g. regulation, of pumps, pumping installations or systems by using valves
    • F04D15/0011Control, e.g. regulation, of pumps, pumping installations or systems by using valves by-pass valves

Description

R. CLIBORN INJECTOR DISCHARGE PRESSURE REGULATOR FOR PUMPS Filed March 3, 1958 3 Sheets-Sheet l barn - Faberf 67/ Dec. 25, 1962 R. CLIBORN 3,070,025

INJECTOR DISCHARGE PRESSURE REGULATOR FOR PUMPS Filed March 5, 1958 3 Sheets-Sheet 2 p/sc/m P65 54 O AFL'A LL 2 210 T Eoberf C/[barzz b M lmww' afia??? R. CLIBORN INJECTOR DISCHARGE PRESSURE REGULATOR FOR PUMPS Filed March 3, 1958 3 Sheets-Sheet 3 United States Patent Oflflce dfilfldlzfl Patented Dec. 25, 1962 3,fl7tl,tl25 INEECTUR DISQIilARGE PRESSURE REGULATQR FUR FUR H d Robert Clihorn, filevelancl, @hio, assignor to Thompson Raine Wcoldridge line, a corporation oi ()hio Filed Mar. 3, 11953, er. No. 718,742 4 Claims. {61. ltl3-97) This invention relates to pumping apparatus and more particularly to a pump having a ssrouded impeller and a casing which provides a chamber in communication with the discharge portion of the pump, and which affords a gap adapted to control the flow of fluid from the chamber into t.'.e central area of the casing in accordance with the discharge pressure in the chamber.

According to the general principles of the present invention, and as set forth in applicants copending application Serial No. 327,216, filed December 19, 1953, now Patent No. 2,865,297, of which the present application is a continuation-impart, an impeller is provided which has a central inlet and includes a plurality of pumping passageways communicating with the central inlet and extending radially outwardly to the periphery of tile imeller. A pump casing provides a volute pumping chamber for the impeller and a cover member on the end of the casing has an open ended inlet passageway adapted to lie in registry with the central inlet of the impeller.

In one form of the invention an annular lip is provided at one end of the passageway and is situtated adjacent an annular chamber formed in the cover member The annular chamber communicates with the pump dis charge through a plurality of circumferentially spaced metering passages. A sleeve is received in the inlet passageway of the cover member and includes an end portion which provides a closure for the annular camber. The end portion of the sleeve cooperates with the annular lip to form an injector gap which directs a sheet of fluid across the width under a big; velocity into the inlet of the impeller. The injector ction improves the fuel velocity distribution in the inlet by accelerating the slow moving particles of fluid in the boundary layer where the velocity of the impeller inlet is at a maximum. The injecior action not only serves to prime the pump but also provides a radial velocity distribution corresponding with the linear velocities of the impeller vane. Cavitation is thus prevented and operation at lower fuel inlet heads is possible.

The width of the injector gap is controlled automatically by the pump discharge pressure which is introduced into the pressure control chamber to afford axial adjustment of the sleeve controlling the width of the injector gap.

in a second embodiment the width of a throttling orifice is controlled by the ambient pressure for the pump, in accordance with. the pressure control principle of the invcntion.

Anot'er embodiment of the invention provides for an automatically adjustable pressure gap as described, which is controlled by the inlet pressure for the pump but which is responsive thereto so as to throttle the flow of fluid through the pump.

in this embodiment, the control of the throttling action by the inlet pressure is effective to afford a predetermined substantially uniform pumping pressure and flow. Yet another embodiment provides for throttling the flow through the pump in response to the ambient pressure for the pump.

Accordingly, it is an object of the present invention to provide an integral discharge pressure regulator for pumps in which a pressure chamber of substantially annular configuration is disposed in a cover for the pump and ha a gap whose width is determined in accordance with the pressure in the pressure chamber whereby to control the rate of flow to the pump.

Another object is to provide a structure as described which reduces cavitation in the pump, by providing a rate of flow directly determined in accordance with the requirements of the pump.

Another object is to provide a discharge control which in one embodiment thereof is adapted to maintain the flow of fluid to the pump with decreasing inlet pressure.

Another object is to provide a discharge control means as described which, in another embodiment, is regulated by ambient pressure relative to the pump.

Another object of the invention is to provide a discharge control system in which, in another embodiment, the ambient pressure is effective to adjust the gap so as to throttle the system.

Yet another object of the invention is to provide a discharge control means as described in which the throttling action is responsive to the pressure condition at the inlet portion of the system.

Many other features, advantages and additional objects of the present invention will become manifest to those versed in the art upon making reference to to detailed description which follows and the accompanying sheet of drawings, in which a preferred structural embodiment incorporating the principles of the present invention is shown by way of illustrative example.

In the drawings:

FEGURE 1 is a fragmentary cross ectional view of an injector cover for a pump constructed in accordance with the principles of the present invention in affording automatic control or an injector gap structure;

FIGURE 2 is a front view of another embodiment of the invention in which the injector gap is controllable in accordance also with the ambient pressure relative to the p p;

FIGURE 3 is a sectional view of the pump shown in FIGURE 2;

FEGURE 4 is a sectional view of an embodiment controlled by inlet pressure to throttle tee system so as to maintain substantially uniform how; and

FIGURE 5 is an embodiment corresponding to that of FlGURE 4 in which the throttling action. is controlled by the ambient pressure.

As shown on the drawings: 1

Referring now to FlGURE l, a pump incorporating the principles of the present invention is indicated gen erally by reference numeral 1t) and includes a casing ill formed by a body member 12 and a cover member 13 suitably flanged and bolted together by a plurality of fasteners 13a and sealed by an O-ring 13b. As shown in PiGURE 1, the cover 13 has a bypass chamber 14 and is provided with a central inlet passageway 15 opening into a volute pumping chamber 15 carrying a bearing ring 17 in which is journalled the hub portion 18 of a shrouded impeller 19. The cover member 13 also includes an annular lip 2t} which co-operates with a. tapered end portion 21 of a sleeve member 22 so as to provide an injector gap 23 arranged to direct a sheet of fluid across the lip 2t} and into the central inlet 15a of the impeller 1?, as hereinafter further described. The inlet passageway 15 is counterbored to provide an annular shoulder 1441, the counterbored portion of the inlet passageway 15 receiving a radially extending flange 24 forming an annular abutment shoulder for the sleeve member 22.

The flange 24 of the sleeve 22 and shoulder 14a of the cover member 13 together form opposite sides of a pressure control chamber 25. By introducing a pressure fluid into the pressure control chamber 25, an axial thrust will be imparted to the sleeve member 22 which will tend to move the sleeve member in one direction so as to increase the width of the injector gap 23. In order to conduct such a pressure fiuid into the control chamber 25 a plurality of circumferentially spaced passageways 26 is provided in the cover member 33 which place the pressure control chamber 25 in communication with the: chamber 14. The chamber 14 in turn communicates with the pumping chamber 16 through a plurality of circumferentially spaced passageways 2'7 opening to the discharge portion 23 of the said pumping chamber. Toprovide a control bias for the sleeve member 22, a coil spring 2h is bottomed against a retainer 3% which is carried in a recess 31 formed in the inlet passageway 35. The spring 29 engages the opposite face of the flange 2 s on the sleeve member 22 at its other end, and there is thus exerted a continuous spring pressure on the sleeve member 22 tending to close the injector gap By virtue of this arrangement, the position of the sleeve 22 will be variable with the pump discharge pressure and accordingly, the width of the injector gap will be automatically controlled as a function thereof, with corn sequent improvement in fuel velocity distribution and substantial elimination of cavitation.

Referring now to FIGURES 2 and 3, a second ernbodiment of the invention is seen and designated generally by reference numeral 32. A casing 33 is provided for the control means 32 which is mounted by bolts 34 on an impeller housing 35 in which is journalled an impeller drive shaft 36 for connection with an engine drive (not shown). The shaft 36 is supported in the housing 35 by bearings 37 and 38, a shrouded impeller 59 being fixed thereto within a chamber 4%. The impeller 39 is provided with pressure equalizing passages 4-2 and i3 as shown, in the impeller 39 and between the impeller bearing ring 4 and the opposed ring & respectively, this structure forming no part of the present invention. The hub 46 of the impeller is sealed by bearings 37 and 4 8 within an inlet passageway 49 in the casing 35, which opens directly into the central pumping chamber as of the impeller. Thus the fiuid is passed from the inlet 4'3 through the central pumping chamber 50 and the impeller 39 into the discharge area 41 around plate 41a and thence into the control system 32 the plate 41a preferably extending entirely in back of the face of the rotor or impeller 3? but being open in register with the control means 32 to place the control means in communication with the discharge area 41, as seen in FIGURES 2 and 3.

The casing 33 has a body portion 51 and an outlet portion 52 suitably flanged and bolted together by bolts 53, and in order to afford control of the discharge flow from the pump, the body portion 51 defines an annular flow chamber 54 in communication with the discharge area :1. The chamber 54 has an inset Wall 55 which cooperates with a sleeve 56 having a tapered end 57, to define an annular throttling orifice 58, the casing having a counterbored portion 59 which cooperates with the sleeve 55 to define a pressure control chamber 68 in in accordance with the invention. The discharge por tion 52 is provided with a central bore 61 whose inner portion 62 is of relatively wide diameter to form part of the chamber as, an intermediate portion thereof 63 receiving the relatively thickened sleeve portion 64, which at its other end (65 rides on an annular bearing wall 66 having a seal 57a. The sleeve thus provides a shoulder 67 against which a pressure ring 63 is biased by means of a spring 69 so as to urge the sleeve 56 toward the outlet end it? of the bore, which is of reduced diameter in comparison with the intermediate area 63. As seen, the inner end 73 of the sleeve $6 is tapered and blunt, and is spaced from the shoulder '72 between portions 63 and '70 of the bore 61.

In order to throttle the fluid passing through the throttling orifice $3 to afford a uniform flow, the body portion 51 of the casing 33 defines a passage 73 which affords communication between the pressure control chamher i0 and the ambient pressure for the pump. The pressure acts on the pressure ring 6% in cooperation with the spring 6% to urge the sleeve 56 to the left. The ambient pressure thus acts on the area provided by the sleeve shoulder 67, which is of a predetermined dimension for this purpose. Balancing these forces, and effecting the desired differential throttling action, is the pressure from within the bore 61 and the intermediate portion 63, which also acts on a pressure area which is defined by the shoulder 67 of the sleeve 56. Thus the forces on the opposite ends of the sleeve 56 substantially balance out except for an area at the left hand extremity of the sleeve which corresponds to the dimensions of the shoulder 67. This pressure on the left hand extremity of the sleeve 56 serves to move the sleeve 56 toward the right to reduce the throttling gap or orifice 58 to an extent which will provide the desired continuously uniform discharge flow. An O-ring e351 may be provided in the discharge portion 63 to insure that a pressure differential will be maintained between the left hand extremity of the sleeve 56 and the portion of the sleeve 56 provided by the shoulder 67.

Referring now to FIGURE 4, a third embodiment of the invention is seen wherein a differential pressure sleeve controls the width of an injector gap as hereinbefore described, the discharge pressure being utilized in conjunction with the inlet pressure for this purpose. This system '74 has a casing 75 which is formed by a body member '76, as well as a cover member 77, elements 7d and '77 being suita ly flanged and bolted together by a plurality of fasteners '78, and sealed by an Q-ring 79. The body portion is has a bypass chamber St) and is provided with an inlet passageway 81 which opens into a pumping chamber 32 carrying a bearing ring 83 in which is sealed the hub portion $4 of a shrouded impeller 85, the by pass chamber (iii receiving fiuid from chamber 82 through passages 82 a, substantially as described with respect to the first embodiment of the invention. The body 76 also defines an annular lip 86 which co-operates with a tapered end portion of a sleeve 87 so as to provide an injector gap 83 arranged to direct a sheet of fluid across the lip $6 and into the central portion 81a of the impeller 35. The inlet passage 81 is counterbored to define an annular shoulder 39 which co-operates with the sleeve 87 and a cap 90, to provide a pressure control chamber M, the cap 9i; having a relatively wide bore 92; forming part of the chamber 91 and being fastened to the body portion 76 by means of a counterbore 93 and bolts $4, a seal a being disposed in the cap In order to provide a differential pressure control as described, the sleeve 87 defines a shoulder 95 within the chamber 91, and an opposed shoulder 96 adapted to receive pressure from the chamber fit The sleeve also has formed therein a plurality of apertures 97 intermediate the ends of the chamber 91 whereby the inlet pressure in the passage 81 is transmitted to the said chamber and acts upon an area corresponding to that of the shoulder 95 to urge the sleeve 87 to the left, in cooperation with a spring 98 which bears against a pressure bearing 99 which is retained against the shoulder 95. This force is balanced by the pressure from the discharge portion of the pump unit in the chamber 8% to vary the width of the injector gap 38, whereby a desirable velocity distribution of the fiuid is achieved in the boundary layer where the velocity of the impeller is at a maximum.

The embodiment of FIGURE 5 corresponds structurally to that of FIGURE 4, and similar parts are suitably indicated and otherwise designated by similar reference numbers, but the ambient pressure for the pump is utilized to make the pump discharge pressure control system independent of the inlet pressure for the pump. This is accom lished by means of a passage to defined in the body portion 76a and affording communication between the chamber filo and the fluidsurrounding the pump.

The action of the embodiments of FIGURES 1, 4 and 5 is thus the opposite of that of the embodiment of FIG- URES 2 and 3, in the sense that the discharge pressure of the first and last embodiments tends to open the injector gap, while in the second embodiment it tends to close the gap to provide a uniform delivered pressure. However, in each of the embodiments the control is achieved in accordance with pressure sensitive means which afford a constantly adjusted flow metering action.

Although I have herein set forth and described my invention with respect to certain specific principles and details thereof, it will be obvious to those skilled in the art that these may be varied without departing from the spirit and scope of the invention as set forth in the hereunto appended claims.

I claim as my invention:

1. A pump construction comprising a pump having a housing,

an impeller journalled in said housing,

said housing having an inlet and an outlet for said impeller,

a discharge pressure regulator for said pump including a casing mounted on said housing,

said casing having an inlet communicating with the outlet of said housing,

a control sleeve slidably mounted in said casing and registered with said inlet in said casing,

said casing having a chamber around said sleeve and closed by said sleeve,

said sleeve providing a passage therethrough and said passage normally communicating with the inlet in said casing,

said casing having an outlet communicating with said passage,

a throttling surface on said casing in register with said sleeve,

said sleeve normally spaced from said surface in variably proximate relationship to adjustably throttle the casing inlet in response to movement of the sleeve,

said sleeve having a relatively large pressure surface at the end thereof adjacent the outlet in said casing for urging the sleeve toward the throttling surface in response to fluid pressure in the passage,

said sleeve having a relatively small pressure surface at the end thereof adjacent said inlet in said casing for urging the sleeve away from the inlet in response to pressure at the inlet,

said sleeve having a shoulder within said chamber disposed to urge the sleeve away from the casing inlet in response to fluid pressure thereagainst,

spring means in said chamber urging said sleeve toward the outlet in said casing,

and a passageway in said casing communicating said chamber with the exterior of said casing for pressurizing said chamber and said shoulder in said chamber with ambient fluid whereby said pressure surfaces and said shoulder cooperate with said spring means to control said throttling as a function of the pressure of the ambient fluid and the pressure of the fluid entering said casing through said inlet in said casing.

2. The device according to claim 1 wherein said relatively large pressure surface on said sleeve has a cross sectional dimension equal to the cross sectional dimension of said relatively small pressure surface plus the cross sectional dimension of said shoulder on said sleeve to provide a sensitively adjusted throttling action.

3. A pump construction comprising a pump having a housing,

an impeller journalled in said housing,

an inlet in said housing for said impeller and an outlet in said housing for said impeller,

and a flow control device for said pump including a casing structure for said housing,

a sleeve in said casing structure,

an inlet in said casing structure in register with said sleeve,

a throttling surface on said casing structure,

said sleeve being in proximate adjustable register with said throttling surface.

means transmitting fluid from the impeller outlet past the throttling surface for controlling the flow of said fluid to a point of use,

said casing structure having a chamber surrounding said sleeve and substantially closed by said sleeve,

a pressure surface on one end of said sleeve pressurized by fluid in said inlet in said casing structure to urge the sleeve away from the inlet in the casing structure,

a pressure surface at the opposite end of the sleeve exposed to fluid from the impeller discharge to urge the sleeve in a direction opposite from the pressure surface on said one end of said sleeve,

a shoulder on said sleeve in said chamber disposed to urge the sleeve away from the inlet in response to fluid pressure thereagainst,

means communicating said chamber with a source of pressurized fluid to pressurize the shoulder,

and spring means acting against the sleeve to urge the sleeve away from the inlet in said casing structure,

said pressure surfaces, said shoulder and said spring means cooperatively eflecting throttling of the inlet by reciprocation of the sleeve toward and away from said throttling surface as a function of the pressure of the source of pressurized fluid and fluid pressure at the inlet.

4. The pump construction of claim 3 wherein the flow control device for the pump is mounted in the inlet of said housing.

References Cited in the file of this: patent UNITED STATES PATENTS 921,916 Trent May 18, 1909 1,322,810 Moody Nov. 25, 1919 1,353,915 Kime Sept. 28, 1920 1,465,097 Sherzer Aug. 14, 1923 1,801,370 Schmidt Apr. 21, 1931 1,849,557 Stelzer Mar. 15, 1932 2,556,829 Teague June 12, 1951 2,574,631 Ely Nov. 13, 1951 2,684,634 Schneider July 27, 1954 2,785,634 Marshall Mar. 19, 1957 2,786,420 Kenney Mar. 26, 1957 2,819,675 Gilman Jan. 14, 1958 2,861,585 Becker Nov. 25, 1958 FOREIGN PATENTS 133,892 Switzerland Sept. 16, 1929 636,848 Great Britain May 10, 1950

US718742A 1958-03-03 1958-03-03 Injector discharge pressure regulator for pumps Expired - Lifetime US3070025A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US718742A US3070025A (en) 1958-03-03 1958-03-03 Injector discharge pressure regulator for pumps

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US718742A US3070025A (en) 1958-03-03 1958-03-03 Injector discharge pressure regulator for pumps

Publications (1)

Publication Number Publication Date
US3070025A true US3070025A (en) 1962-12-25

Family

ID=24887309

Family Applications (1)

Application Number Title Priority Date Filing Date
US718742A Expired - Lifetime US3070025A (en) 1958-03-03 1958-03-03 Injector discharge pressure regulator for pumps

Country Status (1)

Country Link
US (1) US3070025A (en)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3238534A (en) * 1962-10-15 1966-03-01 English Electric Co Ltd Hydraulic pumps and reversible pump turbines
US3285501A (en) * 1964-12-07 1966-11-15 John E Mcdonald Centrifugal fans
US3504986A (en) * 1968-03-12 1970-04-07 Bendix Corp Wide range inducer
DE2337601A1 (en) * 1972-09-05 1974-03-14 Saurer Ag Adolph Annex to mix and circulate waermetraegern
NL7408962A (en) * 1973-07-03 1975-01-07 Smedegaard As Centrifugal regulating mechanism.
US3871796A (en) * 1973-11-15 1975-03-18 Mccord Corp Pump assembly
JPS5171502A (en) * 1974-12-18 1976-06-21 Hitachi Ltd Honpuno kyabiteeshonboshisochi
JPS5293902U (en) * 1976-01-09 1977-07-13
US4120603A (en) * 1977-03-28 1978-10-17 General Motors Corporation Jet flap controlled fuel pump
US4661041A (en) * 1985-11-05 1987-04-28 Itt Corporation Self-draining pump arrangement
US4884943A (en) * 1987-06-25 1989-12-05 A. Ahlstrom Corporation Method and apparatus for pumping high-consistency fiber suspension
US6699008B2 (en) 2001-06-15 2004-03-02 Concepts Eti, Inc. Flow stabilizing device
US20050152775A1 (en) * 2004-01-14 2005-07-14 Concepts Eti, Inc. Secondary flow control system
US20170037856A1 (en) * 2015-08-03 2017-02-09 Parker-Hannifin Corporation Integral pump pressure relief valve

Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US921916A (en) * 1908-01-06 1909-05-18 Simeon V Trent Cut-off valve for centrifugal pumps.
US1322810A (en) * 1919-11-25 Rotary pump with adjustable gate
US1353915A (en) * 1919-11-21 1920-09-28 Ransom R Micks Centrifugal-pump
US1465097A (en) * 1923-08-14 Regulating centkieugal pumps
CH133892A (en) * 1928-07-18 1929-06-30 Sulzer Ag Centrifugal pump.
US1801370A (en) * 1927-10-11 1931-04-21 Westinghouse Electric & Mfg Co Oil impeller for governors
US1849557A (en) * 1929-06-12 1932-03-15 M T Davidson Company Centrifugal pump
GB636848A (en) * 1948-05-19 1950-05-10 Sidney Zaleski Hall Improvements in or relating to centrifugal pumps
US2556829A (en) * 1945-03-20 1951-06-12 Bendix Aviat Corp Fluid regulator
US2574631A (en) * 1950-04-28 1951-11-13 Ely George William Constant pressure centrifugal pump
US2684634A (en) * 1946-04-16 1954-07-27 Sfindex Guiding means for liquids and gases
US2785634A (en) * 1950-08-18 1957-03-19 Bendix Aviat Corp Fluid pressurizing apparatus
US2786420A (en) * 1952-03-27 1957-03-26 Stanley G Harwood Pressure controlled pump
US2819675A (en) * 1953-08-18 1958-01-14 Worthington Corp Propeller pump or blower
US2861585A (en) * 1954-04-19 1958-11-25 Logansport Machine Company Hydraulic relief valve

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1322810A (en) * 1919-11-25 Rotary pump with adjustable gate
US1465097A (en) * 1923-08-14 Regulating centkieugal pumps
US921916A (en) * 1908-01-06 1909-05-18 Simeon V Trent Cut-off valve for centrifugal pumps.
US1353915A (en) * 1919-11-21 1920-09-28 Ransom R Micks Centrifugal-pump
US1801370A (en) * 1927-10-11 1931-04-21 Westinghouse Electric & Mfg Co Oil impeller for governors
CH133892A (en) * 1928-07-18 1929-06-30 Sulzer Ag Centrifugal pump.
US1849557A (en) * 1929-06-12 1932-03-15 M T Davidson Company Centrifugal pump
US2556829A (en) * 1945-03-20 1951-06-12 Bendix Aviat Corp Fluid regulator
US2684634A (en) * 1946-04-16 1954-07-27 Sfindex Guiding means for liquids and gases
GB636848A (en) * 1948-05-19 1950-05-10 Sidney Zaleski Hall Improvements in or relating to centrifugal pumps
US2574631A (en) * 1950-04-28 1951-11-13 Ely George William Constant pressure centrifugal pump
US2785634A (en) * 1950-08-18 1957-03-19 Bendix Aviat Corp Fluid pressurizing apparatus
US2786420A (en) * 1952-03-27 1957-03-26 Stanley G Harwood Pressure controlled pump
US2819675A (en) * 1953-08-18 1958-01-14 Worthington Corp Propeller pump or blower
US2861585A (en) * 1954-04-19 1958-11-25 Logansport Machine Company Hydraulic relief valve

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3238534A (en) * 1962-10-15 1966-03-01 English Electric Co Ltd Hydraulic pumps and reversible pump turbines
US3285501A (en) * 1964-12-07 1966-11-15 John E Mcdonald Centrifugal fans
US3504986A (en) * 1968-03-12 1970-04-07 Bendix Corp Wide range inducer
DE2337601A1 (en) * 1972-09-05 1974-03-14 Saurer Ag Adolph Annex to mix and circulate waermetraegern
US3893785A (en) * 1972-09-05 1975-07-08 Saurer Ag Adolph Device for mixing and impelling of heat-exchange fluids
NL7408962A (en) * 1973-07-03 1975-01-07 Smedegaard As Centrifugal regulating mechanism.
US3871796A (en) * 1973-11-15 1975-03-18 Mccord Corp Pump assembly
JPS5171502A (en) * 1974-12-18 1976-06-21 Hitachi Ltd Honpuno kyabiteeshonboshisochi
JPS5293902U (en) * 1976-01-09 1977-07-13
US4120603A (en) * 1977-03-28 1978-10-17 General Motors Corporation Jet flap controlled fuel pump
US4661041A (en) * 1985-11-05 1987-04-28 Itt Corporation Self-draining pump arrangement
US4884943A (en) * 1987-06-25 1989-12-05 A. Ahlstrom Corporation Method and apparatus for pumping high-consistency fiber suspension
US6699008B2 (en) 2001-06-15 2004-03-02 Concepts Eti, Inc. Flow stabilizing device
US20050152775A1 (en) * 2004-01-14 2005-07-14 Concepts Eti, Inc. Secondary flow control system
US7025557B2 (en) 2004-01-14 2006-04-11 Concepts Eti, Inc. Secondary flow control system
US20170037856A1 (en) * 2015-08-03 2017-02-09 Parker-Hannifin Corporation Integral pump pressure relief valve
US10513343B2 (en) * 2015-08-03 2019-12-24 Parker-Hannifin Corporation Integral pump pressure relief valve

Similar Documents

Publication Publication Date Title
US3504986A (en) Wide range inducer
GB1227052A (en)
US2502546A (en) Hydraulic apparatus
US2873576A (en) Means for controlling the rotational speed of the low-pressure compressor rotor of gas turbine engines
US3104520A (en) Turbosupercharger bypass ejector
US2599680A (en) Liquid distributing system
US3170481A (en) Flow control valve
US2632295A (en) Inlet ram for power plants
US3410287A (en) Pure fluid velocity sensor control apparatus
US2845086A (en) Flow regulators
US2450535A (en) Means for automatically controlling the supply of liquid fuel to a prime mover
US5141389A (en) Control system for regulating the axial loading of a rotor of a fluid machine
US4793589A (en) Piston valve with proportional solenoid controlled pilot valve
GB920331A (en) Improvements in and relating to a control operator for valves
GB1240192A (en) Hydraulic valve assembly
BR0012417B1 (en) Flow regulator
US4817376A (en) Modular sub-assembly for turbine engine fuel control systems
US2333044A (en) Governing mechanism
US2905191A (en) Valve
GB1580082A (en) Variable performance centrifugal pump
GB1109356A (en) Electro-magnetically operated fluid-flow valves
GB1214933A (en) A flow regulator
US2957424A (en) Centrifugal pump
US2600633A (en) Constant volume variable speed driven vane pump
GB1204356A (en) Pressure reducing valve