US2642805A

US2642805A - Fire engine pump governor

Info

Publication number: US2642805A
Application number: US117253A
Authority: US
Inventors: Nepper Richard Curt
Original assignee: AHRENS FOX Inc
Current assignee: AHRENS FOX Inc; AHRENS-FOX Inc
Priority date: 1949-09-22
Filing date: 1949-09-22
Publication date: 1953-06-23
Anticipated expiration: 1970-06-23

Description

JNVENToR 5 Sheeizksheet l R/CHARD Cupr /VEPPE/Q n c. NEPPER FIRE ENGINE PUMP GOVERNOR June 23, 1953 Filed sept 22, 1949 June 23, 1953 R. c. NEPPER 2,642,805

l FIRE ENGIANE PUMP GOVERNORv v y Imam/role.v 'k I /P/CHARD C//Rf/l/EPPER.

1 L L "Qi l R. c NEPPR-f- Fm: msm: Pull? cvm'n June 23, 1953 s tsxmfasnm a mea sept. 2z, 1949 INVENTOA ICHA RD CupT/l/EPPER June 23, 1953 med sept 2z. 1949 Patented June 23, 1953 FIRE ENGINE PUMP GOVERNOR Richard Curt Nepper, Cincinnati, Ohio, assignor, by mesne assignments, to Ahrens-Fox, Inc., Cincinnati, Ohio, a corporation of Ohio Application September 22, 1949, 'Serial No. 117,253 9 claims. (o1. 10s- 17) rIhis invention pertains to kan improved lgovernor control for fire engine pumping apparatus. More particularly, this invention pertains to a new type of hydraulic governor for fire engine pumps.

One of the objects of this invention .is to control the speed of the driving vengine of the lpumper by means of suitable throttle actuating devices in response to vibrations lin power demand as one or more discharge outlets of the pump are opened or closed.

Another object of this invention is to have a hydraulic power control cylinder to actuate the throttle mechanism of one or more carburetors of the driving engine of -a re engine pumper, the piston in the cylinder being controlled by two hydraulically loaded control valves which are responsive to variations in the delivery pressure from the re pump. f

Still another object of this invention is to .provide a throttle control .mechanism for a fire engine pumper which hydraulically actuates the throttle of the driving engine in accordance with the pressure delivered by the water pump so as to automatically maintain a .predetermined discharge pressure for the pump for any condition of hose line demand from the pump.

Further features and advantages of this invention will appear from a detailed description of the drawings in which:

Figure 1 is a schematic diagram illustrating the essential elements and arrangement of thel improved hydraulic fire pump governor control system.

Figure 2 is a plan view, partly in section on the line 2-2 of Figures 3, 4 and 5, showing the hydraulic cylinder actuating mechanism for the throttles of the carburetors of the driving engine.

Figure 3 is a sectional view on the line 3-3 of Figures 2, 4 and 5.

Figure 4 is a Isectional View on the line 4 4 of Figures 2 and 3.

Figure 5 is a sectional View similar to Figure 4.

Figure 6 is a sectional view of the pressure control unit. Y

Figure '7 is a fragmentary enlarged sectional view of a portion of Figure 6, particularly showing residual pressure holding valve and rpiston cup assembly of the pressure control unit.

For illustrative purposes this invention is shown applied to a 'fire engine pumper, Figure 1, having a main driving engine I0 which is connected through the usual transmission YII and drive shaft I2 to drive the water pump I3, the engine having suitable carburetor mechanism shown at I4. v The water pump I3 has `a .suction inlet I5 and a discharge manifold I6 having a series of hose coupling outlets Il and I8 to which any number vand variety of hoses may be connected ina well knownmanner. f l

Referring to Figures 2 and 3 below the car buretors I4', there is provided a .set of governor control throttle valves 1.9, mounted on shafts rod 28 of the throttle actuating cylinder 29. A

suitable piston 30 .is fixed to the inner :end ofthe piston rod .28 and operates in the bore 3l of the cylinder .29 which forms the fluid pressure 'cham ber y32 for actuating the piston 30 for outward movement of the rod 28 limited by the stop sleeve 28a to `close the governor control throttle valves I9 so .as to reduce the speed and power of the engine. A compression spring 33. acting between the surface 34 of the piston 30 and the surface 35 of the mounting bracket 36 carrying the cylinder 29 on the engine intake manifold 23a, normally urges the rod 28 in a direction to open the governor control throttle valves I9.

Fluid pressure for actuating the piston 30 by application of pressure in the chamber 32 is derived from the oil pump or similar fluid pressure source 31 driven from the main driving engine in a conventional manner. The pump 31 receives its supply from the crankcase yreservoir 31a through a suction line 38 and transmits pressure through the pressure line 39 which in turn is connected to the passageway 40 on the control valve body portion 29a of the Acylinder 29. The inlet passageway 40 connects through a suitable fluid resistance 4| with the passageway or bore 42 which in turn opens into the ball valve chamber 43 containing the inlet ballvalve 44. The ball valve chamber 43 connects through the passageway 45, Figure 2, with the pressure chamber 32 of the cylinder 29. The pressure chamber 32 of the cylinder 2 9 also connects through the .passageway 46, Figure 2, with the ball valve chamber containing the discharge b'all valve 4B. The chamber 41 connects through l the passageway -or bore 49 and a suitable fluid resistance yllwith :the r,discharge or return line k5| which conveys Huid l.back to the reservoir 31.

The ball valve 44 is arranged to close against the valve seat 52 and is confined in proper operative position in the chamber 43 by the bushing 53 fixed in the valve body portion 29a. A plunger 54, axially slidable in the bore 42 on a solid head 55 and spaced guide surfaces 56 for free passage of liquid from bore 42 into the chamber 43, is operable to hold the ball valve 44 off the valve seat 52. A similar plunger 51 operating in the bore 58, in the bushing 53, serves to hold the ball Valve 44 against the seat 52. The ball valve 48 is arranged to close against the seat 59 and is confined in proper operative position in the chamber 41 by the bushing 60 fixed in the valve body portion 29a. A plunger 6|, similar to the plungers 54 and 51, is axially slidable in the bore 49 and is operable to hold the ball valve 48 away from the seat 59. A similar plunger 62, axially slidable in the bore 63 of the bushing 60, serves to move the ball valve 48 into engagement with the seat 59.

Across the heads 54a and 62a is a resilient diaphragm 64 of suitable composition material which is held in place by the pressure chamber cover 65 secured to the valve body portion 290J by suitable bolts 66. The pressure chamber 61 in the pressure chamber cover 65 is connected through a line 68 and the shut-off valve 69 to the discharge manifold |6 of the water pump, so that Water pressure in the manifold will be applied in the chamber 61. Suitable bleeder line 10 and valve 10a is povided to remove any trapped air in this circuit.

Over the heads 51a and 6|a of the respective plungers 51 and 6|, there is provided a second resilient diaphragm 12 of suitable composition material which is held in place by the pressure chamber cover 13, secured to the valve body portion by suitable bolts 14. The pressure chamber 15 in the pressure chamber cover 13 is connected through a line 16 with the outlet bushing 11 of the pressure control unit 18, shown best in Figures 6 and '1. A suitable air bleeder 19 is provided for the line 16 to remove entrapped air in this circuit. A pressure gauge h 8| is also connected into the line 16.

The pressure control unit 18 comprises a reservoir portion 82 containing a supply of oil 83 which is poured into the reservoir through the filler cap 84. Below the reservoir is the pressure cylinder portion 85 having a bore 86 in which is reciprocatably mounted the piston 81 having the piston cup 88. The piston cup 88 `is normally held against the piston 81 by a compression spring 89 which abuts at its other end against the valve washer 90 to normally hold the valve washer against the seat 9| provided on the end of the outlet bushing 11. On the valve washer 90 is carried the spring loaded residual poppet valve 92 having a head 93 with an annular lip 94 engaging the recessed seat surface 95 on the valve Washer 90. A compression spring 96 acting between the Outer face 91 of the washer valve 90 and the collar 98 fixed to the end of the valve stem 99 of the valve 92, serves to normally hold the annular lip 94 against the seat face 95.

Fluid 83 from the reservoir 82 enters the cylinder bore 86 through the gravity passageway |00 when the piston cup is in retracted position as shown in Figures 6 and 7. Leakage past the cup 88 passes through the holes |0| into the chamber |02 around the piston 81 and is returned to the reservoir through the passageway |03. The rear end of the pStOn. 87 S guided in the bore 88 by the flanged portion |04 which also supports the seal |05 to prevent leakage of fluid from the chamber |02. A washer |06 held in place by a snap ring |01 serves as a retracted position limit stop for the piston 81.

The piston 81 is connected through a rod |08 to the pressure collar |09 reciprocatably mounted in a bore ||0 in the bracket fastened to the cylinder portion 85 by suitable screws ||2. A compression spring |3 abuts against the face ||4 of the collar |09 and engages at its other end the face ||5 of the nut ||6 operating on the threaded portion ||1 of the screw ||8. The screw is journaled in the bearing bushing ||9 and held against axial movement by the thrust bearing |20 supported appropriately in the outer end of the housing |2| fixed to the member by suitable screws |22. An operating handwheel |23 is fixed to the outer end of the screw for rotation of the screw ||8 to axially reciprocate the nut ||6 to thereby vary the pressure exerted by the spring ||3 on the piston 81.

As the piston cup 88 moves forward to the right vof the passageway ||0, Figures 6 and 7, pressure is built up in the cylinder bore 86 which is transmitted to the line 16 and the pressure chamber 15 for controlling the operation of the valve plungers 51 and 6|. When the piston is moved to the right, Figures 6 and 7, the valve 92 is opened to allow fluid under pressure to be sent into the pressure chamber 15. When the piston is stationary at the desired setting indicating by the gauge 8|, the residual valve mechanism functions to maintain a several pounds differential between the fluid pressure in chamber 15 and the line 16 relative to the pressure in the cylinder portion 85. This slight excess pressure in chamber 15 and line 16 serves to prevent drainage back into the reservoir and avoids the possibility of cavitation in the system in a manner common to well known hydraulic braking systems for automotive vehicles. The piston cup 88 in the bore provides the sole means for maintaining the overall pressure in the control circuit comprising the line 16 and the pressure chamber 15.

The

ball valves

44 and 48 are thus loaded on one end through the diaphragm 12 by hydraulic oil pressure from the control unit 18. The setting of this unit is determined by the pressure required by any particular number or size of hose outlets being used. The opposite ends of these

ball valves

44 and 48 are loaded through the diaphragm 64 by the water pressure from the discharge manifold |6 from the pump I3. In this manner, oil pressure from the main driving engine oil pump of the pumper is controlled so as to regulate the carburetor setting for the engine to maintain a predetermined desired output pressure for the pump I3.

In starting up the pumper, assume that a pumping pressure of lbs. per square inch is required for the hose lines to be put in operation. By adjusting the handwheel |23 of the control unit 18 to the point where 150 lbs. desired pressure is indicated on the governor pressure gaugev81, a pressure of 150 lbs. per square inch will be provided in the pressure chamber 15 against the diaphragm 12. In view of the fact that the driving engine and the pump |3 have not yet developed this pressure, the inlet ball valve 44 will be held closed against the seat 52 and the discharge ball valve 48 will be held open away from the seat 5,9, as shown Figure 4. This allows .fluid pressurein the pressure chamber 32 of the cylinder .29 to be expelled through the discharge ball valve 4 8 under the action oi the compression Spring .3,3 moving the piston rod 28 and piston to the position 30o up against the stop screw 30o which in turn opens the throttles I9 of Vthe carburetors to increase the speed and power of the engine and increase the discharge ofthe pump 1 3. Asthe pump pressure approaches the desired 1.50 lbs. per square inch, the same pressure developes in the chamber 6l behind the diaphragm 64 so that the discharge ball valve 48 is also closed against the seat 59 and a balanced condition thus results.

With the pump operating under the above bal.- anced condition, assume that one or more discharge outlet l1-I8 are closed and the power requirements correspondingly reduced. closing of these outlets will cause an increased pressure on the discharge of lthe pump which will be correspondingly reflected in the pressure chamber 61 behind the diaphragm 64 which will counteract the pressure established in the p resi sure chamber 'I5 behind the diaphragm 'I2 by the control unit 18, holding the discharge ball valve 48 closed and opening the inlet ball valve 44 as shown in Figure 5. This allows additional fluid to enter the pressure chamber 32 of the cylinder 29 to move the piston 30 against the spring 33, forcing the piston toward a position in which the throttles are closed. This movement continues until once more a balance is obtained between the pressure established by the control unit 18 and the discharge pressure or the pump.

Having thus fully set vforth and described this invention, what is claimed is:

1. In a governor for a nre pump having a main driving engine, a carburetor for controlling Vthe operation of said engine, a water Dump driven from said engine, and an oil pump for and driven by said engine, a fluid pressure actuator connected to regulate said carburetor, a control valve mechanism connected in series between said actuator and ,said oil pump, means for actuating said valve mechanism solely from the output pressure of said water pump to regulate duid pressure ilow from said oil pump to said fluid pressure actuator, and further manually controlled means connected to actuate said valve mechanism in opposition to the actuation of the valve mechanism by the output pressure of the water pump so as to regulate said fluid pressure actuator for said carburetor to maintain a predetermined output pressure for said water pump.

2. In a governor for a re pump having a main driving engine, a carburetor for controlling the operation of said engine, a Water pump driven from said engine, and an oil pump for and driven by said engine, a fluid pressure actuator connected to regulate said carburetor, a control valve mechanism connected in series between said actuator and said oil pump, means for actuating said valve mechanism solely from the output pressure of said Water pump to regulate fluid pressure flow from said oil pump to said fluid pressure actuator, and further manually controlled means connected to actuate said valve mechanism in opposition to the actuation of the valve mechanism by the output pressure of thewater pump so as to regulate said uid pressure actuator for said carburetor to maintain a predetermined output pressure for said water pump, said further means including a manually ad- The,

instable pressure @control unit for .maintaining a preselected opposing pressure on said control valve mechanism tothe pressure from the outuut of said water pump.

3,. a nre engine, a .main driving engine. a hydraulically actuated engine speed regulator including, a `source of fluid pressure driven lfrom said engine, a .liydraulic Amotor operable to control the speed of said engine, a control valve connected between said source of fluid pressure and said hydraulic motor, .a water `pump driven from said engine, means for ,actuating said control valve solely Vfrom the output pressure of said water pump so as 'to regulate fluid pressure flow .from said source of vkfluid pressure to said hydraulic motor, and a preselectable manually operated pressure ,control unit connected to said control valve to apply pressure to actuate said valve in opposition to the actuating pressure from the output of said water pump.

'f1- `1n .a governor `control system for a nre engine pump, a control -valve mechanism having an inlet valve., and a discharge valve, a source 4oi fluid pressure connected to said valves, a fluid Pressure actuating cylinder connected to both of said valves, means for mechanically connecting said cylinder to regulate the speed of the driving engine,y means for connecting iluid pressure solely from the output of the pump to simultaneously actuate both o f said valves so as to open said inlet valve and -close said outlet valve to regulate flow from said source of uid pressure to said cylinder, and a manually operated Dreselectable pressure control unit connected to simultaneously Vapply pressure to both of said valves in .opposition to the pressure from the output Aof said pump so as to close said inlet valve and open said voutlet valve for regulation of the application of said source o f fluid pressure to said cylinder.

5. In a goyernor control system for a fire engine pumper having, a main driving engine, a carburetor for regulating the speed of said engine, a lubricating pump driven from said engine, and a water pump driven from said engine, an actuating cylinder having a reciprocatable Piston connected to regulate said carburetor, resilient means for normally actuating said piston in a direction to control said carburetor to increase ,the speed of said engine, -a fluid pressurechamber in said .cylinder behind said piston .eiTectiv-e when pressure is applied thereto to move said piston to .control said .carburetor to decrease the speed of said engine, a control valve means serially interconnected between said lun bricating pump and .said chamber operable to control the application of fluid pressure to the said .chamber in said cylinder, a manually operated adjustable pressure control unit arranged to ,actuelle said valve means, and means connected to said valve means and said water pump to simultaneously actuate said Valve means from the output pressure of said water pump and in opposition to the pressure applied from lsaid manually operated adjustable pressure control unit.

6. In a governor control system for a fire engine pumper having, a, main driving engine, a carburetor for regulating the speed of said engine, a lubricating pump driven from said engine, and a Water pump driven from said engine, an actuating cylinder having a reciprocatable piston connected to regulate said carburetor, resilient means for normally actuating said piston in a direction to control said carburetor to increase the speed of said engine, a fluid pressure chamber in said cylinder behind said piston effective when pressure is applied thereto to move said piston to control said carburetor to decrease the speed of said engine, a control valve means interconnected between said lubricating pump and said cylinder operable to control the application of :duid pressure to the pressure chamber in said cylinder, a manually adjustable pressure control unit, and means for controlling said valve means simultaneously from the output pressure of said water pump and pressure applied from said manually adjustable pressure control unit, said last mentioned means comprising a diaphragm engaging one side of said control valve means, a pressure chamber behind said diaphragm, conduit means connecting output water pressure from said water pump into said pressure chamber, a second resilient diaphragm engaging said control valve means in opposed relationship to said rst mentioned diaphragm, a second pressure chamber behind said second diaphragm, and conduit means connecting said second pressure chamber to said pressure control unit.

7. In a governor control system for a fire engine pumper having, a main driving engine, a carburetor for regulating the speed of said engine, a lubricating pump driven from said engine, and a Water pump driven from said engine, an actuating cylinder having a reciprocatable piston connected to regulate said carburetor, resilient means for normally actuatingl said piston in a direction to control said carburetor' to increase the speed of said engine, a fluid pressure chamber in said cylinder behind said piston effective when pressure is applied thereto to move said piston to control said carburetor to decrease the speed of said engine, a control valve means interconnected between said lubricating pump and said cylinder operable to control the application of fluid pressure to the pressure chamber in said cylinder, a manually adjustable pressure control unit, and means for controlling said valve means simultaneously from the output pressure of said water pump and pressure applied from said manually adjustable pressure control unit, said last mentioned means comprising a diaphragm engaging one side of said control valve means, a pressure chamber behind said diaphragm, conduit means connecting output water pressure from said water pump into said pressure chamber, a second resilient diaphragm engaging said control valve means in opposed relationship to said rst mentioned diaphragm, a second pressure chamber behind said second diaphragm, and conduit means connecting said second pressure chamber to said pressure control unit, said pressure control unit comprising a fluid reservoir, a cylinder arranged to receive a supply of fluid from said reservoir', and manually actuable means for moving said piston to set up a predetermined static pressure in said cylinder and said second pressure chamber.

8. In a control valve mechanism for a fire engine pump governor, a valve body, an inlet ball valve, an outlet ball valve, a source of oil pressure connected to said inlet valve, a fluid pressure control cylinder interconnected between said valves, and a discharge conduit connected to said outlet valve, a rst set of plungers slidable in said valve body and engaging one side of each of said ball valves, a resilient diaphragm positioned against the ends of each of said plungers, and a pressure chamber cover' secured to said valve body over said diaphragm, and means connecting water pressure from the output of the fire engine pump into said pressure chamber', a second set of plungers slidable in said valve body engaging the ball valves in opposed relation to said rst set of plungers, a resilient diaphragm positioned against the ends of `said second set of plungers, a second pressure chamber cover secured to said valve body over said second diaphragm, and means maintaining a static source of predetermined fluid pressure in the second pressure chamber.

9. In a control valve mechanism for a fire engine pump governor, a valve body, an inlet ball valve, an outlet bail valve, a source of oil pressure connected to said inlet valve, a fluid pressure control cylinder interconnected between said valves, and a discharge conduit connected to said outlet valve, a first set of plungers slidable in said valve body and engaging one side of each of said ball valves, a resilient diaphragm positioned against the ends of each of said plungers, and a. pressure chamber cover secured to said valve body over said diaphragm, and means connecting water pressure from the output of the lire engine pump into said pressure chamber', a

second set of plungers `slidable in said valve body engaging the ball valves in opposed relation to said first set of plungers, a resilient diaphragm positioned against the ends of said second set of plungers, a second pressure chamber cover secured to said valve body over said second diaphragm, and means maintaining a static source of predetermined fluid pressure in the second pressure chamber, a fluid resistance interconnected between said inlet ball valve and said output Water pressure from said fire engine pump, and a second fluid resistance interconnected between said discharge ball valve and said discharge conduit.

RICHARD CUR'I' NEPPER.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 859,327 McMullen July 9, 1907 1,093,585 Hoffman Apr. la, 1914 1,834,333 Church Dec. 1, 1931