US3700360A - Double-acting tandem piston pump - Google Patents

Double-acting tandem piston pump Download PDF

Info

Publication number
US3700360A
US3700360A US3700360DA US3700360A US 3700360 A US3700360 A US 3700360A US 3700360D A US3700360D A US 3700360DA US 3700360 A US3700360 A US 3700360A
Authority
US
Grant status
Grant
Patent type
Prior art keywords
piston
cylinder
end
rod
control rod
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
Inventor
Roland E Shaddock
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.)
Myers-Sherman Co
Original Assignee
Myers-Sherman Co
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
Grant date

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162Adaptations of cylinders
    • F04B53/164Stoffing boxes
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L25/00Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
    • F01L25/02Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means
    • F01L25/04Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means by working-fluid of machine or engine, e.g. free-piston machine
    • F01L25/06Arrangements with main and auxiliary valves, at least one of them being fluid-driven
    • F01L25/063Arrangements with main and auxiliary valves, at least one of them being fluid-driven the auxiliary valve being actuated by the working motor-piston or piston-rod
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L25/00Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
    • F01L25/08Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by electric or magnetic means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/111Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
    • F04B9/113Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by a double-acting liquid motor

Abstract

A high pressure tandem piston pump reciprocated by pressured oil from a vehicle engine driven hydraulic pump to surge water at high pressure from a vehicle tank or other source through a hose and nozzle to create a jumping action or jack hammer driving of the nozzle forcing it through and around obstructions in a sewer pipe. The engine driven pump pumps oil to opposite sides of one of the pistons of the tandem pump causing it to reciprocate the piston for high pressure surging delivery of water. Oil flow to opposite sides of the driving piston to is controlled from a valve tripped by a switch which is actuated by a control rod slidable in a recess of the connecting rod between the two pistons of the tandem pump and arranged to be pushed to a switch tripping position at one end of the stroke of the pump admitting high pressure oil which further ejects the control rod and holds it in an extended position until pulled to a retracted locked position at the opposite end of the stroke of the pump permitting the switch to again be tripped for reversing the flow from the engine driven pump.

Description

United States Patent Shaddock 51 Oct. 24, 1972 [54] DOUBLE-ACTING TANDEM PISTON PUMP Primary Examiner-Robert M. Walker 72] Inventor: Roland E. Shaddock, Streator, m. Ammey-Cam [73] Assignee: Myers-Sherman Company, Streator, [57] ABSTRACT A high pressure tandem piston pump reciprocated by [22] Filed: Aug. 23, 1971 pressured oil from a vehicle engine driven hydraulic pump to surge water at high pressure from a vehicle Appl' tank or other source through a hose and noule to R A can i create a jumping action or jack hammer driving of the elated pp n Dam nozzle forcing it through and around obstructions in a [62] Division of Set. N0. 857,424, Sept. 12, 1969, sewer pipe, The engine driven pump pumps oi] t p- Pat. No. 3,658,589. posite sides of one of the pistons of the tandem pump causing it to reciprocate the piston for high pressure [52] US. Cl. .Al7l404, 417/390, 91/275 surging delivery of water. Oil flow to opposite sides of [51] int. Cl.......F04b 9/08, F04b 17/00, F04b 35/00, the driving piston to is controlled from a valve tripped Foll 25/08 by a switch which is actuated by a control rod slidable [5s] Fieldolsearch ........417/390, 404;91/27s, 313, in a recess of the wnnectins rod between the two 334 pistons of the tandem pump and arranged to be pushed to a switch tripping position at one end of the [56] New and stroke of the pump admitting high pressure oil which further ejects the control rod and holds it in an ex- UNITED STATES PATENTS tended position until pulled to a retracted locked posi- 2,087,713 7/1937 Whiteside et al. .....417/404 x 9". 9 9 the 9" 'P 2 854 826 [0/1958 Johnston 417/404 mlttmg the switch to again be tripped for reversmg the n f th d I 2,726,490 12/1955 Lowe ..91/275 x W mm e engme Pump 2,842,108 7/1958 Sanders ..l23/ 102 7 Claims, 3 Drawing Figures TANK PATENTEDum 24 1912 SHEU 1 [1F 2 1 DOUBLE-ACTING TANDEM PISTON PUMP RELATED APPLICATION This application is a division of my application entitled Catch Basin and Sewer Pipe Cleaner," U.S. Ser. No. 857,424 filed Sept. 12, 1969, now US. Pat. No. 3,658,589, granted Apr. 25, I972.

BRIEF SUMMARY OF THE INVENTION In my aforesaid parent application, there is described and claimed a single vehicle for vacuum cleaning of catch basins and flushing of sewer pipes with water surged through a hose and nozzle at pressures of about 2,000 to 3,000 pounds per square inch causingthe hose to jump and move the nozzle for seeking its way around and through obstructions in a sewer pipe or the like in the manner of a jack hammer. The present invention now relates to the double-acting tandem piston pump disclosed in my parent application for producing the high pressure surging of water through the hose and nozzle.

The tandem piston pump of this invention is mounted on the single vehicle disclosed in my parent application and has a first piston reciprocated by pressurized oil from a hydraulic pump conveniently driven through a conventional power take-off from the vehicle engine. This first piston reciprocates a second piston to surge water from the vehicle tank through a hose which is reeled on the front of the vehicle and carries a self propelling nozzle on its leading end.

The tandem piston water pump of this invention forces water through the hose at pressures of 2,000 to 3,000 pounds per square inch, but as the pumping piston reaches the end of its stroke and is reversed, there is a momentary lull in the water flow creating a pulsing action which causes the hose to jump and moves the nozzle to seek its way around and through obstructions in the manner of a jack hammer.

Since the tandem piston pump is hydraulically driven, it can be conveniently located anywhere on the vehicle close to or remote from an engine driven oil pump and driven at any rate controlled by the pressure of the hydraulic fluid.

In its preferred embodiment, the double-acting tandem piston pump of this invention has a central body portion with cylinders of the same or different diameters extending from both sides thereof. A piston rod extends through the central body into both cylinders and piston heads are secured on the ends of the rod. One of the pistons is actuated by oil from the engine driven pump to drive the other piston for surging the water at high pressure. A feature of the invention includes a control rod slidable in a recess in the piston rod and extending through the head of the oil cylinder to trip a switch controlling a valve which controls oil flow to and from the opposite ends of the oil cylinder. This control rod is pushed to a switch tripping position by the piston rod and is ejected to a further extended position by the oil pressure introduced into the end of the cylinder for reversing the piston stroke. Then when the oil piston reaches the end of its stroke remote from the cylinder head, the control rod is pulled from its extended position to a locked retracted position permitting the switch to return to an initial position for reversing the oil flow control valve. The control rod thus only has a short stroke being moved only when the oil piston ap proaches the ends of its stroke.

It is then an object of this invention to provide a tandem pump having a driving piston actuated hydraulically from a rotary pump and a driven piston delivering high pressure water at surging flow rates.

A further object of this invention is to provide a douhie-acting tandem piston pump with a driving piston in a first cylinder of a selected size and a driven piston in a second cylinder of selected size connected by a common piston rod which trips a control rod to effect reversal of the stroke of the pistons.

A further object of the invention is to provide a double-acting piston pump with a common central body, cylinders of selected sizes on opposite sides of the body, pistons slidable in the cylinders connected by a common piston rod extending through the body, and a control rod actuated from the piston rod for effecting reversal of flow of pressurized fluid to opposite sides of the driving piston which control rod is urged by driving fluid pressure on one side of the piston to an extended position and pulled to a retracted locked position by the piston rod.

A still further object of the invention is to provide an oil trap protecting the control rod against impact when driven to its extended position.

Other and further objects of this invention will be apparent to those skilled in this art from the following description of the annexed sheets of drawings showing a preferred embodiment of the invention.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a diagrammatic view of the water and oil circuits for the tandem pump which is illustrated in longitudinal cross-section;

FIG. 2 is a broken longitudinal cross-sectional view of the tandem piston pump of this invention;

FIG. 3 is a view similar to FIG. 2 but on a section line 90 therefrom and showing the pistons at the opposite ends of their stroke.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT The tandem pump of this invention is conveniently mounted on the catch basin and sewer pipe cleaning vehicle disclosed in my aforesaid parent application, Ser. No. 857,424, and receives water from a tank diagrammatically illustrated at 12 in FIG. 1 to surge the water through a hose diagrammatically illustrated at 28 with a high pressure self-propelling spray nozzle 29 on its front end and having a hollow head 30 with rearwardly opening orifices.

This pump 60 has a central cylindrical body 61 with a first cylinder 62 extending from one side thereof and a second cylinder 63 extending from the other side thereof. These cylinders can be of the same or different diameters for a purpose to be more fully hereinafter described.

The cylinder 62 has an end head 64 thereon. The cylinder 63 has an end head 65 thereon.

As best shown in FIGS. 2 and 3, a piston rod 66 extends through the central body 61 into both the cylinders 62 and 63. A first piston head 67 is secured to an end of the piston rod 66 in the cylinder 62, and a second piston head 68 is secured to the opposite end of the rod in the cylinder 63. Piston rings 69 are carried in grooves in the piston 67 and sealingly engage the cylinder wall 62. Similar piston rings 70 are carried in grooves in the piston 68 and engage the cylinder wall 63. These piston rings include a plastic ring body with a groove in the end wall thereof facing the cylinder chamber receiving an O-ring which sealingly connects the end face of the ring with the piston ring groove and which causes an expansion of the ring body against the cylinder wall under the influence of pressure in the cylinder.

In the illustrated form of the pump 60 the piston 67 is the driving piston and is actuated by oil under pressure from an engine-driven hydraulic pump. Oil is selectively circulated to and from opposite faces of the piston 67 through a first port 71 in the central body 61 and a second port 72 in the end head 64. The piston 68 is the water pumping piston, and the cylinder 63 receives water into the opposite ends thereof from a common manifold 73 through a port 74 in the central body 61 and a port 75 in the end head 65. Water pumped by the piston 68 is discharged from opposite ends of the cylinder 63 into a common outlet 76 from a first port 77 in the central body 61 and a second port 78 in the end head 65.

Packings 79 and 80 in the central body 61 sealingly engage the piston rod 66 to prevent leakage between the oil and water sides of the pump.

As shown in FIG. 1, the inlet manifold 73 for the water side of the pump receives water from the supply tank 12 of the vehicle through a conduit 81 and the water is discharged through the manifold 76 and hose 28 to the nozzle 29.

Check valves 82 are provided in each of the ports 74, 75, 77 and 78. These valves are spring-loaded to closed positions, and are arranged in the ports so that the valve 82 in the port 74 will be closed as the piston is moved to the left-hand end of its stroke, while the valve in the port 77 will be open to discharge the water being pumped into the manifold 76. At the same time the valve in the port 75 will be opened to admit water to the right-hand side of the piston 68, while the valve in the port 78 will be closed. The valves are operated by pressure differentials, with the water inlet valves opening on the suction stroke, closing on the pressure stroke, and with the outlet valves closing on the suction stroke and opening on the pressure stroke. These valves, therefore, alternately admit water from the supply tank to opposite sides of the piston and alternately discharge the water on the pressure stroke of the piston, with one inlet valve being opened on one side of the piston and one discharge valve being opened on the opposite side of the piston at the same time, while the other two valves are closed.

The driving piston 67 alternately receives oil on opposite sides thereof through the ports 71 and 72, which act both as inlet and outlet ports.

As shown in FIG. 1, oil from a tank 83 on the vehicle is fed through an intake tube 84 to the inlet side of an engine-driven oil pump 85. This pump discharges through a tube 86 into a four-port spring-centered spool valve diagrammatically illustrated at 87. This valve 87 is hydraulically actuated from a solenoid operated pilot valve 88. The solenoid valve 88 is controlled from a master switch 89 supplying actuating current to a reversing micro-switch 90 having one pole 91 actuating a solenoid 92 on one side of the valve spool in the pilot valve 88 and a second pole 93 actuating a second solenoid 94 on the opposite side of the spool valve.

Oil from the tube 86 passes through the valve 87 to a tube 95, discharging to a pressure regulating valve 96 which dumps into a return tube 97 back to the tank 83. The valve 96 maintains a predetermined pressure differential between the tubes 95 and 97.

The spool in the valve 87 is shifted by oil under pressure from chambers 98 and 99 at opposite ends of the spool. These chambers selectively receive oil at the pressure maintained by the valve 96 under the control of the pilot valve 88. This pilot valve 88 has an inlet oil tube 100 in the oil line 95 ahead of the valve 96 and an outlet oil tube 101 downstream of the valve 96 so that the pilot valve only receives oil under the pressure maintained by the valve 96. This oil is selectively fed under control of the pilot valve 88 through a tube 102 to the chamber 98 and through a tube 103 to the chamber 99. With the leaf a of the microswitch in the position shown in FIG. 1, current flows through the wire 91 to energize the solenoid 92, thus shifting the spool in the valve 88 so that oil from the tube 100 will flow to the tube 102 and chamber 98 for forcing the spool in the valve 87 to the right. At the same time oil in the chamber 99 will be drained back through the tube 103, through the valve 88 to the return line 101 back to the tank through the tube 97 The valve 87, when shifted by oil under pressure from the chamber 98, will communicate the pump pressure tube 86 to the port 72, while at the same time opening the port 71 to the tube and through the pressure valve 96 back to the tank 83. Oil under the full pressure of the pump 85 will thereby be introduced to the left-hand side of the cylinder 62, forcing the piston 67 to the right. When the piston reaches the right-hand end of its stroke, as shown in FIG. 3, the leaf 90a of the micro-switch 90 returns to its opposite pole and energizes the line 93, which activates the solenoid 94 and reverses the pilot valve 88 so that oil from the pressure line will flow to the line 103 and to the chamber 99, while oil from the chamber 98 will flow through the tube 102 into the line 101 back to the tank. The valve 87 will thereupon be shifted so that oil is fed under pressure to the port 71 and drained from the port 72.

The micro-switch activating means is shown in FIGS. 2 and 3, and includes a control rod 104 freely mounted in an axial recess 105 in the left-hand end of the piston rod 66. The rod 104 slides freely through a cap 106 which is threaded in the end of the piston rod 66 and is adapted to allow high pressure oil from the port 72 to flow into the recess 105. The rod 104 has a head 107 on its inner end adapted to bottom at opposite ends of the piston rod stroke respectively on the cap 106 and on the end wall 1050 of the recess 105. A reduced diameter integral rod portion 108 slides through a gland 109 in the end head 64 and provides a shoulder 110 in which port 72. The gland 109 has a recess 111 exposed to the port 72 and confronting the shoulder 1 10.

The reduced diameter portion 108 of the control rod 104 projects beyond the end head 64 and has an enlarged head 112 thereon slidably mounted in an openended cylinder 113 which is secured to the outer face of the end head 64. In the position illustrated in FIG. 2 the end wall 105a of the recess has just pushed the control rod 104 to move this head 112 to its extended posimmm tion projecting beyond the cylinder 113. In this extended position the head 112 has tripped the switch leaf 90a, admitting oil to the port 72, thus starting the piston on its stroke to the right. Since the head end 107 of the rod 104 is exposed to the high pressure in this port 72 while the other head end 112 of the rod 104 is exposed to the atmosphere, the rod 104 is driven further outwardly, moving the shoulder 110 into the recess 11], where trapped oil in this recess will prevent the shoulder from impacting against the gland 109. The rod will remain in its extended position, with its head 112 against the switch leaf 900 until the cap 106 engages the head 107 at the inboard end of the piston stroke, as shown in FIG. 3. Then the head 112 of the control rod 104 will be pulled into the cylinder 113 to a position where a peripheral grove 114 in the head is aligned with spring-loaded ball-bearings 115 carried by the cylinder. These spring-loaded ball bearings or detents will snap into this groove 114 for holding the control rod 104 in a retracted inward position, as shown in FIG. 3.

In the position of FIG. 3 the head 112 has been withdrawn into the cylinder 113 sufficiently to allow the spring-loaded leaf 90a of the micro-switch to move to the right and change the pole position of the switch. The control rod will remain in the position of FIG. 3, held by the detents 115 until it is again pushed by the recessed end wall 150a, returning the rod to the position of FIG. 2 for the next stroke.

In the position of FIG. 8, fluid is just beginning to enter the port 71 to start the piston on its stroke to the left.

In the position of the leaf 900, shown in FIGS. I and 2, the solenoid-actuated pilot valve 88 feeds oil under the differential pressure maintained across the valve 96 to position the main valve 87 so that oil will flow into the port 72 and out of the port 71. This, of course, will drive the piston 67 to the right-hand end of the cylinder 62, whereupon, as shown in FIG. 3, the cap 106 will engage the control rod head 107, retracting the head 112 into the cylinder 113 to a position where it is retained by the spring pressed detents 115. Of course, upon reversal of the pole position of the micro-switch to the position of FIG. 3, the pilot valve 88 will again be energized to reverse the main valve 87 and introduce pressurized oil into the port 71 and out of the port 72, thereby moving the piston 67 to the left.

It will be appreciated that while the stroke of the piston rod 66 may be quite long, the control rod 104 is only shifted a short distance, just sufficient to throw the leaf 90a of the micro-switch 90 between its poles. Thus, when the piston rod 66 moves to the right from the position of FIG. 2, the rod 104 will remain stationary, being retained in its extended position by oil pressure in the port 72. Then when the piston rod 66 moves to the inboard end of its stroke, as shown in FIG. 3, the head 107 will be engaged by the cap 106, pulling the rod 104 therewith only until the head 112 is moved into the cylinder 113 sufficiently to align the groove 114 with the spring-pressed detents 115. For example, the control rod 104 may only be shifted 1 inch or so in installations where the piston rod 66 is shifted 15 inches or more.

As illustrated, the cylinders 62 and 63 are of the same diameter, but if it is desired to increase the flow capacity of the water pump, the cylinder 63 and piston 68 can be of a larger diameter than the cylinder 62 and piston 67. Conversely, if it is desired to obtain a higher maximum water pressure, the cylinder 62 and piston 67 can be larger than the cylinder 63 and piston 68.

From the above descriptions of the pump 60 it will be understood that the engine-driven oil pump operates through a pilot valve and a main valve to alternately deliver pressurized oil into the opposite ends of the cylinder 62. When oil is delivered into one end of the cylinder 62, it is simultaneously drained from the other end of the cylinder 62. This, of course, reciprocates the piston 67 which, in turn, drives the piston 68. Water is supplied from the tank 12 altemately to opposite sides of the piston 68, and when one side of the piston is on the intake stroke, the other side is on the pressure stroke, and the water is delivered under pressure to the hose 28. Very high pressures may be developed in the chamber of the oil cylinder 62 to deliver water under very high pressures. These high pressures will be maintained, although there is a momentary lull or dwell in the water flow as the pistons reverse their stroke. As a result, the water is delivered to the hose at a high pressure, but at a flow rate which drops rapidly at the end of the stroke and then picks up very rapidly. This causes the hose 28 to jump, and effects the jack-hammer driving of the nozzle 29.

I claim as my invention:

1. A tandem pump which comprises a central body, a cylinder of selected diameter mounted on and extending axially from each side of said body, a piston head in each cylinder in sealed relation therewith, a piston rod slidably mounted in said body having its ends secured to the pistons in said cylinders, inlet ports at both ends of one cylinder, separate outlet ports at both ends of said one cylinder, valves in said inlet and outlet ports admitting fluid to the cylinder on the suction stroke of the piston and discharging said fluid on the opposite side of the piston, combination inlet and outlet ports on the opposite ends of the other cylinder, means for selectively introducing fluid under pressure into one of said combination ports to reciprocate the piston in the cylinder between the ports, a control rod means controlled from the piston rod for controlling the flow of the pressured fluid to and from the combination ports whereby reciprocation of the piston by the pressurized fluid will reciprocate the piston in said one cylinder to alternately surge fluid through one and then the other of said outlet ports, mechanical means holding said control rod in a retracted fixed position during one stroke of the piston between the combination ports, and fluid pressure actuated means holding the control rod in an extended fixed position during the opposite stroke of said piston.

2. The pump of claim 1 wherein said means reversing flow through the combination inlet and outlet ports includes a solenoid actuated pilot valve tripped at the ends of the stroke of the piston rod and a high pressure oil valve actuated by the solenoid valve for controlling flow to and from said combination ports.

3. A tandem piston pump effective to surge water through a hose and self-propelling nozzle on the leading end of the hose to cause the hose and nozzle to jump at periodic intervals which comprises a central body, first and second cylinders of selected diameters each secured to an opposite side of said central body and extending coaxially therefrom, end heads on the outer ends of said cylinders, a piston rod slidably mounted in the central body and extending into both cylinders, pistons slidably mounted in the cylinders secured on the ends of the piston rod, a water inlet port in said body communicating with the inner end of the first cylinder, a water inlet port in the end head of said first cylinder communicating with the outer end of said first cylinder, a water outlet port in said body communicating with the inner end of said first cylinder, a water outlet port in said end head of said first cylinder communicating with the outer end of said first cylinder, valves in each of said inlet ports opening on the suction stroke of the piston in said first cylinder, valves in said outlet poi-ts opening on the pressure stroke of the piston in said first cylinder, a combination inlet and outlet port in said central body communicating with the inner end of said second cylinder, a combination inlet and outlet port in the end head on said second cylinder communicating with the outer end of said second cylinder, a pump delivering oil under pressure to and receiving oil from said combination ports, a control rod controlled by said piston rod reversing oil flow through said combination ports to opposite sides of the piston in said second cylinder for reciprocating the piston to drive the piston in said first cylinder for surging water alternately through said outlet ports, mechanical means holding said control rod in one fixed position during one stroke of the piston in the second cylinder, and oil pressure actuated means holding said control rod in a second fixed position during the opposite stroke of said piston in the second cylinder.

4. The pump of claim 3 wherein the means for reversing flow through the combination ports includes an oil actuated spool control valve selectively venting oil to said combination ports and a solenoid actuated pilot valve tripped by the piston rod controlling the oil actuated spool valve.

5. A pump having a pair of opposed cylinders, a piston rod projecting into both cylinders, piston heads on the ends of said rod, means for introducing fluid under pressure alternately into the opposite ends of one cylinder for reciprocating the piston therein to drive the piston rod for reciprocating the piston in the other cylinder, said means including an axial recess extending inwardly from the end of the piston rod in the cylinder receiving the fluid under pressure, a cap on said recess, a control rod in said recess having a first head engaged by the piston rod at one end of its stroke and by the cap at the other end of its stroke, an end head on the cylinder receiving the fluid under pressure, a reduced diameter portion on said control rod sliding through said end head in sealed relation therewith, a second head on the reduced diameter control rod portion beyond the end head of the cylinder, a supplemental cylinder receiving said second end head in slidable re lation, a groove in said second head, spring-pressed detents in said supplemental cylinder engaging in said groove to hold the control rod in retracted position, a switch engaged by the control rod in the extended position thereof, and said control rod being reciprocated at the ends of the stroke of the piston rod to trip said switch whereby the detents will hold the control rod in stationary position between the ends of the piston rod 6. 'fhe pump of claim 5 wherein the sea] for the control rod in the cylinder end head has a fluid trapping recess and the control rod has a shoulder bottoming against fluid trapped in said recess to cushion the outward driving of the rod through the end head.

7. In combination with a cylinder having an end head on one end thereof, a body at the opposite end thereof, a piston rod slidable through said body, and a piston on the piston rod in said cylinder, the improvement of a control device for regulating flow of oil under pressure into opposite ends of the cylinder for reciprocating the piston which comprises said piston rod having an axial recess communicating with the end head end of the cylinder, a control rod having one end freely movable in said recess and the other end slidable through said end head in sealed relation therewith, said control rod having opposed shoulders respectively outside of said end head and inside of said end head limiting sliding movement of the control rod through the end head, said control rod being pushed by fluid under pressure in the end head end of the cylinder to an extended position, means on the piston rod pulling the control rod to a retracted position, means on the end head holding the control rod in said retracted position whereby the rod is locked in fixed position except at the very ends of the stroke of the piston, and switch means tripped by the end of the control rod each time it is shifted by the piston rod.

l l l UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION ()ctober 24, 1972 Patent No.

a, 700, 360 Dated Inventor(s) Roland E. ShaddOCk It is certified that error appears in the above-identified patent and that said Letters Patent are hereby corrected as shown below:

Column 4, line 55, cancel "which" and insert --the--.

Column 5, line 16, cancel "grove" and insert --groove--;

line 28, cancel "150a" and insert --l05a--.

Signed and sealed this 16th day of July 1971+.

(SEAL) Attest:

McCOY M. GIBSON, JR. Attesting Officer C. MARSHALL DANN Commissioner of Patents FORM PO-lDSO (10-69) USCOMM DC owe-P69 n u s oovrnunzm PRINTING orncr: Inn 0-!6l-33l

Claims (7)

1. A tandem pump which comprises a central body, a cylinder of selected diameter mounted on and extending axially from each side of said body, a piston head in each cylinder in sealed relation therewith, a piston rod slidably mounted in said body having its ends secured to the pistons in said cylinders, inlet ports at both ends of one cylinder, separate outlet ports at both ends of said one cylinder, valves in said inlet and outlet ports admitting fluid to the cylinder on the suction stroke of the piston and discharging said fluid on the opposite side of the piston, combination inlet and outlet ports on the opposite ends of the other cylinder, means for selectively introducing fluid under pressure into one of said combination ports to reciprocate the piston in the cylinder between the ports, a control rod means controlled from the piston rod for controlling the flow of the pressured fluid to and from the combination ports whereby reciprocation of the piston by the pressurized fluid will reciprocate the piston in said one cylinder to alternately surge fluid through one and then the other of said outlet ports, mechanical means holding said control rod in a retracted fixed position during one stroke of the piston between the combination ports, and fluid pressure actuated means holding the control rod in an extended fixed position during the opposite stroke of said piston.
2. The pump of claim 1 wherein said means reversing flow through the combination inlet and outlet ports includes a solenoid actuated pilot valve tripped at the ends of the stroke of the piston rod and a high pressure oil valve actuated by the solenoid valve for controlling flow to and from said combination ports.
3. A tandem piston pump effective to surge water through a hose and self-propelling nozzle on the leading end of the hose to cause the hose and nozzle to jump at periodic intervals which comprises a central body, first and second cylinders of selected diameters each secured to an opposite side of said central body and extending coaxially therefrom, end heads on the outer ends of said cylinders, a piston rod slidably mounted in the central body and extending into both cylinders, pistons slidably mounted in the cylinders secured on the ends of the piston rod, a water inlet port in said body communicating with the inner end of the first cylinder, a water inlet port in the end head of said first cylinder communicating with the outer end of said first cylinder, a water outlet port in said body communicating with the inner end of said first cylinder, a water outlet port in said end head of said first cylinder communicating with the outer end of said first cylinder, valves in each of said inlet ports opening on the suction stroke of the piston in said first cylinder, valves in said outlet ports opening on the pressure stroke of the piston in said first cylinder, a combination inlet and outlet port in said central body communicating with the inner end of said second cylinder, a combination inlet and outlet port in the end head on said second cylinder communicating with the outer end of said second cylinder, a pump delivering oil under pressure to and receiving oil from said combination ports, a control rod controlled by said piston rod reversing oil flow through said combination ports to opposite sides of the piston in said second cylinder for reciprocating the piston to drive the piston in said first cylinder for surging water alternately through said outlet ports, mechanical means holding said control rod in one fixed position during one stroke of the piston in the second cylinder, and oil pressure actuated means holding said control rod in a second fixed position during the opposite stroke of said piston in the second cylinder.
4. The pump of claim 3 wherein the means for reversing flow through the combination ports includes an oil actuated spool control valve selectively venting oil to said combination ports and a solenoid actuated pilot valve tripped by the piston rod controlling The oil actuated spool valve.
5. A pump having a pair of opposed cylinders, a piston rod projecting into both cylinders, piston heads on the ends of said rod, means for introducing fluid under pressure alternately into the opposite ends of one cylinder for reciprocating the piston therein to drive the piston rod for reciprocating the piston in the other cylinder, said means including an axial recess extending inwardly from the end of the piston rod in the cylinder receiving the fluid under pressure, a cap on said recess, a control rod in said recess having a first head engaged by the piston rod at one end of its stroke and by the cap at the other end of its stroke, an end head on the cylinder receiving the fluid under pressure, a reduced diameter portion on said control rod sliding through said end head in sealed relation therewith, a second head on the reduced diameter control rod portion beyond the end head of the cylinder, a supplemental cylinder receiving said second end head in slidable relation, a groove in said second head, spring-pressed detents in said supplemental cylinder engaging in said groove to hold the control rod in retracted position, a switch engaged by the control rod in the extended position thereof, and said control rod being reciprocated at the ends of the stroke of the piston rod to trip said switch whereby the detents will hold the control rod in stationary position between the ends of the piston rod stroke.
6. The pump of claim 5 wherein the seal for the control rod in the cylinder end head has a fluid trapping recess and the control rod has a shoulder bottoming against fluid trapped in said recess to cushion the outward driving of the rod through the end head.
7. In combination with a cylinder having an end head on one end thereof, a body at the opposite end thereof, a piston rod slidable through said body, and a piston on the piston rod in said cylinder, the improvement of a control device for regulating flow of oil under pressure into opposite ends of the cylinder for reciprocating the piston which comprises said piston rod having an axial recess communicating with the end head end of the cylinder, a control rod having one end freely movable in said recess and the other end slidable through said end head in sealed relation therewith, said control rod having opposed shoulders respectively outside of said end head and inside of said end head limiting sliding movement of the control rod through the end head, said control rod being pushed by fluid under pressure in the end head end of the cylinder to an extended position, means on the piston rod pulling the control rod to a retracted position, means on the end head holding the control rod in said retracted position whereby the rod is locked in fixed position except at the very ends of the stroke of the piston, and switch means tripped by the end of the control rod each time it is shifted by the piston rod.
US3700360A 1971-08-23 1971-08-23 Double-acting tandem piston pump Expired - Lifetime US3700360A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US17376771 true 1971-08-23 1971-08-23

Publications (1)

Publication Number Publication Date
US3700360A true US3700360A (en) 1972-10-24

Family

ID=22633402

Family Applications (1)

Application Number Title Priority Date Filing Date
US3700360A Expired - Lifetime US3700360A (en) 1971-08-23 1971-08-23 Double-acting tandem piston pump

Country Status (1)

Country Link
US (1) US3700360A (en)

Cited By (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2214051A1 (en) * 1973-01-12 1974-08-09 Flow Research Inc
US4062639A (en) * 1974-11-06 1977-12-13 The Hotsy Corporation Fluid motor-driven pump using fluid pressure to set position of pilot valve
US4119113A (en) * 1975-02-06 1978-10-10 Extracorporeal Medical Systems, Inc. Double-action proportioning pump
US4242057A (en) * 1979-09-24 1980-12-30 Bender Emil A Tandem long stroke reciprocating mud pump assembly
US4286929A (en) * 1977-03-23 1981-09-01 Rodney T. Heath Dual pressure gas motor, and method of operation
US4545736A (en) * 1982-06-09 1985-10-08 Thomas Willett & Co. Ltd. Apparatus for automatically processing slurry
FR2587765A1 (en) * 1985-09-25 1987-03-27 Bernard Francois High hydraulic power converter with steady output
US4830583A (en) * 1988-03-02 1989-05-16 Sri International Fluid motor-pumping apparatus and system
US4889035A (en) * 1985-07-16 1989-12-26 Thermo Electron Web Systems, Inc. Magnetically actuated valve for cyclically operating piston-cylinder actuator
US5018950A (en) * 1988-03-11 1991-05-28 Reinhart Lawrence W Electrohydraulic method and apparatus
US5092744A (en) * 1990-03-14 1992-03-03 Possis Corporation Intensifier
US5106276A (en) * 1988-03-11 1992-04-21 Reinhart Lawrence W Electrohydraulic method and apparatus
US5348451A (en) * 1989-10-16 1994-09-20 Framo Developments (Uk) Limited Pump apparatus
US6045334A (en) * 1996-03-20 2000-04-04 Hypro Corporation Valve disabler for use in high pressure pipe cleaning applications
US6065945A (en) * 1998-03-03 2000-05-23 Zamzow; Charles W. Hydraulic engine
US6231322B1 (en) * 1996-08-30 2001-05-15 Post-Mix Equipment Ab Method and device for the production of beverages
US6443709B1 (en) 1998-02-23 2002-09-03 Robert L Jackson Oscillating spring valve fluid pumping system
US20040096344A1 (en) * 2002-11-13 2004-05-20 Nuovo Pignone Holding S.P.A. Simplified piston slidable in a cylinder
US6769884B2 (en) * 2000-12-11 2004-08-03 Cory L. Miller Hydraulic drive system for piston pumps
EP1536135A2 (en) 2003-11-26 2005-06-01 Elgin Sweeper A pump
US20060102034A1 (en) * 2003-02-15 2006-05-18 Man Roland Druckmaschinen Ag Washing apparatus for printing and/or coating mechanisms in a processing machine
WO2006124006A2 (en) * 2005-05-20 2006-11-23 Ena Muhendislik Danismanlik Enerji Makina Ve Yelkapan Sanayi Ve Ticaret Ltd. Sti Wind turbine mechanism
US20070073233A1 (en) * 2005-09-28 2007-03-29 Possis Medical, Inc. Thrombectomy catheter deployment system
US20070129679A1 (en) * 2005-12-05 2007-06-07 Possis Medical, Inc. Pneumatic drive unit
WO2008029288A3 (en) * 2006-07-19 2008-10-30 Fluid O Tech Srl Fluid-powered proportioning pump and system for dispensing fluid inluding such a pump
US20110031802A1 (en) * 2008-07-24 2011-02-10 Gladiator Equipment LLC Hoist employing a multiple piston cylinder
US20110238037A1 (en) * 2010-03-19 2011-09-29 Chorng-Fure Robin Hwang Gas-pressured medication delivery device
US20140199182A1 (en) * 2013-01-11 2014-07-17 Super Products Llc Reciprocating water pump
CN104976165A (en) * 2015-06-10 2015-10-14 西南交通大学 Water pressure variable pump
US20160245266A1 (en) * 2015-02-23 2016-08-25 Federal Signal Corporation Piston shifting control system
CN106523335A (en) * 2016-08-25 2017-03-22 湖南莫尔顿智能勘探机器人有限公司 Automatic reversing water pump

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2087713A (en) * 1934-03-29 1937-07-20 American Hydraulic Pump Corp Double acting deep well pump
US2726490A (en) * 1951-10-26 1955-12-13 Crucible Steel Co America Billet grinder
US2842108A (en) * 1955-11-15 1958-07-08 Sanders John Claytor Closed-loop acceleration control system
US2854826A (en) * 1955-01-12 1958-10-07 John Blue Company Inc Method and system for transferring a pressurized normally gaseous liquid

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2087713A (en) * 1934-03-29 1937-07-20 American Hydraulic Pump Corp Double acting deep well pump
US2726490A (en) * 1951-10-26 1955-12-13 Crucible Steel Co America Billet grinder
US2854826A (en) * 1955-01-12 1958-10-07 John Blue Company Inc Method and system for transferring a pressurized normally gaseous liquid
US2842108A (en) * 1955-11-15 1958-07-08 Sanders John Claytor Closed-loop acceleration control system

Cited By (46)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2214051A1 (en) * 1973-01-12 1974-08-09 Flow Research Inc
US4062639A (en) * 1974-11-06 1977-12-13 The Hotsy Corporation Fluid motor-driven pump using fluid pressure to set position of pilot valve
US4119113A (en) * 1975-02-06 1978-10-10 Extracorporeal Medical Systems, Inc. Double-action proportioning pump
US4286929A (en) * 1977-03-23 1981-09-01 Rodney T. Heath Dual pressure gas motor, and method of operation
US4242057A (en) * 1979-09-24 1980-12-30 Bender Emil A Tandem long stroke reciprocating mud pump assembly
US4545736A (en) * 1982-06-09 1985-10-08 Thomas Willett & Co. Ltd. Apparatus for automatically processing slurry
US4889035A (en) * 1985-07-16 1989-12-26 Thermo Electron Web Systems, Inc. Magnetically actuated valve for cyclically operating piston-cylinder actuator
FR2587765A1 (en) * 1985-09-25 1987-03-27 Bernard Francois High hydraulic power converter with steady output
US4830583A (en) * 1988-03-02 1989-05-16 Sri International Fluid motor-pumping apparatus and system
US5018950A (en) * 1988-03-11 1991-05-28 Reinhart Lawrence W Electrohydraulic method and apparatus
US5106276A (en) * 1988-03-11 1992-04-21 Reinhart Lawrence W Electrohydraulic method and apparatus
US5348451A (en) * 1989-10-16 1994-09-20 Framo Developments (Uk) Limited Pump apparatus
US5092744A (en) * 1990-03-14 1992-03-03 Possis Corporation Intensifier
US6045334A (en) * 1996-03-20 2000-04-04 Hypro Corporation Valve disabler for use in high pressure pipe cleaning applications
US6231322B1 (en) * 1996-08-30 2001-05-15 Post-Mix Equipment Ab Method and device for the production of beverages
US6443709B1 (en) 1998-02-23 2002-09-03 Robert L Jackson Oscillating spring valve fluid pumping system
US6065945A (en) * 1998-03-03 2000-05-23 Zamzow; Charles W. Hydraulic engine
US6769884B2 (en) * 2000-12-11 2004-08-03 Cory L. Miller Hydraulic drive system for piston pumps
US20040265145A1 (en) * 2000-12-11 2004-12-30 Miller Cory L Hydraulic spool-piece
US20040096344A1 (en) * 2002-11-13 2004-05-20 Nuovo Pignone Holding S.P.A. Simplified piston slidable in a cylinder
US20060067842A1 (en) * 2002-11-13 2006-03-30 Stefano Meucci Simplified piston slidable in a cylinder
US20060102034A1 (en) * 2003-02-15 2006-05-18 Man Roland Druckmaschinen Ag Washing apparatus for printing and/or coating mechanisms in a processing machine
EP1536135A2 (en) 2003-11-26 2005-06-01 Elgin Sweeper A pump
US20050142012A1 (en) * 2003-11-26 2005-06-30 Elgin Sweeper Rodder pump
WO2006124006A3 (en) * 2005-05-20 2007-05-10 Ena Muhendislik Danismanlik En Wind turbine mechanism
WO2006124006A2 (en) * 2005-05-20 2006-11-23 Ena Muhendislik Danismanlik Enerji Makina Ve Yelkapan Sanayi Ve Ticaret Ltd. Sti Wind turbine mechanism
US9801642B2 (en) 2005-09-28 2017-10-31 Boston Scientific Limited Thrombectomy catheter deployment system
US20070073233A1 (en) * 2005-09-28 2007-03-29 Possis Medical, Inc. Thrombectomy catheter deployment system
US20110208205A1 (en) * 2005-09-28 2011-08-25 Eric Joel Thor Thrombectomy Catheter Deployment System
US8491523B2 (en) 2005-09-28 2013-07-23 Medrad, Inc. Methods of conducting thrombectomy procedures and deploying a thrombectomy catheter
US7935077B2 (en) 2005-09-28 2011-05-03 Medrad, Inc. Thrombectomy catheter deployment system
US9161765B2 (en) 2005-09-28 2015-10-20 Boston Scientific Limited Thrombectomy catheter deployment system
US7842010B2 (en) * 2005-12-05 2010-11-30 Medrad, Inc. Pneumatically-operated thrombectomy catheter deployment system
US20070129679A1 (en) * 2005-12-05 2007-06-07 Possis Medical, Inc. Pneumatic drive unit
WO2008029288A3 (en) * 2006-07-19 2008-10-30 Fluid O Tech Srl Fluid-powered proportioning pump and system for dispensing fluid inluding such a pump
JP2009543981A (en) * 2006-07-19 2009-12-10 フルイド−オー−テック エスアールエル Fluid dispensing system which includes a proportional pump and the pump of the fluid-powered
CN101512104B (en) 2006-07-19 2012-08-22 福力德-O-技术有限责任公司 Fluid-powered proportioning pump for dispensing fluid including pump
US8393686B2 (en) * 2008-07-24 2013-03-12 Gladiator Equipment LLC Hoist employing a multiple piston cylinder
US20110031802A1 (en) * 2008-07-24 2011-02-10 Gladiator Equipment LLC Hoist employing a multiple piston cylinder
US8551071B2 (en) * 2010-03-19 2013-10-08 Halozyme, Inc. Gas-pressured medication delivery device
US20110238037A1 (en) * 2010-03-19 2011-09-29 Chorng-Fure Robin Hwang Gas-pressured medication delivery device
US20140199182A1 (en) * 2013-01-11 2014-07-17 Super Products Llc Reciprocating water pump
US20160245266A1 (en) * 2015-02-23 2016-08-25 Federal Signal Corporation Piston shifting control system
CN104976165A (en) * 2015-06-10 2015-10-14 西南交通大学 Water pressure variable pump
CN104976165B (en) * 2015-06-10 2017-01-25 西南交通大学 One kind of hydraulic variable displacement pump
CN106523335A (en) * 2016-08-25 2017-03-22 湖南莫尔顿智能勘探机器人有限公司 Automatic reversing water pump

Similar Documents

Publication Publication Date Title
US3250226A (en) Hydraulic actuated pumping system
US3433415A (en) Hydraulic systems
US4286929A (en) Dual pressure gas motor, and method of operation
US3307787A (en) Fountain
US3963383A (en) Air driven pump
US5529460A (en) Pressure washer with flow control switch
US4632754A (en) Desalination apparatus
US5232352A (en) Fluid activated double diaphragm pump
US2074618A (en) Pumping system
US2803110A (en) Hydraulic power drive for reciprocating members
US3930756A (en) Metering pulse pump
US3597120A (en) Injector-recirculation pump
US5616009A (en) Mud pump
US4349130A (en) Liquid metering pump
US3963385A (en) Valve assembly for concrete pumps
US5909775A (en) Dual chamber foam pump
US4500267A (en) Mud pump
US4022381A (en) Airless spray apparatus
US3807894A (en) Storm choke apparatus for submergible pumps
US3495544A (en) Hydraulic system
US5513963A (en) Direct action fluid motor and injection pump
US4871302A (en) Apparatus for removing fluid from the ground and method for same
US3937440A (en) Metering pump and combination two-section pinch-off aspirator valve
US2781775A (en) Limited capacity check valve
US4348161A (en) Pressure converting apparatus