US3384029A - Hydraulic pumping apparatus - Google Patents

Hydraulic pumping apparatus Download PDF

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Publication number
US3384029A
US3384029A US495168A US49516865A US3384029A US 3384029 A US3384029 A US 3384029A US 495168 A US495168 A US 495168A US 49516865 A US49516865 A US 49516865A US 3384029 A US3384029 A US 3384029A
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United States
Prior art keywords
outlet
barrel
cylinder
housing
passage
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Expired - Lifetime
Application number
US495168A
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English (en)
Inventor
Robert E Raymond
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.)
YORK FLUID POWER Inc
Hydrokinetics Inc
Original Assignee
Hydrokinetics Inc
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Publication date
Application filed by Hydrokinetics Inc filed Critical Hydrokinetics Inc
Priority to US495168A priority Critical patent/US3384029A/en
Priority to CH1462466A priority patent/CH454626A/de
Priority to DE1653480A priority patent/DE1653480B2/de
Priority to GB45447/66A priority patent/GB1169947A/en
Priority to BE688123D priority patent/BE688123A/xx
Application granted granted Critical
Publication of US3384029A publication Critical patent/US3384029A/en
Assigned to MILL AND MINE SERVICES, INC., A CORP. OF PA reassignment MILL AND MINE SERVICES, INC., A CORP. OF PA ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: SCOVILL INC., A CT CORP.
Assigned to YORK FLUID POWER, INC. reassignment YORK FLUID POWER, INC. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: MILL AND MINE SERVICES, INC.
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons
    • F04B53/125—Reciprocating valves
    • F04B53/126—Ball valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/143—Cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/18—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having self-acting distribution members, i.e. actuated by working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members

Definitions

  • a hydraulic pumping mechanism that includes a housing with two separate outlet ports, an inlet port, and a control inlet port. Within the housing, a pressurized outlet chamber is isolated from an inlet chamber which communicates with the housing inlet port.
  • a cylinder barrel assembly is slideably mounted within the housing and is provided with a plurality of circumferentially spaced cylinders having a cam driven piston disposed in each cylinder.
  • Each cylinder includes two separate cylinder outlets. The first outlet communicates with an outlet manifold formed in the barrel which in turn communicates with one of the housing outlet ports and the second outlet communicates with the outlet chamber that surrounds the barrel which in turn communicates with the other housing outlet port.
  • Each piston includes an intake port which communicates with a passage or cavity formed in the piston which in turn communicates with the interior of the cylnder.
  • a ball-check valve and valve seat assembly is disposed within the piston to permit only the ingress of fluid through the intake port.
  • An annular piston and cylinder are disposed in the housing in force transmitting relationship with the barrel to control the relative displacement of the pistons in the cylinders.
  • the flow through the second outlet varies with the required flow to the load and performs a cooling function as it passes through the outlet chamber in heat transmitting relationship with the barrel.
  • two fixed displacement outlet flows are delivered through each of the separate housing outlets in any proportion desired as determined by the relative axial spacing of the cylinder outlets with respect to the piston stroke.
  • the present invention relates generally to hydraulic machines and in particular to a novel piston type pumping apparatus.
  • the pumping apparatus of the present invention comprises a suitable housing, cylinder means provided with two separate outlets and piston means disposed in the cylinder means and including inlet port means communicating with the cylinder means. Fluid is taken into the cylinder means through the piston inlet means on the suction stroke and then is discharged through the separate cylinder outlets during different portions of the compression stroke thereby providing in essence two pumps in one.
  • the novel pumping apparatus permits two separate outlet flows in which flow from one cylinder outlet may be delivered to a load while the other outlet feeds a second circuit to circulate a cooling flow to cool the pump. This is particularly advantageous in variable displacement operation during high pressure holding periods when the pump is deadheading.
  • the flow in the second circuit provides very efiicient cooling of the first circuit.
  • the novel pumping apparatus of the present invention permits two separate outlet flows from one set of pistons which can function as two distinct fixed displacement pumps.
  • the flow from the separate outlets can be divided in any manner by simple adjustment of the piston stroke relative to the position of the cylinder outlets in the cylinder.
  • the novel pumping apparatus permits one pumping apparatus to function as a low pressure, high volume pump in a conventional high-low pump system. Low pressure is unloaded to one circuit as the high pressure circuit builds up and then the lower pressure circuit circulates to cool the high pressure circuit in the pump.
  • the novel pumping apparatus may incorporate a cylinder barrel cartridge assembly wherein the cylinders, pistons, and valve means are an integral assembly and may be manufactured in a convenient pumping package for use in a variety of housing envelopes for many different applications.
  • a standard size cartridge may be employed to reduce inventory and provide easy access to reduce maintenance costs.
  • the novel pumping apparatus permits in variable displacement operation, one outlet circuit to be controlled for variable flow with the excess flow being delivered to another outlet circuit depending upon the position of the other cylinder outlet relative to the piston stroke at any instant.
  • the novel pumping apparatus may be manufactured and fabricated at relatively low cost due to the simplicity of construction and the lack of relatively close tolerance requirements.
  • an object of the present invention to provide an apparatus of the type described which provides two separate cylinder outlets in conjunction with one set of piston means to permit the one set of pistons to function as two separate pumps.
  • FIG. 1 is a side sectional View of a pumping apparatus constructed in accordance with the present invention, the section being taken along a vertical plane through the centerline of the apparatus;
  • FIG. 2 is a side view of a pumping cartridge assembly constructed in accordance with the present invention, the remainder of the apparatus being shown in section as seen in FIG. 1;
  • FIG. 3 is a side sectional view of a portion of the apparatus shown in MG. 1 illustrating a check valve for the cooling outlet port in the housing, the section being taken along a vertical plane through the centerline of the apparatus;
  • FIG. 4 is a side view of a portion of the valve assembly shown in FIG. 3;
  • FIG. 5 is an end view of that portion of the valve assembly shown in FIG. 4;
  • FIG. 6 is a side sectional view of a portion of the apparatus of the present invention illustrating the novel piston and piston inlet construction, the section being taken along a vertical plane through the centerline of the piston;
  • FIG. 7 is a diagrammatic view of a typical closed circuit cooling system wherein the fluid may be forced through an oil filter to clean the fluid before returning to the pump inlet port;
  • FIG. 8 is an end sectional view of the pump of FIG. 1, the section being taken along the line 8-8 of FIG. 1.
  • FIGS. 1 and 2 a variable displacement pump constructed in accordance with the present invention is illustrated in FIGS. 1 and 2 and comprises a housing indicated generally at that includes a front housing portion indicated generally at 22 and a rear housing portion indicated generally at 24.
  • the housing portions are joined together at the central portion of the pump and held by a plurality of studs 26.
  • a drive shaft 28 is mounted in the forward end of the housing by tapered roller bearing assemblies 30 and 32 which are pressed into recesses 34 and 36.
  • An oil seal 38 is pressed into a recess 40 in housing 20 and includes an annular resilient element 42 that wipes the periphery of drive shaft 28.
  • the inner end of drive shaft 28 carries a cam means indicated generally at 44 which includes a central bore 46 provided with a keyway 48 that receives a key 50 for preventing rotation of cam means 44 relative to shaft 28.
  • the cam means is retained on shaft 28 by a nut 52 which is tightened into locked relationship on a threaded inner end of shaft 28.
  • cam means 44 includes an inclined surface 54 which engages a plurality of nylon shoes 56, the latter including sockets 58 which form pivotal ball joints with ball-shaped ends 68 formed on a plurality of pumping pistons 62.
  • Each of the nylon shoes 56 is surrounded by a metal casing 64 that is crimped around the ball-shaped end 60 of its respective piston 62.
  • Each metal casing 64 also includes an inwardly extended annular protrusion 66 that snaps into an annular recess 68 formed in the base of the nylon shoe portion.
  • a cylinder barrel cartridge assembly indicated generally at 70 is axially slideably mounted within housing 20 and guided by a plurality of guide grooves 72 which receive longitudinally extending bearing members 76.
  • Members 76 may best be described as side rail bearings and function not only to absorb piston side thrust reaction imposed on barrel 70 but, in addition, bearing members 76 function as keys against cylinder barrel reaction and thereby serve to absorb torque.
  • Pistons 62 are disposed in respective barrel cylinders 78 which receive low pressure oil or hydraulic fluid in a novel manner via housing inlet port 80, passage 84 in front housing portion 22, an inlet chamber indicated generally at 86 within housing 20 and barrel inlet passages 88 formed in each piston 62.
  • inlet ports 88 in pistons 62 communicate with a cavity 71 formed in each piston 62 which in turn communicates with a respective cylinder 78 through an orifice 73 in the rearward end of piston 62.
  • Each of the pistons 62 is provided with an intake valve means formed by a ball-check valve 75 is freely carried in the opening to cavity 71 between a valve seat portion 77 and a stop portion 79 formed in each piston 62.
  • each cylinder 78 includes a unique outlet port construction whereby a first cylinder outlet port 81 is disposed in a side wall of each cylinder 78 and a second cylinder outlet passage 83 is axially spaced from outlet port 81 and formed in the rearward end of cylinders 78.
  • the axially spaced cylinder outlets 81 and 83 may both be disposed in a side wall of cylinder 78 without departing from the spirit of the invention although the structure shown is preferred. Further, the inlet port may also be formed in the cylinder instead in the pistons as shown in the preferred embodiment without departing from the spirit of the present invention.
  • each of the cylinders 78 includes a respective reaction plug, indicated generally at in free self-aligning engagement with the inner end surface 92 of rear housing portion 24.
  • Each reaction plug 99 is provided with a central bore 94 that carries a pressure responsive outlet valve means formed by a ball check valve 96 which is freely retained in bore 94 by a threaded plug 98.
  • Each threaded plug 98 includes a seat portion 100, a second barrel outlet passage 102, and a radial passage 103, the latter communicating with an annular passage 104 formed in the outer wall of reaction plug 98.
  • bore 94 in each reaction plug 98 includes a valve stop 106 and a compression spring 108 which serve to limit the stroke of the ball and bias its toward a closed position.
  • a plurality of pressure responsive valves 87 attached to the outer surface of barrel 70 by screws 89, covers each of the first cylinder outlets 81 and is in the form of a substantially flat, flexible reed-type valve.
  • Pressure responsive valves 87 is normally biased in a closed position and the degree of valve opening is limited by a stiff back-up plate 91 attached by screws 89 to pressure responsive valves 87.
  • valves 87 are preferred because they provide eflicient valve means and yet conveniently take up little space. Further, valves 87 are easily incorporated into the cylinder barrel cartridge assembly 70 to provide an integral package to offer the attractive commercial advantages previously mentioned.
  • first barrel outlet passages 81 are each valved by their respective pistons 62 and will be referred to herein as piston position responsive valves for said first barrel outlet passages.
  • Outlet chamber 93 is isolated from the inlet fluid in inlet chamber 86 by an annular seal engaging barrel 70 and an annular cylinder barrel driving piston, indicated generally at 146 which will be described in detail later herein.
  • Outlet chamber 93 completely surrounds cylinder barrel assembly 70 and forms a passage means for the outlet flow of fluid through a check valve 220 disposed in a housing outlet port 222 formed in the rear housing portion 24.
  • outlet passage 81 is closed by the outer wall of cylinder 78 and flexible reed valve 87 will close.
  • outlet passage 81 depends upon the position of barrel 70, hence passage 81, relative to the stroke of piston 62. Further, since the fluid from outlet passage 81 flows completely around barrel 70, a very effective cooling flow is developed.
  • Hollow outlet member 110 includes the central passage 112 that communicates with high pressure discharge passage 114 that in turn leads to housing outlet port 116.
  • outlet member 110 also includes a foot portion provided with a surface 118 that is in slideable sealed engagement with a longitudinally extending surface 120 formed in the outer wall of cylinder barrel 70.
  • pressure biased outlet member 110 includes a piston surface 124 that causes the pressurized hydraulic fluid in passage 112 to bias the surface 118 on outlet member 110 downwardly into sealed engagement with longitudinally extending surface 120 on barrel 70.
  • outlet member 110 can be structurally modified so as to be hydraulically balanced in accordance with the teachings in my co-pending application Serial No. 594,350.
  • a spring 126 augments the biasing force of the high pressure oil on piston surface 124 and also serves to retain surface 118 in sealed engagement with surface 120 at low pressures and at the outset of operation.
  • outlet member 110 The outer peripheral surface of outlet member 110 is provided with an annular seal 128 and a threaded plug 129 is screwed into the hole forming passage 112 and includes an inner protrusion that forms a retainer for the end of spring 126.
  • outlet member 110A includes a base surface 136 that is hydraulically biased int-o sealed engagement with a longitudinally extending surface 138 formed in the outer wall of cylinder barrel 70. Outlet member 110A is biased downwardly against longitudinally extending surface 138 by a force exerted by a piston surface 124, pressurized oil in a passage 140.
  • cylinder barrel 70 is constantly biased towards the front of the housing means by a control spring 142 which is interposed between a spider 143 and an annular shoulder 145 formed on cylinder barrel 7 0.
  • Cylinder barrel 70 is hydraulically shifted axially against the biasing force of control spring 142 by an annular cylinder barrel driving piston indicated generally at 146 in FIG. 1.
  • Piston 146 is mounted in a cylindrical surface 148 and forms therewith control cylinder 150 for receiving pressurized oil in a manner later to be described.
  • a small annular piston surface 152 of large diameter provides suflicient axial force with low control pressures to shift cylinder barrel 70 against the force of control spring 142.
  • piston 146 includes a rear end 155 in force transmitting engagement with annular seal which in turn is in force transmitting engagement with an annular base portion 157 on cylinder barrel cartridge 70.
  • pressurized oil is delivered through control apparatus to control cylinder via outlet port 122-A, passage 140, passage 144, orifice 147, radial passages 130 in spool housing 151, lateral passage 154 in control block 156, longitudinal passage 158 in control block 156, vertical passage 160 in control black 156 and passage 162 in housing 20 which connects to control cylinder 150.
  • spool housing 151 carries a longitudinally shiftable spool member 164 that is normally biased towards a closed position by a spring 166, the latter being contained in a spring housing 168 that is threaded into control block 156 at a threaded hole 170.
  • Compression spring 166 is selectively compressed or compressed by manipulating a control knob 172 that includes a shank 174 in threaded engagement with spring housing 168 at a threaded hole 176.
  • a radial passage 178 communicating with passage 162 in housing 20 provides a direct drain back to tank for any fluid that may flow back from control cylinder 150 during shock conditions.
  • control block 156 is mounted on housing 20 by a plurality of studs 192. It will be understood that other types of control apparatus responsive to various load conditions can be readily adapted to replace control apparatus 135.
  • the pumping pistons 62 are returned and biased against cam means 44 by a single centrally disposed piston return rod 194, FIG. 1, which includes an arcuate socket 196.
  • a ball 198 fits into socket 196 of rod 194 and also into a socket 200 formed in a piston return yoke 202.
  • Yoke 202 includes a plurality of radially extending slots 204 that fit around neck portions 206. Piston return y-oke 202 applies force to the rear sides of the ball-shaped piston ends 60 and in turn receives force from piston return rod 194 via the pivot joint formed by ball 198 and sockets 196 and 200.
  • a compression spring 210 is disposed between a shoulder 214 on the rear end of piston return rod 194, a shoulder 214 on a spring retainer plug 216 which in turn bears against the front side of spider 143.
  • Spider 143 is restrained from rearward movement by the shoulders 224 formed on the ends of reaction plugs 90. It should be pointed out the reaction plugs 90 are fitted loosely into respective holes 91 in spider 143 and are in free engagement with the inner surface 92 of the housing whereby the plugs are self-aligning with respect to pump cylinders 78.
  • cam 44 reciprocates pistons 62 which, on the suction stroke draw fluid into cylinders 78 via inlet port 80, inlet passage 84, inlet chamber 86, barrel inlet passages 88, cavity or passage 71, and orifice 73.
  • inlet port means may be disposed in the cylinders 78 themselves instead of in pistons 62 without departing from the spirit of the invention.
  • the intake fluid forces ball-check valve 75 away from seat portion 77 as it enters passages 88 and fiows through cavity 71 and out of orifice 73 into cylinders 78.
  • valves 87 are normally biased in a closed position.
  • first cylinder outlet passages 81 On the compression stroke, fluid is delivered first through first cylinder outlet passages 81 as the flexible valves 87 are forced open with the degree of opening being limited by back-up plate 91.
  • the amount of flow through passages 81 depends upon the position of passages 81 relative to the stroke of pistons 62 which in the variable displacement pump illustrated, varies according to the position of barrel 70. Fluid then flows into and through outlet chamber 93 to housing outlet port 222 and out one way check valve assembly 220, best seen in FIGS. 3, 4, and 5.
  • check valve 220 is biased against a valve seat portion 226 by a spring 228 and prevents fluid from flowing back into outlet chamber 93.
  • ressurized fluid from cylinder outlets passages 81 flows through chamber 93 and forces valve 220 open to permit fluid to flow out of housing outlet port 222.
  • outlet check valve 220 may be used in place of outlet check valve 220 to prevent flow back through port 222 on the suction stroke of pistons 62.
  • the fluid from port 222 may then be delivered to a load or recirculated for cooling purposes.
  • a typical closed circuit cooling system is illustrated diagrammatically in FIG. 7.
  • the fluid from port 222 leads to a heat exchanger 260 and then is forced through a very fine filter 262 before returning to reservoir 250.
  • the fluid from reservoir 250 is pulled through a conventional wire screen filter 252 to inlet port 80. Therefore, the oil circulated through the pump housing 29 is cooled and cleansed before returning to the interior of the housing. It is important to point out that a substantial flow through cylinder outlet passages 81 occurs which is delivered out of outlet port 222 to provide very eflicient cooling of the hydraulic system.
  • the fluid in inlet chamber 86 is isolated from the fluid in outlet chamber 93 by annular seal 95.
  • variable control apparatus 135 for shifting annular piston 146 and cylinder barrel 70 as previously mentioned.
  • a constant pressure at the load is obtained by arranging spool 164 to open only when a predetermined selected load pressure is exceeded.
  • Control knob 172 is adjusted to compress spool control spring 166 so as to bias spool 164 with the proper force to permit its opening when the predetermined selected operating pressure is exceeded.
  • oil from the manifold passes through passage 144 and orifice 147 to spool cylinder 149.
  • the increased pressure in the spool chamber overcomes the preset control force exerted by spool control spring 166 whereby the spool is shifted to the left, as viewed in FIG. 1, and oil is released through radial passages 130 in spool housing 151 and thence through the previously described passages to the control cylinder 150.
  • the pumping apparatus may be readily adapted to perform as two fixed displacement pumps with both housing outlet ports 116 and 222 connected to a load.
  • the cylinder barrel 70 may be fixedly positioned to divide the flow between outlets 81 and 83 in any manner desired or a variable flow control may be used to control one circuit with the excess delivered to the second circuit.
  • valve means such as, for example, an orifice which permits substantial flow in only one direction may be used to replace valves 87 and outlet passage 81, particularly for recirculating cooling fluid, without departing from the spirit of the present invention.
  • a variable displacement axial type pump the combination of a housing including a housing inlet port and first and second housing outlet ports; an axially shiftable cylinder barrel disposed in said housing and including a cylinder provided with axially spaced first and second barrel outlet passages, a piston mounted for reciprocation in said cylinder, and a barrel inlet passage; intake valve means carried by said barrel for said inlet passage whereby fluid enters said cylinder on the suction stroke and fluid is discharged first from said first barrel outlet passage and one of said housing outlet ports during a portion of the compression stroke of said piston and then through said second barrel outlet passage and the other of said housing outlet ports during a subsequent portion of said compression stroke, said first barrel outlet passage including a piston position responsive valve and a pressure responsive valve; and a pressure responsive outlet valve means for said second barrel outlet passage whereby fluid is diverted through said first barrel outlet passage to cool said pump during operating conditions of reduced flow through said second barrel outlet passage.
  • a housing including a housing inlet port and first and second housing outlet ports; an axially shiftable cylinder barrel disposed in said housing and including a plurality of cylinders, each of said cylinders including a first barrel outlet passage in a side wall of said barrel and a second barrel outlet passage, pistons mounted for reciprocation in said cylinders, an annular manifold communicating with said second barrel outlet passages, and barrel inlet passages communicating with said cylinders; intake valve means carried by said barrel for said inlet passages whereby fluid enters said cylinders on the suction strokes and fluid is discharged first from said first barrel outlet passages and one of said housing outlet ports during portions of compression strokes of said pistons and through said second barrel outlet passages, said annular manifold, and the other of said housing outlet ports during subsequent portions of said compression strokes, each of said first barrel outlet passages including a piston position responsive valve and a pressure responsive valve; and a pressure responsive outlet valve for each of said second barrel outlet passages
  • the apparatus defined in claim 5 that includes a hollow outlet member radially shiftably mounted in said housing and provided with an inner surface slidably engaging the outer surface of said cylinder barrel for the passage of pressurized fluid from said annular manifold to said other of said housing outlet ports.
  • the apparatus defined in claim 5 that includes an annular cylinder barrel driving piston for axially shifting said cylinder barrel, and an annular seal between said barrel driving piston and said barrel, said seal serving to separate an inlet chamber in said housing from an annular cooling chamber in said housing.
  • the apparatus defined in claim 5 that includes a hydraulically actuated control cylinder in said housing; an annular cylinder barrel driving piston disposed in said control cylinder for varying the location of said first barrel outlet passages relative to said pistons.
  • said barrel includes a plurality of axially extending guides; and a plurality of bearing members disposed between said guides and said housing.
  • the apparatus defined in claim 5 that includes a plurality of reaction plugs carried by said barrel and having inner ends disposed in said cylinders and outer ends freely engaging said housing, said second barrel outlet passages and pressure responsive outlet valves being disposed in said reaction plugs.
  • FIG. 1 reference numeral 130 has been added with a lead line to the dottedpassage communicating passages 130 and 162.
  • reference numeral 124 has been deleted and 110-A inserted therefor.
  • reference numeral 92 has been added with a lead line to the barrel surface represented by reference numeral 92 in Fig. 1.
  • Column 6, cancel lines 13 31 and substitute der 150 via cylinder block outlet passage 1221A, passage 140 in outlet member llO-A, passage 144, orifice 147 and a radial passage v130 that connects with a housing passage 162 which in turn connects with control cylinderlSO as seen in Fig. l.
  • a control spool 149 is axially slideably mounted in a spool housing 151 and is biased toward a left position by compression spring 166 in which position spool 149 normally isolates radial passage 130 from control orifice 147.
  • control orifice 147 When the fluid pressure through control orifice 147 exceeds a predetermined pressure value, established by the selected setting of a control knob 172 that includes a shank 174 in threaded engagement with a spring housing 168 at a threaded hole 176, then spool 149 shifts to the right thereby overcoming spring 166 via self-aligning spool end 164. Radial passage 130 is thereby opened and pressurized fluid is released to control cylinder 150 as explained above. This serves to shift cylinder block 70 to the left, Fig. l, to a new position of equilibrium wherein the force exerted on the cylinder block by compression spring 142 equals the force exerted on said block by annular control piston 146.
  • a radial passage 178 in the pump housing provides a drain from the control apparatus 135 back to the relatively low pressure outlet chamber 93.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
US495168A 1965-10-12 1965-10-12 Hydraulic pumping apparatus Expired - Lifetime US3384029A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US495168A US3384029A (en) 1965-10-12 1965-10-12 Hydraulic pumping apparatus
CH1462466A CH454626A (de) 1965-10-12 1966-10-11 Hydraulische Kolbenpumpe
DE1653480A DE1653480B2 (de) 1965-10-12 1966-10-11 Einrichtung zum Verändern der Fördermenge einer Taumelscheiben-Axialkolbenpumpe
GB45447/66A GB1169947A (en) 1965-10-12 1966-10-11 Reciprocating Hydraulic Pumps
BE688123D BE688123A (enrdf_load_html_response) 1965-10-12 1966-10-12

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US495168A US3384029A (en) 1965-10-12 1965-10-12 Hydraulic pumping apparatus

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US3384029A true US3384029A (en) 1968-05-21

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US495168A Expired - Lifetime US3384029A (en) 1965-10-12 1965-10-12 Hydraulic pumping apparatus

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US (1) US3384029A (enrdf_load_html_response)
BE (1) BE688123A (enrdf_load_html_response)
CH (1) CH454626A (enrdf_load_html_response)
DE (1) DE1653480B2 (enrdf_load_html_response)
GB (1) GB1169947A (enrdf_load_html_response)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2440158A1 (de) * 1973-08-27 1975-03-06 Trw Inc Hydraulischer antrieb
US20150361970A1 (en) * 2013-02-04 2015-12-17 Parker-Hannifin Corporation ("Parker") Gas compressor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4126640B4 (de) * 1991-08-12 2005-06-16 Robert Bosch Gmbh Pumpenanordnung mit einer Vorförderpumpe und einer Radialkolbenpumpe

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US2620733A (en) * 1946-06-19 1952-12-09 John W Overbeke Hydraulic fluid mechanism
US2990781A (en) * 1957-11-25 1961-07-04 Gen Motors Corp Wobble plate pump
US3024731A (en) * 1960-08-03 1962-03-13 Gen Electric Arrangement for adjusting the displacement of a piston
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US3183847A (en) * 1961-12-22 1965-05-18 Hydro Kinetics Inc Variable displacement pump
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US3067694A (en) * 1959-12-24 1962-12-11 Lear Siegler Inc Piston pump
US3024731A (en) * 1960-08-03 1962-03-13 Gen Electric Arrangement for adjusting the displacement of a piston
US3183847A (en) * 1961-12-22 1965-05-18 Hydro Kinetics Inc Variable displacement pump
US3145660A (en) * 1962-02-13 1964-08-25 Bush Vannevar Free piston hydraulic pump
US3249052A (en) * 1964-03-17 1966-05-03 Peter S Karlak Variable delivery multi-liquid pump

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US20150361970A1 (en) * 2013-02-04 2015-12-17 Parker-Hannifin Corporation ("Parker") Gas compressor

Also Published As

Publication number Publication date
CH454626A (de) 1968-04-15
DE1653480C3 (enrdf_load_html_response) 1974-05-16
DE1653480B2 (de) 1973-10-18
BE688123A (enrdf_load_html_response) 1967-03-16
GB1169947A (en) 1969-11-05
DE1653480A1 (de) 1973-03-01

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