US20040042906A1 - Long-piston hydraulic machines - Google Patents

Long-piston hydraulic machines Download PDF

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Publication number
US20040042906A1
US20040042906A1 US10/647,557 US64755703A US2004042906A1 US 20040042906 A1 US20040042906 A1 US 20040042906A1 US 64755703 A US64755703 A US 64755703A US 2004042906 A1 US2004042906 A1 US 2004042906A1
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United States
Prior art keywords
piston
cylinder
swash
plate
hydraulic machine
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.)
Abandoned
Application number
US10/647,557
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English (en)
Inventor
Vernon Gleasman
Keith Gleasman
Matthew Wrona
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.)
Torvec Inc
Original Assignee
Torvec Inc
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
Priority claimed from US10/229,407 external-priority patent/US20040042910A1/en
Application filed by Torvec Inc filed Critical Torvec Inc
Priority to US10/647,557 priority Critical patent/US20040042906A1/en
Assigned to TORVEC, INC. reassignment TORVEC, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GLEASMAN, KEITH E., GLEASMAN, VERNON E., WRONA, MATTHEW R.
Priority to CA002494996A priority patent/CA2494996C/fr
Priority to MXPA05002282A priority patent/MXPA05002282A/es
Priority to JP2004531484A priority patent/JP4350038B2/ja
Priority to BR0313882-8A priority patent/BR0313882A/pt
Priority to CNB038205033A priority patent/CN100406726C/zh
Priority to EP03791793A priority patent/EP1546559A4/fr
Priority to AU2003265692A priority patent/AU2003265692B2/en
Priority to KR1020057003519A priority patent/KR100659682B1/ko
Priority to PCT/US2003/026707 priority patent/WO2004020827A2/fr
Priority to US10/789,739 priority patent/US6983680B2/en
Publication of US20040042906A1 publication Critical patent/US20040042906A1/en
Priority to US11/153,111 priority patent/US7416045B2/en
Priority to US11/199,632 priority patent/US7635255B2/en
Priority to US12/176,678 priority patent/US20080276609A1/en
Abandoned 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders 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
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons
    • F04B1/126—Piston shoe retaining 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
    • F04B1/141—Details or component parts
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/109—Lubrication

Definitions

  • This invention relates to hydraulic pump/motor machines that have elongated pistons reciprocating in cylinders and, more particularly, to a system for lubricating such pistons while maintaining contact between the heads of such pistons and the swash-plate of the pump/motor.
  • Hydraulic pumps and motors are well known and widely used, having reciprocating pistons mounted in respective cylinders formed in a cylinder block and positioned circumferentially at a first radial distance about the rotational axis of a drive element.
  • Many of these pump/motor machines have variable displacement capabilities; and they are generally of two basic designs: (a) either the pistons reciprocate in a rotating cylinder block against a variably inclined, but otherwise fixed, swash-plate or (b) the pistons reciprocate in a fixed cylinder block against a variably inclined and rotating swash-plate that is generally split to include a non-rotating (but nutating) wobbler that slides upon the surface of a rotating (and nutating) rotor. While the invention herein is applicable to both of these designs, it is particularly appropriate for, and is described herein as, an improvement in the latter type of machine.
  • One spherical end of the dog bone is pivotally mounted into the head end of the piston, while the other spherical end is usually covered by a pivotally-mounted conventional “shoe” element that must be held at all times against the swash-plate wobbler.
  • Dog-bone rods are also sometimes used to interconnect one end of each piston with the inclined (but not rotating) swash-plates of hydraulic machines having rotating cylinder blocks.
  • this latter type of machine omits such dog-bones, using instead elongated pistons, each having a spherical head at one end (again, usually covered by a pivotally-mounted conventional shoe element) that effectively contacts the non-rotating flat surface of the swash-plate.
  • Such elongated pistons are designed so that a significant portion of the axial cylindrical body of each piston remains supported by the walls of its respective cylinder at all times during even the maximum stroke of the piston.
  • This additional support for such elongated pistons is designed to assure minimal lateral displacement of each spherical piston head as it slides over the inclined-but-not-rotating swash-plate when the pistons rotate with their cylinder block.
  • blow-by that portion of the high-pressure fluid that is forced between the walls of each cylinder and the outer circumference of each piston body as the reciprocating piston drives or is driven by high-pressure fluid.
  • blow-by provides good lubrication only if tolerances permit the flow of sufficient fluid between the walls of the cylinder and the long cylindrical body of the piston, and blow-by sufficient to assure good lubrication often negatively affects the volumetric efficiency of the pump or motor machine. For instance, a 10 cubic inch machine can use as much as 4 gallons of fluid per minute for blow-by. While smaller tolerances can often be used to reduce blow-by, the reduction of such tolerances is limited by the need for adequate lubrication.
  • the invention disclosed below is directed to improving the volumetric efficiency of such elongated-piston machines while, at the same time, assuring (a) appropriate lubrication of the pistons and (b) simplification of the apparatus used to maintain contact between the pistons and the swash-plate.
  • the invention is disclosed on two different hydraulic machines. Both have the preferred format of fixed cylinder blocks and rotating/nutating swash-plates. [However, persons skilled in the art will appreciate that the invention is equally applicable to hydraulic machines with rotating cylinder blocks and swash-plates that do not rotate with the drive elements of the machines.]
  • Each disclosed machine can operate as either a pump or a motor.
  • One has a swash-plate that, while rotating at all times with the drive element of the machine, is fixed at a predetermined inclined angle relative to the axis of the drive element so that the pistons move at a maximum predetermined stroke at all times.
  • the swash-plate of the other disclosed machine has an inclination that can be varied throughout a range of angles in a manner well known in the art to control the stroke of the pistons throughout a range of movements up to a maximum in each direction.
  • each piston is elongated, having an axial cylindrical body portion that preferably is substantially as long as the axial length of the respective cylinder in which it reciprocates.
  • each piston also has a spherical head end that, by means of a conventionally pivoted shoe and relatively simple apparatus, is maintained in effective sliding contact with a flat face of the machine's swash-plate.
  • the axial length of each cylindrical piston body is selected to assure minimal lateral displacement of the spherical first end of the piston at all times.
  • each cylinder formed within the cylinder blocks of each machine is provided with a respective lubricating channel formed in the cylindrical wall of each cylinder.
  • This lubricating channel is positioned so that at all times during reciprocation of the piston within its respective cylinder, each respective lubricating channel remains substantially closed by the axial cylindrical body of the piston during its entire stroke.
  • each respective lubricating channel is formed circumferentially and radially transects each cylinder.
  • Also formed in the fixed cylinder block of each machine is a plurality of further passageways that interconnect each of the just-described lubricating channels.
  • the interconnection of all of the lubricating channels, one to another, forms a single, continuous lubricating passageway in the cylinder block.
  • This continuous lubricating passageway is formed entirely within the cylinder block, preferably transecting each cylinder and being centered circumferentially at substantially the same radial distance as the cylinders are centered about the rotational axis of the drive element.
  • each piston is described as having an axial cylindrical body portion and a spherical head end, while each respective cylinder has a valve end and an open head portion beyond which the spherical head end of each piston extends at all times.
  • the continuous lubricating passageway just described above is not connected by either fluid “input” or fluid “output” passageways but instead is substantially closed off by the cylindrical body portions of the pistons at all times during operation of the machine.
  • this lubricating passageway almost instantly fills with initial blow-by of high-pressure fluid that enters at the valve end of each cylinder and then passes between the walls of each cylinder and the outer circumference of the body portion of each driven piston.
  • This blow-by effectively maintains high pressure within the continuous lubricating passageway at all times.
  • a plurality of sealing members, each located respectively near the open end of each cylinder, provides a relatively tight seal for substantially eliminating blow-by between the body portion of each piston and the open head portion of each respective cylinder, thereby allowing the escape of only minimal blow-by from this lubricating passageway past the open end of the cylinders.
  • the lubricating fluid in this closed continuous lubricating passageway moves constantly as the result of the ever-changing pressures in each of the respective cylinders as the pistons reciprocate. That is, as the pressure in each cylinder is reduced to low pressure on the return stroke of each piston, the high-pressure fluid in the otherwise closed lubricating passageway is again driven between the walls of each cylinder and the outer circumference of the body of each piston into the valve end of each cylinder experiencing such pressure reduction.
  • this secondary blow-by is not “lost”, i.e., it does not return to the sump to be replenished into the closed loop hydraulic system by the charge pump.
  • this secondary blow-by is immediately returned to the closed loop without requiring the use of a charge pump, and the closed continuous lubricating passageway is immediately replenished by the entrance of a similar flow of high-pressure blow-by from the valve end of each cylinder experiencing increased pressure.
  • This just-described lubricating passageway provides appropriate lubrication to the high-speed reciprocation of the pistons while substantially reducing blow-by.
  • blow-by was reduced by 90%. That is, the blow-by experienced by conventional commercial hydraulic machines of comparable specifications generally ranges between 4-5 gallons per minute, while the blow-by experienced by the invention's prototypes ranges between 0.5-0.7 gallons per minute, thereby remarkably increasing the volumetric efficiency of the invention's hydraulic machines.
  • fixed-cylinder-block hydraulic machines can be built smaller and lighter than conventional rotating block hydraulic machines having similar specifications.
  • the disclosed invention makes it possible to use these smaller and lighter designs to meet the high-speed/high-pressure specifications required for automotive use.
  • each of the invention's support assemblies disclosed herein (a) omits dog-bones that normally are mounted between the outer end of each piston and the nutating-only wobbler portion of a conventional rotating/nutating swash-plate but (b) also omits the nutating-only wobbler portion of a conventional rotating/nutating swash-plate.
  • a conventional shoe is mounted directly to the spherical head of each piston and is maintained in effective sliding contact with the flat face of the swash-plate's rotor portion by means of a minimal spring bias sufficient to maintain such effective sliding contact in the absence of hydraulic pressure at the valve ends of the pump's cylinders.
  • the first simplified support mechanism comprises a unique hold-down plate assembly biased by a coil spring positioned circumferentially about the rotational axis of the pump's drive element.
  • the invention's second support mechanism is even simpler, comprising nothing more than a conventional shoe mounted directly to the spherical head of each piston, with the minimal bias being supplied by a plurality of springs, each spring being positioned respectively between the body portion of each respective piston and the valve end of each respective cylinder. While the second support mechanism is a little more difficult to assemble than the first, the latter is considerably simpler, lighter, and cheaper to manufacture.
  • FIG. 1 is a partially schematic and cross-sectional view of a hydraulic machine with a fixed cylinder block and a rotating/nutating swash-plate having a fixed angle of inclination, showing the invention incorporated in the cylinder block and at the piston/swash-plate interface.
  • FIG. 2 is a partially schematic and cross-sectional view of the fixed cylinder block of the hydraulic machines of FIGS. 1 and 3 taken along the plane 2 - 2 with parts being omitted for clarity.
  • FIG. 3 is a partially schematic and cross-sectional view of a hydraulic machine with a fixed cylinder block and a rotating/nutating swash-plate having a variable angle of inclination, again showing the invention incorporated in the cylinder block and at the piston/swash-plate interface.
  • FIGS. 4A and 4B are partially schematic and cross-sectional views of the swash-plate and piston shoe hold-down assembly disclosed in FIGS. 1 and 3 when the swash plate is inclined at +25°, with parts removed for clarity, showing relative positions of the head ends of the pistons, shoes, and special washers, as well as the spring-biased hold-down element that biases each sliding shoe against the flat face of the swash-plate;
  • the view in FIG. 4A is taken in the plane 4 A- 4 A of FIG. 3 in the direction of the arrows
  • the view in FIG. 4B is taken in the plane 4 B- 4 B of FIG. 4A.
  • FIGS. 5A and 5B, 6 A and 6 B, and 7 A and 7 B are, respectively, views of the same parts illustrated in FIGS. 4A and 4B when the swash-plate is operating at three other inclinations, namely, at +15°, 0°, and ⁇ 25°.
  • FIG. 8 is an enlarged, partial, schematic and cross-sectional view of only a single cylinder and piston for another hydraulic machine similar to those shown in FIGS. 1 and 3 but showing a more simplified second embodiment of a spring-biased hold-down assembly for the invention's piston shoes.
  • hydraulic motor 10 includes a fixed cylinder block 12 having a plurality of cylinders 14 (only one shown) in which a respective plurality of mating pistons 16 reciprocates between the retracted position of piston 16 and the extended position of piston 16 ′.
  • Each piston has a spherical head 18 that is mounted on a neck 20 at one end of an elongated axial cylindrical body portion 22 that, in the preferred embodiments shown, is substantially as long as the length of each respective cylinder 14 .
  • Each spherical end 18 fits within a respective shoe 24 that slides over a flat face 26 formed on the surface of a rotor 28 that, in turn, is fixed to a drive element, namely, shaft 30 of the machine.
  • Shaft 30 is supported on bearings within a bore 31 in the center of cylinder block 12 .
  • Flat face 26 of fixed rotor 28 is inclined at a predetermined maximum angle (e.g., 25°) to the axis 32 of drive shaft 30 , being supported by an appropriate thrust bearing assembly 35 .
  • a modular valve assembly 33 which is bolted as a cap on the left end of cylinder block 12 , includes a plurality of spool valves 34 (only one shown) that regulates the delivery of fluid into and out the cylinders 14 .
  • each of the machines disclosed can be operated as either a pump or as a motor.
  • the fixed-angle swash-plate machine shown in FIG. 1 is being operated as a motor.
  • fluid inlet 36 and outlet 39 are preferably connected through appropriate “closed loop” piping to a mating hydraulic pump (e.g., pump 110 shown in FIG. 3 and discussed below) so that, at all times, fluid pressure biases spherical ends 18 and respective shoes 24 against flat face 26 .
  • a mating hydraulic pump e.g., pump 110 shown in FIG. 3 and discussed below
  • the serial extension and retraction of each respective piston causes rotor 28 to rotate, thereby driving shaft 30 .
  • Flat face 26 is fixed at the maximum angle of inclination so that, when the flow rate of hydraulic fluid being circulated in the closed loop through inlet 36 and outlet 39 is relatively small, pistons 16 reciprocate relatively slowly, resulting in a relatively slow rotation of drive shaft 30 .
  • Cylinder block 12 is modified by the invention to address such lubrication needs and to reduce such blow-by losses.
  • each cylinder 14 is transected radially by a respective lubricating channel 40 formed circumferentially therein.
  • a plurality of passageways 42 interconnect all lubricating channels 40 to form a continuous lubricating passageway in cylinder block 12 .
  • Each respective lubricating channel 40 is substantially closed by the axial cylindrical body 22 of each respective piston 16 during the entire stroke of each piston. That is, the outer circumference of each cylindrical body 22 acts as a wall that encloses each respective lubricating channel 40 at all times.
  • Continuous lubricating passageway 40 , 42 is simply and economically formed within cylinder block 12 as can be best appreciated from the schematic illustration in FIG. 2 in which the relative size of the fluid channels and connecting passageways has been exaggerated for clarification.
  • the just-described lubrication arrangement is not only remarkably simple, but it also permits a similar simplification of the pinion/swash-plate interface apparatus of the hydraulic machine to further reduce the cost of manufacture and operation.
  • the pinion/swash-plate interface apparatus shown in FIG. 1 comprises only (a) rotor 28 mounted on drive shaft 30 using conventional needle and thrust bearings and (b) a simple spring-biased hold-down assembly for maintaining piston shoes 24 in constant contact with the rotating and nutating flat surface 26 of rotor 28 .
  • a simple spring-biased hold-down assembly for maintaining piston shoes 24 in constant contact with the rotating and nutating flat surface 26 of rotor 28 .
  • the first embodiment of the invention's hold-down assembly includes a coil spring 50 that is positioned about shaft 30 and received in an appropriate crevice 52 formed in cylinder block 12 circumferentially about axis 32 .
  • Spring 50 biases a hold-down element 54 that is also positioned circumferentially about shaft 30 and axis 32 .
  • Hold-down element 54 is provided with a plurality of openings, each of which surrounds the neck 20 of a respective piston 16 .
  • a respective special washer 56 is positioned between hold-down element 54 and each piston shoe 24 .
  • Each washer 56 has an extension 58 that contacts the outer circumference of a respective shoe 24 to maintain the shoe in contact with flat face 26 of rotor 28 at all times.
  • a variable hydraulic pump 110 includes a modular fixed cylinder block 112 which is identical to cylinder block 12 of hydraulic motor 10 shown in FIG. 1 and described above.
  • Cylinder block 112 has a plurality of cylinders 114 (only one shown) in which a respective plurality of mating pistons 116 reciprocates between the retracted position of piston 116 and variable extended positions (the maximum extension being shown in the position of piston 116 ′).
  • Each piston has a spherical head 118 that is mounted on a neck 120 at one end of an elongated axial cylindrical body portion 122 that, in the preferred embodiment shown, is substantially as long as the length of each respective cylinder 114 .
  • Each spherical piston head 118 fits within a respective shoe 124 that slides over a flat face 126 formed on the surface of a rotor 128 that, as will be discussed in greater detail below, is pivotally attached to a drive element, namely, shaft 130 that is supported on bearings within a bore 131 in the center of cylinder block 112 .
  • variable pump 110 is also provided with a modular valve assembly 133 that is bolted as a cap on the left end of modular cylinder block 112 and, similarly, includes a plurality of spool valves 134 (only one shown) that regulates the delivery of fluid into and out of cylinders 114 .
  • each of the machines disclosed can be operated as either a pump or as a motor.
  • the variable-angle swash-plate machine 110 shown in FIG. 3 is being operated as a pump, and drive shaft 130 is driven by a prime mover (not shown), e.g., the engine of a vehicle. Therefore, during the one-half of each revolution of drive shaft 130 , lower pressure fluid is drawn into each respective cylinder 114 entering a port 137 from a “closed loop” of circulating hydraulic fluid through inlet 136 as each piston 116 is moved to an extended position.
  • each respective piston 116 During the next half of each revolution, the driving of each respective piston 116 back to its fully retracted position directs high-pressure fluid from port 137 into the closed hydraulic loop through outlet 139 .
  • the high-pressure fluid is then delivered through appropriate closed loop piping (not shown) to a mating hydraulic motor, e.g., motor 10 discussed above, causing the pistons of the mating motor to move at a speed that varies with the volume (gallons per minute) of high-pressure fluid being delivered in a manner well known in the art.
  • modular cylinder block 112 it is constructed identical to cylinder block 12 which has already been described. That is, the cylindrical wall of each cylinder 114 is transected radially by a respective lubricating channel 40 ′ formed circumferentially therein. A plurality of passageways 42 ′ interconnects all lubricating channels 40 ′ to form a continuous lubricating passageway in cylinder block 112 . A cross section of cylinder block 112 taken in the plane 2 - 2 looks exactly as the cross-sectional view of cylinder block 12 in FIG. 2.
  • the flow of lubricating fluid in closed continuous lubricating passageway 40 ′, 42 ′ is moderate but continuous as the result of “secondary” blow-by in response to piston motion and to the changing pressures in each half-cycle of rotation of drive shaft 130 as the pistons reciprocate.
  • lower fluid pressure is present in each cylinder 114 when each piston 116 is moving to an extended position, while the source of the high-pressure fluid that is forced between the walls of the cylinders and the outer circumference of each piston 116 occurs as each piston 116 is being driven from its extended position to its fully retracted position by the rotation of drive shaft 130 by the prime mover (not shown).
  • this just-mentioned secondary blow-by back into each cylinder 114 is not “lost”. Instead, it is immediately returned to the well-known closed hydraulic fluid loop that interconnects the pump and motor. That is, this secondary blow-by does not return to a sump and, therefore, does not have to be replenished into the closed loop hydraulic system by a charge pump. Also, while there may be a minimal fluid flow that leaks from closed continuous lubricating passageway 40 ′, 42 ′ past the seals 144 at the end of each cylinder 114 , any such minimal blow-by is instantly replenished by a similar flow of blow-by entering around the opposite end of each piston 116 experiencing increased pressure.
  • the invention permits the machine's swash-plate apparatus to be simplified by (a) the omission of the dog-bones that normally are mounted between the outer end of each piston and a nutating-only wobbler portion of a conventional rotating/nutating swash-plate and (b) the omission of the wobbler portion itself as well as the apparatus conventionally required for mounting the non-rotating wobbler to the rotating/nutating rotor portion of the swash-plate.
  • Rotor 128 is pivotally mounted to drive shaft 130 about an axis 129 that is perpendicular to axis 132 . Therefore, while rotor 128 rotates with drive shaft 130 , its angle of inclination relative to axis 130 can be varied from 0° (i.e., perpendicular) to ⁇ 25°. In FIG. 3, rotor 128 is inclined at +25°. This variable inclination is controlled as follows: The pivoting of rotor 128 about axis 129 is determined by the position of a sliding collar 180 that surrounds drive shaft 130 and is movable axially relative thereto.
  • a control-link 182 connects collar 180 with rotor 128 so that movement of collar 180 axially over the surface of drive shaft 130 causes rotor 128 to pivot about axis 129 .
  • the inclination of rotor 128 varies throughout a continuum from the +25° inclination shown, back to 0° (i.e., perpendicular), and then to ⁇ 25°.
  • swash-plate rotor 128 is balanced by a shadow-link 194 that is substantially identical to control-link 182 and is similarly connected to collar 180 but at a location on exactly the opposite side of collar 180 .
  • Fluid pressure constantly biases pistons 116 in the direction of rotor 128 , and a thrust plate 198 is provided to carry that load.
  • additional bias loading is necessary to assure constant contact between piston shoes 124 and flat surface 126 of rotor 128 .
  • the variable hydraulic machines of this invention are able to provide such additional bias by using either of two simple spring-biased hold-down assemblies, the first being similar to that already described above in regard to hydraulic motor 10 in FIG. 1.
  • FIG. 4A shows an enlarged view taken in the plane 4 A- 4 A of FIG. 3 when viewed in the direction of the arrows
  • FIG. 4B shows an enlargement of the same view of shown in FIG. 1 with parts removed for clarity.
  • the hold-down assembly for pump 110 includes a coil spring 150 that is positioned about shaft 130 and received in an appropriate crevice 152 formed in cylinder block 112 circumferentially about axis 132 .
  • Coil spring 150 biases a hold-down element 154 that is also positioned circumferentially about shaft 130 and axis 132 .
  • Hold-down element 154 is provided with a plurality of circular openings 160 , each of which surrounds the neck 120 of a respective piston 116 .
  • a plurality of special washers 156 is positioned, respectively, between hold-down element 154 and each piston shoe 124 .
  • Each washer 156 has an extension 158 that contacts the outer circumference of a respective shoe 124 to maintain the shoe in contact with flat face 126 of rotor 128 at all times.
  • each piston shoe 124 has a conventional pressure-balancing cavity centered on the flat surface of shoe 124 that contacts flat face 126 of rotor 128 , and that each respective shoe cavity is connected through an appropriate shoe channel 162 and piston channel 164 to assure that fluid pressure present at the shoe/rotor interface is equivalent at all times with fluid pressure at the head of each piston 116 . Since piston channel 164 passes through the center of spherical head 118 of each piston 116 , the position of channel 164 can be used to facilitate appreciation of the relative movements of the various parts of the hold-down assembly.]
  • each piston channel 164 (at the center of each spherical head 118 of each piston 116 ) has the same radial position relative to each respective circular opening 160 in hold-down element 154 .
  • the relative radial position of each piston channel 164 is different for each opening 160 , and the relative positions of each special washer 156 is also different.
  • each special washer 156 slips over the surface of hold-down element 154 as, simultaneously, each shoe 124 slips over the flat face 126 of rotor 128 ; and each of these parts changes relative to its own opening 160 through each of the various positions that can be seen in each of the other eight openings 160 .
  • a size is selected for the boundaries of each opening 160 so that the borders of opening 160 remain in contact with more than one-half of the surface of each special washer 156 at all times during each revolution of rotor 128 and for all inclinations of rotor 128 , as can be seen from the relative positions of special washers 156 and the borders of each of the openings 160 in each of the drawings from FIG. 4A through FIG. 7A.
  • a circular border is preferred for each opening 160 .
  • each shoe 124 and its respective mating special washer 156 using reinforced thermoplastic resin materials.
  • These mating parts can also be combined to form a single thermoplastic shoe/washer combination, with the shoe portion being manufactured so that it is formed about the spherical head 118 of each piston 16 ′, 22 .
  • the cost and complexity of thrust bearing assembly 35 can be significantly reduced by the use of reinforced thermoplastic resins.
  • FIG. 8 The second embodiment of the invention's hold-down assembly, while slightly more difficult to assemble, is considerably simpler and less expensive.
  • This second embodiment is shown schematically in FIG. 8 in an enlarged, partial, and cross-sectional view of a single piston of a further hydraulic machine 210 according to the invention.
  • Piston 216 is positioned in modular fixed cylinder block 212 within cylinder 214 , the latter being transected radially by a respective lubricating channel 40 ′′ formed circumferentially therein.
  • lubricating channel 40 ′′ is interconnected with similar channels in the machine's other cylinders by a plurality of passageways that forms a continuous lubricating passageway in cylinder block 212 ; and, similarly, a surrounding seal 244 is located near the open end of each cylinder 214 to minimize the loss of lubricating fluid from each lubricating channel 40 ′′.
  • fixed cylinder block 212 includes neither a large axially circumferential coil spring nor an axially circumferential crevice for holding the same.
  • the modular fixed cylinder block 212 of hydraulic machine 210 can be connected to either a modular fixed-angle swash-plate assembly (as shown in FIG. 1) or a modular variable-angle swash-plate assembly (as shown in FIG. 3); but in either case, hydraulic machine 210 provides a much simpler hold-down assembly.
  • the hold-down assembly of this embodiment comprises only a respective conventional piston shoe 224 for each piston 216 in combination with only a respective coil spring 250 , the latter also being associated with each respective piston 216 .
  • Each piston shoe 224 is similar to the conventional shoes shown in the first hold-down assembly just discussed above and, similarly, is mounted on the spherical head 218 of piston 216 to slide over the flat face 226 formed on the surface of the machine's swash-plate rotor 228 in a manner similar to that explained above.
  • Each coil spring 250 is, respectively, seated circumferentially about hydraulic valve port 237 at the valve end of each respective cylinder 214 and positioned within the body portion of each respective piston 216 .
  • each shoe 224 slips over flat face 226 of rotor 228 with a lemniscate motion that varies in size with the horizontal position of each piston 216 and the inclination of rotor 228 relative to axis 230 .
  • shoes 224 are maintained in contact with flat face 226 of the swash-plate by hydraulic pressure. Therefore, the spring bias provided by coil springs 250 is only minimal but still sufficient to maintain effective sliding contact between each shoe 224 and flat face 226 in the absence of hydraulic pressure at the valve end of each respective cylinder 214 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
US10/647,557 2002-08-28 2003-08-25 Long-piston hydraulic machines Abandoned US20040042906A1 (en)

Priority Applications (14)

Application Number Priority Date Filing Date Title
US10/647,557 US20040042906A1 (en) 2002-08-28 2003-08-25 Long-piston hydraulic machines
PCT/US2003/026707 WO2004020827A2 (fr) 2002-08-28 2003-08-26 Machines hydrauliques a pistons longs
MXPA05002282A MXPA05002282A (es) 2002-08-28 2003-08-26 Maquinas hidraulicas de piston largo.
CNB038205033A CN100406726C (zh) 2002-08-28 2003-08-26 长活塞液压机
KR1020057003519A KR100659682B1 (ko) 2002-08-28 2003-08-26 기다란 피스톤을 갖는 유압기계
JP2004531484A JP4350038B2 (ja) 2002-08-28 2003-08-26 長ピストン液圧機械
BR0313882-8A BR0313882A (pt) 2002-08-28 2003-08-26 Máquinas hidráulicas de pistão longo
CA002494996A CA2494996C (fr) 2002-08-28 2003-08-26 Machines hydrauliques a pistons longs
EP03791793A EP1546559A4 (fr) 2002-08-28 2003-08-26 Machines hydrauliques a pistons longs
AU2003265692A AU2003265692B2 (en) 2002-08-28 2003-08-26 Long-piston hydraulic machines
US10/789,739 US6983680B2 (en) 2002-08-28 2004-02-27 Long-piston hydraulic machines
US11/153,111 US7416045B2 (en) 2002-08-28 2005-06-15 Dual hydraulic machine transmission
US11/199,632 US7635255B2 (en) 2002-08-28 2005-08-09 Long piston hydraulic machines
US12/176,678 US20080276609A1 (en) 2002-08-28 2008-07-21 Dual hydraulic machine transmission

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US10/229,407 US20040042910A1 (en) 2002-08-28 2002-08-28 Long-piston hydraulic machines
US10/647,557 US20040042906A1 (en) 2002-08-28 2003-08-25 Long-piston hydraulic machines

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
US10/229,407 Continuation-In-Part US20040042910A1 (en) 2002-08-28 2002-08-28 Long-piston hydraulic machines

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US10/789,739 Continuation-In-Part US6983680B2 (en) 2002-08-28 2004-02-27 Long-piston hydraulic machines

Publications (1)

Publication Number Publication Date
US20040042906A1 true US20040042906A1 (en) 2004-03-04

Family

ID=32179426

Family Applications (1)

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US10/647,557 Abandoned US20040042906A1 (en) 2002-08-28 2003-08-25 Long-piston hydraulic machines

Country Status (10)

Country Link
US (1) US20040042906A1 (fr)
EP (1) EP1546559A4 (fr)
JP (1) JP4350038B2 (fr)
KR (1) KR100659682B1 (fr)
CN (1) CN100406726C (fr)
AU (1) AU2003265692B2 (fr)
BR (1) BR0313882A (fr)
CA (1) CA2494996C (fr)
MX (1) MXPA05002282A (fr)
WO (1) WO2004020827A2 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090077959A1 (en) * 2005-06-15 2009-03-26 Torvec, Inc. Orbital transmission with geared overdrive
US20110186302A1 (en) * 2009-12-23 2011-08-04 Bp Corporation North America Inc. Rigless low volume pump system
ITPR20120004A1 (it) * 2012-02-06 2013-08-07 Lavorwash Spa Dispositivo di lavaggio mediante un getto fluido in pressione
US8834133B2 (en) 2010-08-05 2014-09-16 Bp Corporation North America Inc. Pumping device for fluids located at the bottom of a drilled well
EP2933431A1 (fr) * 2014-04-16 2015-10-21 BP Corporation North America Inc. Pompes alternatives pour des systèmes d'assèchement de fond de trou et pistons pour de telles pompes
CN105697258A (zh) * 2014-11-25 2016-06-22 无锡市洗选设备厂 洗砂机用的柱塞泵结构
US20160222955A1 (en) * 2015-01-30 2016-08-04 Caterpillar Inc. Pump having axial cooling
US10030490B2 (en) 2014-04-16 2018-07-24 Bp Corporation North America, Inc. Reciprocating pumps for downhole deliquification systems and fluid distribution systems for actuating reciprocating pumps

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KR100943016B1 (ko) * 2005-06-15 2010-02-18 토르벡 인코포레이티드 이중 유압 머신 트랜스미션
EP2678588B1 (fr) * 2011-02-25 2021-05-05 Neo Mechanics Limited Pompe à piston axial pourvue de pistons dotés de bagues d'étanchéité métalliques
CN104153986B (zh) * 2014-07-21 2016-08-17 沃尔科技有限公司 液压回程的轴向柱塞式液压泵
IT201900024241A1 (it) * 2019-12-17 2021-06-17 Mixtron S R L Pompa a pistoni assiali a piattello inclinato
CN112664386A (zh) * 2020-12-19 2021-04-16 王建设 一种压斜式水动力机

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US2913993A (en) * 1953-05-18 1959-11-24 Ohio Commw Eng Co High temperature hydraulic pump
US3018737A (en) * 1958-01-24 1962-01-30 Ernest E Cook Pump structure
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US4776260A (en) * 1980-11-07 1988-10-11 Vincze Alexander L Constant pressure pump
US4478130A (en) * 1981-03-19 1984-10-23 Sundstrand Corporation Arrangement for slipper cavitation erosion control and impact reduction
US4637293A (en) * 1984-11-14 1987-01-20 Honda Giken Kogyo Kabushiki Kaisha Slant plate type hydraulic device
US4944154A (en) * 1986-12-09 1990-07-31 Honda Giken Kogyo Kabushiki Kaisha Hydraulically operated continuously variable transmission
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US6663354B2 (en) * 2000-11-08 2003-12-16 Linde Aktiengesellschaft Hydrostatic axial piston machine with a control port, a cradle supported swashplate and a swashplate actuating piston

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090077959A1 (en) * 2005-06-15 2009-03-26 Torvec, Inc. Orbital transmission with geared overdrive
US20110186302A1 (en) * 2009-12-23 2011-08-04 Bp Corporation North America Inc. Rigless low volume pump system
US8511390B2 (en) * 2009-12-23 2013-08-20 Bp Corporation North America Inc. Rigless low volume pump system
US8925637B2 (en) * 2009-12-23 2015-01-06 Bp Corporation North America, Inc. Rigless low volume pump system
US9127535B2 (en) 2009-12-23 2015-09-08 Bp Corporation North America Inc. Rigless low volume pump system
US8834133B2 (en) 2010-08-05 2014-09-16 Bp Corporation North America Inc. Pumping device for fluids located at the bottom of a drilled well
ITPR20120004A1 (it) * 2012-02-06 2013-08-07 Lavorwash Spa Dispositivo di lavaggio mediante un getto fluido in pressione
EP2933431A1 (fr) * 2014-04-16 2015-10-21 BP Corporation North America Inc. Pompes alternatives pour des systèmes d'assèchement de fond de trou et pistons pour de telles pompes
US10030490B2 (en) 2014-04-16 2018-07-24 Bp Corporation North America, Inc. Reciprocating pumps for downhole deliquification systems and fluid distribution systems for actuating reciprocating pumps
CN105697258A (zh) * 2014-11-25 2016-06-22 无锡市洗选设备厂 洗砂机用的柱塞泵结构
US20160222955A1 (en) * 2015-01-30 2016-08-04 Caterpillar Inc. Pump having axial cooling
US9828976B2 (en) * 2015-01-30 2017-11-28 Caterpillar Inc. Pump for cryogenic liquids having temperature managed pumping mechanism

Also Published As

Publication number Publication date
CA2494996C (fr) 2008-10-28
WO2004020827A3 (fr) 2004-05-06
BR0313882A (pt) 2005-08-02
KR100659682B1 (ko) 2006-12-21
EP1546559A2 (fr) 2005-06-29
CN100406726C (zh) 2008-07-30
WO2004020827A2 (fr) 2004-03-11
EP1546559A4 (fr) 2011-03-09
AU2003265692B8 (en) 2004-03-19
MXPA05002282A (es) 2005-08-18
AU2003265692A1 (en) 2004-03-19
JP2006510833A (ja) 2006-03-30
CN1688812A (zh) 2005-10-26
KR20050032623A (ko) 2005-04-07
CA2494996A1 (fr) 2004-03-11
AU2003265692B2 (en) 2007-05-17
JP4350038B2 (ja) 2009-10-21

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