US3602105A - Hydraulic apparatus - Google Patents

Hydraulic apparatus Download PDF

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US3602105A
US3602105A US3602105DA US3602105A US 3602105 A US3602105 A US 3602105A US 3602105D A US3602105D A US 3602105DA US 3602105 A US3602105 A US 3602105A
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cylinder
piston
fluid
casing
cylinders
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Emmet G Slusher
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Emmet G Slusher
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01BMACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/10Control of working-fluid admission or discharge peculiar thereto
    • F01B3/103Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block
    • F01B3/104Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block by turning the valve plate
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01BMACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0035Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01BMACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/0064Machine housing
    • F01B3/0067Machine housing cylinder barrel bearing means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01BMACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/007Swash plate
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01BMACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0076Connection between cylinder barrel and inclined swash plate
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01BMACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/10Control of working-fluid admission or discharge peculiar thereto
    • F01B3/103Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block
    • F01B3/108Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block by turning the swash plate (with fixed inclination)

Abstract

A hydraulic apparatus, such as a pump or motor, is contained within an elongated tubular casing having end heads closing opposite ends thereof. An elongated cylinder member is rotatably mounted within the casing and has a plurality of circumferentially spaced cylinder forming bores therein with an elongated piston member movably mounted within each bore, resilient means being arranged for urging the piston members outwardly relative to the cylinder member. Fluid intake or input and outlet flow means communicate with the cylinders for flow of fluid through the pump or motor. A cam or wobble plate is turnably supported on one end head and has piston-engaging portions in the form of a plurality of circumferentially spaced bearing members arranged to be in a plane at an acute angle to the longitudinal axis of the cylinder member whereby rotation of the cam plate effects or is in response to reciprocation of the piston members. The wobble or cam plate has portions thereon meshing with gear means on the adjacent end of the cylinder member for a positive driving connection therebetween for transmitting rotary motion between a power member and the cylinder member and cam plate.

Description

United States Patent 72] Inventor Emmet G. Slusher Primary E.mminerWilliam L. lfreeh P.O. Box 472, Higginsville, Mo. 64037 Attorney-Fishburn, Gold and Litman [211 App]. No 840,346 [22] Filed July 9,1969 [45] Patented Aug. 31,1971
ABSTRACT: A hydraulic apparatus, such as a pump or motor, [54] HYDRAULIC APPARATUS is contained within an elongated tubular casing having end 6Claims,6Drawing Figs. heads closing opposite ends thereof An elongated cylinder 91 483 member is rotatably mounted wlthin the casing and has a plu [52] cl 91/501 rality of circumferentialiy spaced cylinder forming bores 1 Cl F02) 1/02 therein with an elongated piston member movably mounted [51] nt. F041) 1/22, wnhm each bore, resilient ea s bemg arranged for urgmg the piston members outwardly relative to the cylinder 9 4 2, Flew 123/43 member Fluid intake or input and outlet flow means commumcate with the cylinders for flow of fluid through the pump or 5 k f mig motor. A cam or wobble plate is turnably supported on one UNITED STATES PATENTS end head and has piston-engaging portions in the form of a 3 plurality of circumferentially spaced bearing members ar- 1,209,995 12/1916 rd 5531/22 ranged to be in a plane at an acute angle to the longitudinal 3,265,003 8/1966 ward l axis of the cylinder member whereby rotation ofthe cam plate FOREIGN PATENT effects or is in response to reciprocation of the piston mem- 709,183 /1954 Great Britain..... 103/162 bers The wobble or cam plate has portions thereon meshing 1,007,446 10/1965 Great Britain... 103/162 with gear means on the ad acent end of the cylinder member 885,008 5/1943 France 103/162 for a positive driving connection therebetween for trans- 593,597 9/1934 Germany... 103/162 mitting rotary motion between a power member and the 622,787 6/1961 Italy 103/162 cylinder member and cam plate.
I H 3% an 4/ l l3 12 38 e 39 I8 g a l 9 I 25 a z 2 \\Zs -40 ms 431, 3M9 3, 2 5! 4H 5 Ni n y I A." w it; i a w n PATENTEUAUGBI I9?! I 3,602,105
SHEET 2 [1r 3 VENTOR. Emma Slasher BY M, 00!
A TTORNE Y6 PATENIED M1831 l97| SHEET 3 0F 3 INVENTOR. Emme+ G. Slusher 9W QJMU A TTOR NE Y6 HYDRAULIC APPARATUS The present invention relates to hydraulic motors and pumps and more particularly to axial piston-type double-acting-type motors and pumps having piston-engaging bearing members rotatably mounted in canted cam plates operatively connected to a power member and a cylinder member having opposed pistons therein.
The principal objects of the present invention are: to provide an axial piston-type hydraulic motor or pump wherein side thrust on reciprocating piston members is substantially eliminated; to provide such an axial piston-type hydraulic motor or pump having rotatably mounted bearing members in piston-engaging faces of canted cam plates for cooperative actuating relation to piston members reciprocably mounted in a rotatable cylinder member; to provide such an axial pistontype hydraulic motor or pump wherein the bearing members in the cam plate are circumferentially spaced and positioned to effect reciprocation of the piston members with resultant power transmission or pumping upon turning of the cylinder member; to provide such an axial piston-type hydraulic motor or pump wherein the cam plate is operatively connected to an adjacent end of the cylinder member and to a power member for the resultant power transmission or pumping; to provide such an axial piston-type hydraulic motor or pump wherein both the piston members and the bearing members in the cam plates are rotatable thereby providing substantially side thrust free piston members; and to provide such an axial piston-type hydraulic motor or pump which is economical to manufac' ture, easily maintained, simple in operation, positive and efficient in operation, and particularly well suited for the proposed use.
Other objects and advantages of this invention will become apparent from the following description taken in connection with the accompanying drawings wherein are set forth by way of illustration and example certain embodiments of this inven tion.
FIG. 1 is a longitudinal sectional view of a hydraulic axial piston-type motor or pump embodying features of the present invention,
FIG. 2 is a transverse sectional view through the motor or pump taken on line 22, FIG. 1, showing fluid flow means.
FIG. 3 is a longitudinal sectional view of a modified hydraulic axial piston-type motor or pump having a single cam plate.
FIG. 4 is a longitudinal sectional view of an other modified hydraulic axial piston-type motor or pump wherein an adjust-- ment disc is movable between a maximum output and an idle position.
FIG. 5 is a transverse sectional view through the modified type motor or pump taken on line 55, FIG. 4, showing fluid flow means.
FIG. 6 is a longitudinal sectional view similar to FIG. 4 ex-- cept showing the adjustment disc in the idle position.
Referring more in detail to the drawings:
The reference numeral 1 generally designates a hydraulic apparatus, such as a pump or motor, within an elongated, tubular, generally cylindrical casing 2. End heads 3 and 4 close opposite ends of the casing 2 and rotatably support cam or wobble plates 5 and 6 respectively. The cam plates each have piston-engaging portions in the form of a plurality of circumferentially spaced bearing members 7 arranged in a plane at an angle to the longitudinal axis of the casing 2 with the bearing members 7 being rotatably mounted in the cam or wobble plates 5 and 6 and positioned to engage respective outer ends of a plurality of piston members in the form of opposed piston portions 8 reciprocably mounted within cylinder forming bores 9 extending longitudinally through an elongated rotor or cylinder member 10 which is rotatably mounted within the casing 2.
In the illustrated structure, the end heads 3 and 4 each have a flange 11 for engaging the respective opposite ends of the casing 2. End plates 12 and 13 engage the flange 1 1 of the end heads 3 and 4 respectively and hold same in position closing the ends of the casing 1. The flanges 11 and the end plates 12 and 13 each have a plurality of circumferentially spaced bores 14 for receiving tie rods 15 extending therethrough for holding the end plates 12 and 13 and the end heads 3 and 4 in position tightly closing the opposite ends of the casing 2. The end heads 3 and 4 each have inner ends or faces 16 and 17 respectively positioned within the casing 2 with each inner end having an annular recess 18 and 19 therein for mounting suitable bearings 20 and 21 for rotatably supporting the cam plates 5 and 6 respectively.
One of the end heads, for example end head 3, has a bore 22 coaxially aligned with the longitudinal axis of the casing 2 and with the longitudinal axis of the rotor or cylinder member 10. The end head 3 has a counterbore 23 which has a suitable bearing 24 therein for rotatably supporting a power member 25, as later described, extending through the bore 22 and counterbore 23. The end plate 12 has a central bore 26 for permitting the power member 25 to extend therethrough and the end plate 12 engages the bearing 24 holding same in the counterbore 23.
The power member 25 also extends through a bore 27 in the cam plate 5 and in the illustrated structure, the power member 25 extends into a longitudinal axial central bore 28 of the rotor or cylinder member 10 with the power member 25 being operatively connected therein.
The other end head 4 has a bore 29 axially aligned with the central bore 28 and a counterbore 30 which has a bearing 31 therein for rotatably supporting a valve shaft 32, as later described, which extends through the bore 29 and counterbore 30 into the central bore 28 for controlling fluid circulation within the rotor or cylinder member 10. The end plate 13 has a central bore 33 for permitting the valve shaft 32 to extend therethrough and the end plate 13 engages the bearing 31 holding same in the counterbore 30, The valve shaft 32 also extends through a bore 34 through the cam plate 6.
The rotor or cylinder member 10 is illustrated as an elongated, generally cylindrical barrel structure having the cylinder forming bores 9 circumferentially spaced around the central bore 28. Suitablebearings 35 are mounted on the exterior periphery of the rotor or cylinder member 10 adjacent the opposite ends thereof and engage the inner periphery of the casing 2 for rotatably supporting same therein,
It is desirable to provide a positive connection between the rotor or cylinder member 10 and the cam plates 5 and 6 thereby substantially reducing or eliminating side thrust on the outer ends of the opposed piston portions 8. Therefore, the opposite ends respectively of the rotor or cylinder member 10 have gear teeth 36 and 37 forming ring gears adjacent the peripheral edge thereof. Gear teeth 38 and 39 are provided on the cam plates 5 and 6 respectively adjacent their peripheral edges forming ring gears meshing with the gear teeth 36 and 37 respectively, thereby providing a positive driving connection between the rotor or cylinder member 10 and the cam plates 5 and 6.
The hydraulic apparatus 1 will function as a pump when it is driven mechanically and will function as a motor when driving fluid is supplied between the pairs of opposed piston portions 8. For the purpose of illustration, the apparatus 1 will be referred to herein as a motor and the invention will be explained as applied to a motor for driving the power member 25, however, the apparatus 1 may be used as a pump for pumping fluid therethrough by driving the power member 25.
In the illustrated structure, a fluid passage 41) extends between each of the cylinder forming bores 9 and the central bore 28. Suitable fluid under pressure is delivered to the fluid passages 40 through an input or inlet flow passage 41 extending longitudinally though the valve shaft 32. The fluid passages 41) are positioned at the center of the rotor 10 and communicate with the bores 9 between the opposed piston portions 8 of the piston members. The input or inlet flow passage 41 has a port 42 which communicates with a plurality of the fluid passages 40 for supply of fluid between the opposed piston portions 8 thereby separating and urging same outwardly which turns the rotor 10 and the cam plates 5 and 6. After the rotor turns through a portion of its rotation, fluid is discharged from the cylinders 9 through the fluid passages 40 and into an outlet flow passage 43 extending longitudinally through the valve shaft 32. The outlet flow passage 43 has a port 44 which communicates with the fluid passages 40 that are not communicating with the inlet port 42 whereby fluid is continually supplied to one portion of the fluid passages 40 and discharged from the remaining portion of the fluid passages 40.
The valve shaft 32 is illustrated as an elongated tubular member having a center wall member 45 therein for defining and separating the input or inlet and outlet flow passages 41 and 43. The input or inlet port 42 is illustrated as a slotted aperture in the tubular member with the inlet slotted aperture extending between opposite edges of the center wall member 45 at one face or surface thereof. The outlet port 44 is also illustrated as a slotted aperture in the tubular member with the outlet slotted aperture extending between opposite edges of the center wall member 45 at the other face or surface thereof. The slotted apertures 42 and 44 are diametrically aligned and positioned at one end of the valve shaft 32.
When the apparatus 1 is operated as a motor, the power member 25 is driven or rotated through its connection with the rotor or cylinder member 10 and the power member 25 is illustrated as an elongated shaft projecting through and journaled in the end head 3, as previously described, and projecting coaxially into the central bore 23 in the rotor 10 where one end thereof is operatively connected thereto as by being splined to the rotor or cylinder member 10, as indicated at 46, for transmission of rotary motion from the rotor or cylinder member 10 to the power member 25.
The opposed piston portions 8 are movably and rotatably mounted within the cylinder formingbores 9 and the piston portions 8 each have outer ends 47 thereof projecting beyond the outer or opposite ends of the rotor or cylinder member 10. It is desirable to provide firm engagement between the cam plates 5 and 6 and the outer ends 47 of the opposed piston portions 8 with the outer ends 47 firmly engaging the bearing members 7 with no direct connection therebetween. Therefore, suitable resilient members, such as heavy-duty, helical compression springs 48. are mounted within recesses 49 within facing ends of each of the opposed piston portions 8 with the springs 48 being sized and wound to be under a load at all times thereby tending to separate the opposed piston portions 8 and urging the outer ends 47 thereof outwardly from the respective opposite ends of the cylinder forming bores 9.
The bearing members 7 are each illustrated as a roller 50 mounted on an elongated axle 51 with opposite ends of the axle 51 being rotatably mounted in spaced ears 52 extending outwardly from each of the cam or wobble plates 5 and 6. The rollers 50 are arranged to be in a plane canted at an acute angle with the longitudinal axis of the cylinder member 10 whereby rotation of the cam or wobble plates and rotation of the cylinder member 10 effects or is in response to reciprocation of the opposed piston portions 8 within the bores 9. The outer ends 47 of the opposed piston portions 8 are shaped to provide smooth relative movement while in contact with the rollers 50. thereby substantially reducing or eliminating side thrust on the opposed piston portions 8.
The cam plates 5 and 6 are positioned in canted and opposed but symmetrically acute angled relation with the Ion gitudinal axis of the rotor or cylinder member 10 with the surface of the piston-engaging face of the cam plates 5 and 6 intersecting the longitudinal axis of the central bore 28 diagonally and in opposed but symmetrical relation.
For maximum output, the supply input or intake port 42 for the intake fluid passage 41 is directed toward the fluid passage 40 communicating with the cylinder 9 having the opposed piston portions 8 therein positioned in the closest relation and with the cylinders 9 having the opposed piston portions 8 moving outwardly or in their expanding stroke. For maximum output, the outlet port 44 for the outlet fluid passage 43 is aligned with the fluid passage 40 communicating with the cylinder 9 having the opposed piston portions 8 in their farthest apart relation and with the cyiinders 9 having the opposed piston portions 8 moving inwardly or in their retracting stroke. In the illustrated structure, the top cylinder 9, as seen in FIGS. 1 and 2, has the piston portions 8 at their closest together position and will be referred to as top dead center and the bottom cylinder 9, as seen in FIGS. 1 and 2, has the piston portions 8 at their farthest apart position and will be referred to as bottom dead center.
To vary the output of the motor 1, the valve shaft 32 is rotated within the central bore 28, as by a handle 53, mounted on the other or exterior end of the valve shaft 32. When the center wall member 45 extends between top dead center and bottom dead center and the inlet flow passage 41 is on the right, as seen in FIG. 2, the rotor 10 will turn in a clockwise direction, as seen in FIG. 2. When the central wall member 45 is rotated clockwise or counterclockwise, as seen in FIG. 2, the driving force on the rotor 10 will reduce until rotation stops and then reverses. When the center wall member 45 is horizontal and the intake flow passage 41 is at the top, as seen in FIG. 2, rotation will be at one-half speed and one-half torque. When the center wall member 45 is horizontal and the intake flow passage 41 is at the bottom, as seen in FIG. 2, the driving force on the rotor or cylinder member 10 will be a minimum or zero.
Fluid is supplied to the input or intake fluid passage 41 through a suitable conduit 54 thereby rotating the rotor or cylinder member 10 by urging the opposed piston portions 8 apart. Rotation of the cylinder member 10 returns the fluid through the outlet fluid passage 43 to a suitable conduit 55 and rotation of the rotor or cylinder member 10. drives the power member 25 for transmission of power to a using apparatus (not shown). The cam plates 5 and 6 are each turned in the same direction or follow the rotation of the cylinder member 10 through the interengaging of the gear teeth. The power member 25 may be rotated clockwise or counterclockwise by the positioning of the valve shaft 32 with a larger portion of the intake or input port 42 of the intake or input flow passage 41 to the right or left respectively of top dead center, as seen in FIG. 2.
FIG. 3 illustrates a modified hydraulic apparatus, such as a pump or motor 66, within an elongated, tubular, generally cylindrical casing 61. An end head 62 closes one end of the casing 61 and rotatably supports a cam or wobble plate 63 therein. Bearing members 64 are mounted on the cam plate 63 and arranged in a plane at an angle to the longitudinal axis of the casing 61 with the bearing members being rotatably mounted on the cam plate 63 and positioned to engage respective outer ends of a plurality of piston members 65 reciprocably mounted within cylinder forming bores 66 extending longitudinally into an elongated rotor or cylinder member 67 which is rotatably mounted within the casing 61.
In the illustrated structure, the end head 62 has a flange 68 engaging one end of the casing 61 for closing same. An end plate 6? engages the flange 68 to hold suitable bearing members 70, as later described, within the end head 62. An end plate 71 engages and closes the other end of the casing 61. The end plate 69 and'end head 62 are maintained in a closing relation with the one end of the casing 61 and the end plate 71 is maintained in a closing relation with the other end of the casing 61 by a plurality of tie rods 72 extending therethrough.
The cam plate 63 is canted at an acute angle with the iongitudinal axis of the casing 61 and has a ring gear 73 adjacent the peripheral edge of the cam or wobble plate 63 for meshing with a ring gear 74 on an adjacent end and adjacent a peripheral edge of the rotor or cylinder member 67, thereby providing a positive driving connection between the rotor or cylinder member 67 and the cam or wobble plate 63.
In the illustrated structure, the cylinder forming bores 66 are recesses extending into the rotor or cylinder member 67. The bores or recesses 66 have an end recess 75 of reduced diameter to form a socket for receiving one end of an -elon'- gated spring 76. The other end of the elongated spring 76 is received within a recess 77 within the piston members 65 for urging same outwardly from the rotor or cylinder member 67 thereby maintaining the piston members 65 in firm engagement with the bearing members 64.
A valve shaft 78, similar to valve shaft 32, it rotatably sup ported in the end plate 71 for supplying fluid to and receiving fluid from the bores 66 in the rotor 67 and for controlling the direction of rotation of the rotor 67 and the speed and torque produced by the rotation thereof.
A power member 79, similar to power member 25, is rotatably supported in the bearing members 70 within the end head 62 and is operatively connected to the rotor 67 whereby the power member 79 is rotated by the rotor 67 when the modified hydraulic apparatus 60 is operated as a motor and the power member 79 rotates the rotor 67 when the modified hydraulic apparatus 60 is operated as a pump.
FIGS. 4, 5 and 6 illustrate a further modified hydraulic apparatus, such as a pump or motor80, mounted within an elongated, generally cylindrical, tubular casing 81 having an input or intake port 82 communicating with an input or intake channel 83 in the interior periphery of the casing 81 thereby defining an input or intake chamber. The casing 81 has an outlet port 84 also communicating with an outlet channel 85 within the inner periphery of the casing 81 thereby defining an outlet chamber.
An elongated rotor or cylinder member 86 is concentric within and rotatably mounted within the casing 81 and has a plurality of circumferentially spaced cylinder forming bores 87 extending longitudinally therethrough. A fluid or flow passage 88 extends between each of the cylinder forming bores 37 and an exterior periphery of the rotor or cylinder member 86 for communication with the respective intake and outlet channels 83 and 85. The channels 83 and 85 are concentric with the outer periphery of the rotor or cylinder member 86 for compactness of the casing 81 and smoothflow of the fluid through the further modified hydraulic apparatus 80.
End heads 89 and 90 close opposite ends of the casing 81, and one of the end heads, for example end head 90, has an adjustment disc 91 rotatably mounted therein with an axial shaft 92 extending outwardly therefrom through a bore 93 in the one end head 90. The adjustment disc 91 has an annular recess 94 in an inner face thereof to rotatably support a cam plate 95, as by bearings 96 mounted therein.
The cam plate 95 and a cam plate 97 which is rotatably mounted in the other end head 89 are normally canted at opposed but symmetrically, acutely angled relation with the longitudinal axis of the rotor or cylinder member 86 and with their respective inner or piston-engaging faces intersecting the longitudinal axis of the rotor or cylinder member 86 diagonally and in opposed but symmetrical relation. The cam plate 97 has a shoulder 98 for engaging a bearing 99 mounted within an annular recess 100 in one end of the other end head 89 for rotatably supporting same therein.
A power member 101 extends outwardly from the shoulder 98 and is rotatably supported in the other end head 89, as by bearings 102 mounted in an annular recess 103 in the other end of the other end head 89. A closure flange 1 engages the other end of the other end head 89 and has a central bore 195 through which the power member 101 extends and the closure flange 1041 has a plurality of circumferentially spaced bores 106 aligned with an equal number of bores 107 through a flange 108 at the one end of the other end head 89. Each of the bores 106 and 107 are aligned with respective threaded sockets 109 in the casing 81 whereby a tie rod 110 is mounted 'CIIICQCII of the aligned bores and threaded sockets to secure the closure flange 104 in engagement with the other end of the other end head 89 thereby tightly closing same.
The adjustment disc 91 and the cam plate 95 rotatably carried therein are adjustable to position said cam plate 95 in a position parallel with the other cam plate 97 whereby when the modified hydraulic apparatus is employed as a pump and it is desired to stop the pumping action thereof without stopping relative rotation of its parts, the adjustment disc 91 is rotated 180 whereby the cam plates 95 and 97 are parallel, as
shown in FIG. 6. In this position, pairs of opposed pistons 111 shift back and forth within the cylinder forming bores 87 with the turning of the rotor or cylinder member 86. However, there is no relative axial motion between the opposed pistons 111 with the result that no pumping occurs even though the power member 101 continues to be driven.
In the illustrated structure, the axial shaft 92 has a suitable handle 112 mounted thereon for turning the adjustment disc 91 to vary the relation between the cam plates 95 and 97 thereby adjusting the output of the modified hydraulic apparatus 80 between the maximum output position and the parallel or idle position.
The cam plates 95 and 97 each have ring gears 113 and 1141 respectively adjacent their respective peripheral edges for meshing with ring gears 115 and 116 on respective adjacent ends of the rotor or cylinder member 86 thereby providing a positive driving connection between the rotor 86 and the wobble or cam plates 95 and 97. A grooved recess or way 117 extends into a portion of the inner periphery of the casing 81 to provide clearance for the teeth forming the ring gear 114 during turning of the cam or wobble plate 97.
In the structure illustrated in FIGS. 4 and 6, the ring gear 114 is flush with an upper portion of the inner periphery of the casing 81 and the way 117 extends around the lower portion of inner periphery of the casing 81. The end head is sized to permit clearance for the ring gear 113 during turning of the cam or wobble plate while in the position shown in FIG. 1 or the position shown in FIG. 6 or any position therebetween without the necessity of providing a grooved recess or way.
It is to be understood that, while I have illustrated and described certain forms of my invention, it is not to be limited to these specific forms or arrangement of parts herein described and shown.
What I claim and desire to secure by Letters Patent is:
A hydraulic apparatus comprising:
an elongated tubular casing;
. end heads closing opposite ends of said casing;
. an elongated cylinder member rotatably mounted within said casing;
d. a plurality of circumferentially spaced cylinder forming bores in said cylinder member with said cylinder forming bores extending longitudinally through said cylinder member;
e. an elongated piston member mounted within each of said cylinders, said piston members each having at least one end thereof extending beyond one end of said cylinder member; said piston members each having a pair of opposed piston portions mounted within each of said cylinders, said piston portions each having one end thereof extending beyond a respective end of said cylinder member; fluid intake flow means positioned for communicating with said cylinders during a portion of the rotation of said cylinder member for urging said piston members out wardly;
g. fluid outlet flow means positioned for communicating with said cylinders during another portion of the rotation of said cylinder member for escape of fluid during inwardly movement of said piston members;
h. a cam plate turnably mounted on one of said end heads and having piston-engaging portions arranged in a plane canted at an acute angle relative to "the longitudinal axis of said casing, each of said end heads having a cam plate turnably supported thereon;
. said piston-engaging portions of each of said cam plates are a plurality of circumferentially spaced bearing members rotatably mounted in each of said cam plates and positioned to engage said respective ends of said piston portions beyond said respectivecylinders;
j. said bearing members at said cam plates are arranged in planes canted at opposed but symmetrically acutely angled relation with the longitudinal axis of the cylinder member with said respective plane intersecting the iongitudinal axis of said cylinder member diagonally and in opposed but symmetrical relation;
k. gear means associated with said cam plate and said one end of said cylinder member and having meshing engagement for turning said cam plate with said cylinder member, said gear means being associated with each of said cam plates and with opposite ends of said cylinder member, said gear means on said cam plates meshing with said gear means on said respective opposite ends of said cylinder member for turning of said cam plate with said cylinder member, said gear means urging each of said cam plates to follow the rotation of said cylinder member whereby said opposed piston portions of said piston members are reciprocated toward and away from each other within said respective cylinders;
l. a power member operatively connected to said cylinder member for transmission of rotary motion therebetween.
. The hydraulic apparatus as set forth in claim 1 wherein:
. said cylinder member has a central bore extending longitudinally therethrough;
b. said cylinder member has a fluid passageway extending between said central bore and each of said cylinder forming bores, said fluid passageways communicating with said respective cylinders at a point between said opposed piston portions;
c. said cam plates are maintained at fixed angular relation with the longitudinal axis of the cylinder member;
d. said fluid intake flow means and said fluid outlet flow means include an elongated tubular valve shaft coaxially and rotatably mounted within said central bore and having inlet and outlet flow passages extending longitudinally therethrough, said inlet and outlet flow passages being separated by a center wall member and each having a port communicating with a plurality of said fluid passageways in said cylinder member; and
c. said valve shaft has adjustment means associated therewith for selectively positioning said inlet and outlet ports thereby controlling operation of the hydraulic apparatus.
3. The hydraulic apparatus as set forth in claim 1 including:
a. an adjustment disc turnably mounted within one of said end heads and having one of said cam plates rotatably supported thereon; and
b. means associated with said adjustment disc for turning same between a maximum output position and an idle position, said maximum output position having said cam plates canted at an opposed but symmetrically acutely angled relation with the longitudinal axis of said cylinder member, said idle position having said cam plates canted in a parallel relation whereby there is no relative axial motion between said piston portions.
4. The hydraulic apparatus as set forth in claim 3 wherein:
at said power member is an elongated shaft extending outwardly from the other of said cam plates whereby rotation of said cylinder member is transferred to said shaft.
5. The hydraulic apparatus as set forth in claim 3 wherein said fluid intake flow means and said fluid outlet flow means include:
a. an inlet flow channel in an interior surface of said tubular casing, said inlet flow channel being concentric with said cylinder member and extending around a portion of said interior surface of said tubular casing;
b. an outlet flow channel in said interior surface of said tu bular casing, said outlet flow channel being concentric with said cylinder member and peripherally aligned with said inlet flow channel, said outlet flow channel being separated from said inlet flow channel and extending around an other portion of said interior surface of said tubular casing; c. a fluid passageway extending between each of said cylinder forming bores and an exterior' surface of said cylinder member; d. an inlet port extending through said tubular casing and communicating with said inlet flow channel; and an outlet port extending through said tubular casing and communicating with said outlet flow channel. 6. A hydraulic apparatus comprising: a. an elongated tubular casing; b
. end heads closing opposite ends of said casing; an elongated cylinder member rotatably mounted within said casing;
d. a plurality of circumferentially spaced cylinder forming bores in said cylinder member;
. an elongated piston member mounted within each of said cylinders, said piston members each having at least one end thereof extending'beyond one end of said cylinder member;
. fluid intake flow means positioned for communicating with said cylinders during a portion of the rotation of said cylinder member for urging said piston members outwardly;
g. fluid outlet flow means positioned for communicating with said cylinders during another portion of the rotation of said cylinder member for escape of fluid during inwardly movement of said piston members;
h. a cam plate turnably mounted on one of said end heads and having piston-engaging portions arranged in a plane canted at an acute angle relative to the longitudinal axis of said casing;
. said piston-engaging portions of said cam plate are a plurality of circumferentially spaced bearing members rotatably mounted on said cam plate and positioned to engage said end of said piston members beyond said respective cylinders;
j. said bearing members each including a pair of ears mounted on said respective cam plate and extending outwardly therefrom, an elongated axle rotatably mounted on said ears, and a roller mounted on said axle for engaging said respective ends of said piston members beyond ends of said respective cylinders;
k. gear means associated with said cam plate and said one end of said cylinder member and having meshing engage ment for turning said cam plate with said cylinder member, said gear means urging said cam plate to follow the rotation of said cylinder member whereby said piston members are reciprocated within said respective cylinders;
l. a power member operatively connected to said cylinder member for transmission of rotary motion therebetween.

Claims (6)

1. A hydraulic apparatus comprising: a. an elongated tubular casing; b. end heads closing opposite ends of said casing; c. an elongated cylinder member rotatably mounted within said casing; d. a plurality of circumferentially spaced cylinder forming bores in said cylinder member with said cylinder forming bores extending longitudinally through said cylinder member; e. an elongated piston member mounted within each of said cylinders, said piston members each having at least one end thereof extending beyond one end of said cylinder member; said piston members each having a pair of opposed piston portions mounted within each of said cylinders, said piston portions each having one end thereof extending beyond a respective end of said cylinder member; f. fluid intake flow means positioned for communicating with said cylinders during a portion of the rotation of said cylinder member for urging said piston members outwardly; g. fluid outlet flow means positioned for communicating with said cylinders during another portion of the rotation of said cylinder member for escape of fluid during inwardly movement of said piston members; h. a cam plate turnably mounted on one of said end heads and having piston-engaging portions arranged in a plane canted at an acute angle relative to the longitudinal axis of said casing, each of said end heads having a cam plate turnably supported thereon; i. said piston-engaging portions of each of said cam plates are a plurality of circumferentially spaced bearing members rotatably mounted in each of said cam plates and positioned to engage said respective ends of said piston portions beyond said respective cylinders; j. said bearing members at said cam plates are arranged in planes canted at opposed but symmetrically acutely angled relation with the longitudinal axis of the cylinder member with said respective plane intersecting the longitudinal axis of said cylinder member diagonally and in opposed but symmetrical relation; k. gear means associated with said cam plate and said one end of said cylinder member and having meshing engagement for turning said cam plate with said cylinder member, said gear means being associated with each of said cam plates and with opposite ends of said cylinder member, said gear means on said cam plates meshing with said gear means on said respective opposite ends of said cylinder member for turning of said cam plate with said cylinder member, said gear means urging each of said cam plates to follow the rotation of said cylinder member whereby said opposed piston portions of said piston members are reciprocated toward and away from each other within said respective cylinders; l. a power member operatively connected to said cylinder member for transmission of rotary motion therebetween.
2. The hydraulic apparatus as set forth in claim 1 wherein: a. said cylinder member has a central bore extending longitudinally therethrough; b. said cylinder member has a fluid passageway extending between said central bore and each of said cylinder forming bores, said fluid passageways communicating with said respective cylinders at a point between said opPosed piston portions; c. said cam plates are maintained at fixed angular relation with the longitudinal axis of the cylinder member; d. said fluid intake flow means and said fluid outlet flow means include an elongated tubular valve shaft coaxially and rotatably mounted within said central bore and having inlet and outlet flow passages extending longitudinally therethrough, said inlet and outlet flow passages being separated by a center wall member and each having a port communicating with a plurality of said fluid passageways in said cylinder member; and e. said valve shaft has adjustment means associated therewith for selectively positioning said inlet and outlet ports thereby controlling operation of the hydraulic apparatus.
3. The hydraulic apparatus as set forth in claim 1 including: a. an adjustment disc turnably mounted within one of said end heads and having one of said cam plates rotatably supported thereon; and b. means associated with said adjustment disc for turning same between a maximum output position and an idle position, said maximum output position having said cam plates canted at an opposed but symmetrically acutely angled relation with the longitudinal axis of said cylinder member, said idle position having said cam plates canted in a parallel relation whereby there is no relative axial motion between said piston portions.
4. The hydraulic apparatus as set forth in claim 3 wherein: a. said power member is an elongated shaft extending outwardly from the other of said cam plates whereby rotation of said cylinder member is transferred to said shaft.
5. The hydraulic apparatus as set forth in claim 3 wherein said fluid intake flow means and said fluid outlet flow means include: a. an inlet flow channel in an interior surface of said tubular casing, said inlet flow channel being concentric with said cylinder member and extending around a portion of said interior surface of said tubular casing; b. an outlet flow channel in said interior surface of said tubular casing, said outlet flow channel being concentric with said cylinder member and peripherally aligned with said inlet flow channel, said outlet flow channel being separated from said inlet flow channel and extending around an other portion of said interior surface of said tubular casing; c. a fluid passageway extending between each of said cylinder forming bores and an exterior surface of said cylinder member; d. an inlet port extending through said tubular casing and communicating with said inlet flow channel; and e. an outlet port extending through said tubular casing and communicating with said outlet flow channel.
6. A hydraulic apparatus comprising: a. an elongated tubular casing; b. end heads closing opposite ends of said casing; c. an elongated cylinder member rotatably mounted within said casing; d. a plurality of circumferentially spaced cylinder forming bores in said cylinder member; e. an elongated piston member mounted within each of said cylinders, said piston members each having at least one end thereof extending beyond one end of said cylinder member; f. fluid intake flow means positioned for communicating with said cylinders during a portion of the rotation of said cylinder member for urging said piston members outwardly; g. fluid outlet flow means positioned for communicating with said cylinders during another portion of the rotation of said cylinder member for escape of fluid during inwardly movement of said piston members; h. a cam plate turnably mounted on one of said end heads and having piston-engaging portions arranged in a plane canted at an acute angle relative to the longitudinal axis of said casing; i. said piston-engaging portions of said cam plate are a plurality of circumferentially spaced bearing members rotatably mounted on said cam plate and positioned to engage said end of said piston members beyond said respective cylinders; j. said bearing members Each including a pair of ears mounted on said respective cam plate and extending outwardly therefrom, an elongated axle rotatably mounted on said ears, and a roller mounted on said axle for engaging said respective ends of said piston members beyond ends of said respective cylinders; k. gear means associated with said cam plate and said one end of said cylinder member and having meshing engagement for turning said cam plate with said cylinder member, said gear means urging said cam plate to follow the rotation of said cylinder member whereby said piston members are reciprocated within said respective cylinders; l. a power member operatively connected to said cylinder member for transmission of rotary motion therebetween.
US3602105D 1969-07-09 1969-07-09 Hydraulic apparatus Expired - Lifetime US3602105A (en)

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DE3142990A1 (en) * 1980-10-31 1982-06-16 Honda Motor Co Ltd HYDRAULIC DEVICE WITH SWASHPLATE
US4478557A (en) * 1982-03-05 1984-10-23 Messier-Hispano-Bugatti(S.A.) Hydraulic power transducer
US4487108A (en) * 1982-09-23 1984-12-11 Mcluen Carl T Variable displacement pump/motor
US4770084A (en) * 1986-04-23 1988-09-13 Mitsubishi Jukogyo Kabushiki Kaisha Parallel swash plate type fluid machines
US4854826A (en) * 1987-05-15 1989-08-08 Linde Aktiengesellschaft Assembly of a primary power source and several axial piston pumps flanged on it
US5109754A (en) * 1990-06-13 1992-05-05 Shaw Edwin L High torque low speed motor
US5423183A (en) * 1991-01-14 1995-06-13 Advanced Power Technology, Inc. Hydraulic machine with wedge-shaped swashplate
US5524437A (en) * 1995-01-30 1996-06-11 Martin Marietta Corporation Continuously variable hydrostatic transmission having ratio controller actuating components incorporated in output shaft
US5535589A (en) * 1995-01-30 1996-07-16 Martin Marietta Corporation Ratio controller for continuously variable hydrostatic transmission
US5540048A (en) * 1995-01-30 1996-07-30 Martin Marietta Corporation Continuously variable hydrostatic transmission including a pulse width modulation ratio controller
US6109034A (en) * 1997-04-25 2000-08-29 General Dynamics Land Systems, Inc. Continuously variable hydrostatic transmission ratio controller capable of generating amplified stroking forces
US20050207921A1 (en) * 2000-01-10 2005-09-22 Gov't of the U.S.A. as represented by the Adm. of the U.S. Environmental Protection Agency Opposing pump/motors
US20070278027A1 (en) * 2000-01-10 2007-12-06 Government Of Usa, As Represented By The Administ. Of The U.S. Environmental Protection Agency Hydraulic hybrid vehicle with integrated hydraulic drive module and four-wheel-drive, and method of operation thereof
US20080314039A1 (en) * 2000-01-10 2008-12-25 Gov Of The U.S.A, As Rep By The Admn Of The U.S. Environmental Protection Agency Hydraulic hybrid vehicle with integrated hydraulic drive module and four-wheel-drive, and method of operation thereof
US20110165001A1 (en) * 2005-03-25 2011-07-07 Arash Kheradvar Helically actuated positive-displacement pump and method
US9125655B2 (en) 2010-07-16 2015-09-08 California Institute Of Technology Correction and optimization of wave reflection in blood vessels
US9656009B2 (en) 2007-07-11 2017-05-23 California Institute Of Technology Cardiac assist system using helical arrangement of contractile bands and helically-twisting cardiac assist device

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Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3142990A1 (en) * 1980-10-31 1982-06-16 Honda Motor Co Ltd HYDRAULIC DEVICE WITH SWASHPLATE
US4478557A (en) * 1982-03-05 1984-10-23 Messier-Hispano-Bugatti(S.A.) Hydraulic power transducer
US4487108A (en) * 1982-09-23 1984-12-11 Mcluen Carl T Variable displacement pump/motor
US4770084A (en) * 1986-04-23 1988-09-13 Mitsubishi Jukogyo Kabushiki Kaisha Parallel swash plate type fluid machines
US4854826A (en) * 1987-05-15 1989-08-08 Linde Aktiengesellschaft Assembly of a primary power source and several axial piston pumps flanged on it
US5109754A (en) * 1990-06-13 1992-05-05 Shaw Edwin L High torque low speed motor
US5423183A (en) * 1991-01-14 1995-06-13 Advanced Power Technology, Inc. Hydraulic machine with wedge-shaped swashplate
US5575152A (en) * 1991-01-14 1996-11-19 Martin Marietta Corporation Hydraulic machine with wedge-shaped swashplate
US5524437A (en) * 1995-01-30 1996-06-11 Martin Marietta Corporation Continuously variable hydrostatic transmission having ratio controller actuating components incorporated in output shaft
US5535589A (en) * 1995-01-30 1996-07-16 Martin Marietta Corporation Ratio controller for continuously variable hydrostatic transmission
US5540048A (en) * 1995-01-30 1996-07-30 Martin Marietta Corporation Continuously variable hydrostatic transmission including a pulse width modulation ratio controller
US6109034A (en) * 1997-04-25 2000-08-29 General Dynamics Land Systems, Inc. Continuously variable hydrostatic transmission ratio controller capable of generating amplified stroking forces
US20050207921A1 (en) * 2000-01-10 2005-09-22 Gov't of the U.S.A. as represented by the Adm. of the U.S. Environmental Protection Agency Opposing pump/motors
US20070278027A1 (en) * 2000-01-10 2007-12-06 Government Of Usa, As Represented By The Administ. Of The U.S. Environmental Protection Agency Hydraulic hybrid vehicle with integrated hydraulic drive module and four-wheel-drive, and method of operation thereof
US20080314039A1 (en) * 2000-01-10 2008-12-25 Gov Of The U.S.A, As Rep By The Admn Of The U.S. Environmental Protection Agency Hydraulic hybrid vehicle with integrated hydraulic drive module and four-wheel-drive, and method of operation thereof
US7537075B2 (en) 2000-01-10 2009-05-26 The United States Of America, As Represented By The Administrator Of The U.S. Environmental Protection Agency Hydraulic hybrid vehicle with integrated hydraulic drive module and four-wheel-drive, and method of operation thereof
US7617761B2 (en) * 2000-01-10 2009-11-17 The United States of America as represented by the Administrator of the US Environmental Protection Agency Opposing pump/motors
US8162094B2 (en) 2000-01-10 2012-04-24 The United States Of America, As Represented By The Administrator Of The U.S. Environmental Protection Agency Hydraulic hybrid vehicle with large-ratio shift transmission and method of operation thereof
US7984783B2 (en) 2000-01-10 2011-07-26 The United States Of America As Represented By The Administrator Of The U.S. Environmental Protection Agency Hydraulic hybrid vehicle with integrated hydraulic drive module and four-wheel-drive, and method of operation thereof
US20110232418A1 (en) * 2000-01-10 2011-09-29 Government Of The United States Of America, As Represented By The Administrator Of The U.S. Epa Hydraulic hybrid vehicle with large-ratio shift transmission and method of operation thereof
US20110165001A1 (en) * 2005-03-25 2011-07-07 Arash Kheradvar Helically actuated positive-displacement pump and method
US8794937B2 (en) * 2005-03-25 2014-08-05 California Institute Of Technology Helically actuated positive-displacement pump and method
US9656009B2 (en) 2007-07-11 2017-05-23 California Institute Of Technology Cardiac assist system using helical arrangement of contractile bands and helically-twisting cardiac assist device
US9125655B2 (en) 2010-07-16 2015-09-08 California Institute Of Technology Correction and optimization of wave reflection in blood vessels

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