WO2018205015A1 - Variateur hydrostatique basé sur des machines à pistons radiaux - Google Patents

Variateur hydrostatique basé sur des machines à pistons radiaux Download PDF

Info

Publication number
WO2018205015A1
WO2018205015A1 PCT/CA2018/050528 CA2018050528W WO2018205015A1 WO 2018205015 A1 WO2018205015 A1 WO 2018205015A1 CA 2018050528 W CA2018050528 W CA 2018050528W WO 2018205015 A1 WO2018205015 A1 WO 2018205015A1
Authority
WO
WIPO (PCT)
Prior art keywords
radial
control plate
hydrostatic
cylinder block
plate element
Prior art date
Application number
PCT/CA2018/050528
Other languages
English (en)
Inventor
Gerald Dyck
Paul Dries
Derek SCHEPER
Ron SCHEPER
John Czepak
Original Assignee
Kinetics Drive Solutions 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
Application filed by Kinetics Drive Solutions Inc. filed Critical Kinetics Drive Solutions Inc.
Publication of WO2018205015A1 publication Critical patent/WO2018205015A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
    • F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
    • F01B13/06—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement
    • F01B13/061—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with the actuated or actuating element being at the outer ends of the 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F04B1/0535—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders the piston-driving cams being provided with inlets and outlets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H39/00—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution
    • F16H39/04—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit
    • F16H39/06—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type
    • F16H39/26—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type with liquid chambers not shaped as bodies of revolution or shaped as bodies of revolution eccentric to the main axis of the gearing
    • F16H39/30—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type with liquid chambers not shaped as bodies of revolution or shaped as bodies of revolution eccentric to the main axis of the gearing with liquid chambers formed in stationary members
    • F16H39/32—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type with liquid chambers not shaped as bodies of revolution or shaped as bodies of revolution eccentric to the main axis of the gearing with liquid chambers formed in stationary members with sliding vanes carried by the rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/12—Differential gearings without gears having orbital motion
    • F16H48/18—Differential gearings without gears having orbital motion with fluid gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
    • F16H61/423—Motor capacity control by fluid pressure control means

Definitions

  • the present invention pertains to hydrostatic drive systems which are also known as variators. Background
  • Modern hydrostatic drive systems typically consist of at least two hydraulic machines or units fluidly coupled to each other.
  • One hydraulic unit may function as the pump and the other as the motor, or vice versa.
  • a hydrostatic drive system can also function as the variator in a power split, infinitely variable transmission or IVT such as disclosed in US 7,357,744.
  • Positive displacement hydraulic units can be of vane, plunger, diaphragm or piston designs. Bent axis piston hydraulic machines have become common in many hydrostatic drive systems such as the Fendt (AGCO) Vario Transmission or as disclosed in US 8,240,145.
  • a hydrostatic radial piston machine has a rotating cylinder block with multiple radial cylinder bores.
  • the cylinder block is connected to a drive shaft.
  • a fixed central pintle contains fluid passages and radial ports exposed to the cylinder bores.
  • the inner ends of the cylinder bores are alternately in fluid communication first with one set of passages, then the other.
  • the outer ends of the pistons ride in an eccentric cam ring resulting in the pistons moving up and down in the cylinder bores as the block rotates.
  • An example of this type of design is disclosed in US 3,750,533.
  • drawbacks of this design are the limited size of fluid channels in the pintle and high bending loads in the pintle.
  • Other drawbacks include the high tolerances between pintle shaft and rotor for sealing which can create intolerance to thermal differentials between the two elements causing thermal shock seizures and catastrophic failure. Reducing the clearance to compensate however increases the leakage. In effect, there is no way to compensate at this interface both for leakage and potential seizure.
  • a further drawback for this design is an inability to have an additional through shaft in the middle of the machine which is important for packaging of split path IVTs.
  • the drive shaft is only required to transmit torque and the absence of a pintle allows room for an additional through shaft.
  • the new design also compensates for thermal differentials reducing or eliminating the potential for seizure type failure of the pintle design. With the absence of rolling bearings, the new design is also simpler than previous designs creating potential for cost savings.
  • the aforementioned new hydrostatic radial piston machine comprises a housing, a radial cylinder block rotatably supported in the housing about a rotation axis, a plurality of pistons which corresponds to the plurality of bores, a cam ring which is arranged eccentric relative to the radial cylinder block and which circumferentially envelops the radial cylinder block, two control plate elements including a total of at least two control cross-sections, and a plurality of pass through channels in the radial cylinder block corresponding to the plurality of bores in the radial cylinder block.
  • the radial cylinder block includes a plurality of bores extending from an outer enveloping surface of the radial cylinder block into an interior of the radial cylinder block and arranged distributed over a circumference of the radial cylinder block.
  • the plurality of pistons are movably supported in the bores and respectively define an operating cavity for a hydraulic fluid together with the associated bore.
  • ends of the pistons oriented away from the radial cylinder block are movably supported at a continuously cambered inner enveloping surface of the cam ring during a rotation of the radial cylinder block.
  • at least one control cross-section is connected with an inlet channel and at least another control cross-section is connected with an outlet channel.
  • the two control plate elements extend respectively with a face oriented towards a central plane of the radial cylinder block, in which the central plane is perpendicular to the rotation axis, and the two control plate elements extend with the faces oriented towards the radial cylinder block beyond a plane which is defined by a face of the radial cylinder block, in which the face of the radial cylinder block is oriented towards the respective control plate element at a greatest axial width of the radial cylinder block.
  • the plurality of pass through channels as a function of a rotational position of the cylinder block in the cam ring respectively connect the operating cavity with the control cross-section corresponding with the inlet channel or with the control cross-section corresponding with the outlet channel or are closable by a closing surface arranged at the control plate element, in which each control plate element includes a radial bearing portion in which radial forces from the radial cylinder block are transferrable to a respective opposite radial surface in the housing or to a radial surface of a housing cover supported in the housing through a direct contact of the radial bearing portion with the radial surface.
  • the aforementioned new hydrostatic radial piston machine has a housing, a cylinder star which is mounted in the housing such that it can rotate about a rotation axis and has a number of bores which extend starting from an outer lateral surface of the cylinder star into the interior thereof and are distributed over the circumference thereof.
  • the hydrostatic radial piston machine also has a number of pistons corresponding to the number of bores which are arranged in a displaceable manner in the bores and each delimit a working space for a hydraulic fluid together with the associated bore.
  • the hydrostatic radial piston machine also has a lifting ring which is arranged eccentrically to the cylinder star and surrounds the cylinder star in a circumferential manner, and on the inner lateral surface of which ends of the pistons which face away from the cylinder star are supported in a movable manner during the rotary movement of the cylinder star.
  • the hydrostatic radial piston machine has two control mirror bodies which have at least two control cross sections in total, of which at least one is connected to the inlet duct and at least one other is connected to the outlet duct, wherein both control mirror bodies each extend with an end face facing the cylinder star towards a central plane of the cylinder star, which plane is perpendicular to the rotation axis, beyond a plane which is defined by an end face of the cylinder star facing the respective control mirror body at the point of the cylinder star with the greatest axial width.
  • the hydrostatic radial piston machine has a number which corresponds to the number of bores in the cylinder star of through-ducts which are arranged in the latter and, depending on the rotation position of the cylinder star in the lifting ring, each connect a working space to a control cross section which corresponds to the inlet duct or to a control cross section which corresponds to the outlet duct or can be closed by a closure face which is situated on the control mirror body, characterised in that each control mirror body has a bearing region in which radially effective forces can be transmitted to a respective counter face in the housing or a housing cover mounted therein.
  • US 5,228,290 discloses a variator consisting of 2 hydraulic radial piston machines fluidly coupled together.
  • the hydrostatic drive systems and variators of the present invention comprise two of the hydrostatic radial piston machines disclosed in the aforementioned EP 2510192 and/or US 2013/0145929 (issued as US9784252). These two radial piston machines are fluidly connected together with a common control plate in between. At least one of the radial piston machines is of a variable displacement design. Each machine has an independent drive shaft which is connected to its cylinder block. In addition, a third shaft may pass through the middle of the hydrostatic drive system or variator for split power IVT applications.
  • a hydrostatic drive system of the invention comprises a housing, two hydrostatic radial piston machines within the housing and fluidly coupled to each other, and an intermediate control plate element common to each of the two hydrostatic radial piston machines.
  • Each of these hydrostatic radial piston machines comprises a radial cylinder block comprising a plurality of bores, a plurality of pistons corresponding to the plurality of bores, a cam ring, two control plate elements in which one of the two control plate elements is the intermediate control plate element, and a plurality of pass through channels in the radial cylinder block.
  • Each of the two control plate elements in each of the two hydrostatic radial piston machines includes a total of at least two control ports.
  • the intermediate control plate element is rotationally fixed in the housing between the radial cylinder blocks in the two hydrostatic radial piston machines.
  • the radial cylinder block in each of the two hydrostatic radial piston machines can be rotatably supported in the housing about a rotation axis and includes a plurality of bores extending from an outer enveloping surface of the radial cylinder block into an interior of the radial cylinder block and arranged distributed over a circumference of the radial cylinder block.
  • the plurality of pistons in each of the two hydrostatic radial piston machines can be movably supported in the bores and respectively define an operating cavity for a hydraulic fluid together with the associated bore.
  • the cam ring in each of the two hydrostatic radial piston machines can be arranged eccentric relative to the radial cylinder block and circumferentially envelops the radial cylinder block and wherein ends of the pistons oriented away from the radial cylinder block are movably supported at a continuously cambered inner enveloping surface of the cam ring during a rotation of the radial cylinder block.
  • At least one control port in at least one control plate element connects with an inlet/outlet channel and at least another control port in at least one control plate element connects with another inlet/outlet channel.
  • the two control plate elements in each of the two hydrostatic radial piston machines can extend respectively with a face oriented towards a central plane of the radial cylinder block, wherein the central plane is perpendicular to the rotation axis, and the two control plate elements extend with the faces oriented towards the radial cylinder block beyond a plane which is defined by a face of the radial cylinder block, wherein the face of the radial cylinder block is oriented towards the respective control plate element at a greatest axial width of the radial cylinder block.
  • the plurality of pass through channels in the radial cylinder block correspond to the plurality of bores in the radial cylinder block.
  • each control plate element can include a radial bearing portion in which radial forces from the radial cylinder block are transferrable to a respective opposite radial surface in the housing or to a radial surface of a housing cover supported in the housing through a direct contact of the radial bearing portion with the radial surface.
  • control plate elements radially and axially support the radial cylinder blocks in the hydrostatic radial piston machines.
  • the intermediate control plate element is free to move axially in the housing between the radial cylinder blocks in the two hydrostatic radial piston machines, a plurality of compensating pistons axially locates one of the control plate elements other than the intermediate control plate element relative to the housing, and the one of the control plate elements comprises a plurality of compensating piston bores corresponding to the compensating pistons and a plurality of control channels connected to the corresponding compensating piston bores and the corresponding control ports in the bearing faces of the corresponding one of the other control plate elements.
  • the intermediate control plate element is axially fixed in the housing between the radial cylinder blocks in the two hydrostatic radial piston machines, a plurality of compensating pistons axially locates each control plate element other than the intermediate control plate element relative to the housing, and each control plate element other than the intermediate control plate element comprises a plurality of compensating piston bores corresponding to the compensating pistons and a plurality of control channels connected to the corresponding compensating piston bores and the corresponding control ports in the bearing faces of the corresponding control plate elements.
  • the interfaces between the control plate elements and the corresponding radial cylinder blocks may for instance be spherically cambered in shape or conical ring shaped.
  • at least one of the hydrostatic radial piston machines is a variable displacement hydrostatic radial piston machine.
  • both of the hydrostatic radial piston machines are variable displacement hydrostatic radial piston machines.
  • one of the hydrostatic radial piston machines can be a pump and the other of the hydrostatic radial piston machines can be a motor.
  • Hydrostatic drive systems of the invention can advantageously be used in variable transmissions, such as a power split, hydro mechanical infinitely variable transmission or a continuously variable transmission.
  • Figure 1 is a longitudinal cross section of a preferred embodiment of a hydrostatic variator of the invention.
  • Figures la and lb show two detail views of Figure 1.
  • Figure 2 is a transverse cross section of the embodiment of the hydrostatic variator of Figure 1 according to line B-B.
  • Figure 3 is a transverse cross section of the embodiment of the hydrostatic variator of Figure 1 according to line C-C.
  • Figure 4 is a transverse cross section of the embodiment of the hydrostatic variator of Figure 1 according to line D-D.
  • Figure 5 is a transverse cross section of the embodiment of the hydrostatic variator of Figure 1 according to line E-E.
  • Figure 6 and 6a are isometric views of first control plate element 10 in the embodiment of the hydrostatic variator of Figures 1 and la.
  • Figure 7 and 7a are isometric views of intermediate control plate element 24 in the embodiment of the hydrostatic variator of Figures 1 and la.
  • Figure 8 is a longitudinal cross section of an alternate embodiment of a hydrostatic variator of the invention.
  • Figures 8a shows a detail view of Figure 8.
  • Figures 9 and 9a are isometric views of second control plate element 18 in the embodiment of the hydrostatic variator of Figures 8 and 8a.
  • hydrostatic machine refers to a machine which moves fluid between an inlet and an outlet by trapping fluid in one or more movable chambers. It has one drive shaft to transfer mechanical power to the chambers. It may function as a pump or a motor. It may be of variable (fluid) displacement or fixed (fluid) displacement.
  • hydrostatic radial piston machine refers to a hydrostatic machine as described above with a radial arrangement of cylinders and pistons.
  • a “variator” refers to a machine which has an input and an output shaft with variable speed and torque ratios between the two shafts.
  • a “hydrostatic variator” or “hydrostatic drive system” refers to a variator comprising two hydrostatic machines fluidly coupled together. At least one of the hydrostatic machines is of a variable displacement allowing variable speed and torque ratios between the two shafts.
  • Displacement means the volume of fluid moved between inlet and outlet ports of a hydrostatic machine in one revolution of its drive shaft.
  • inlet/outlet channel refers to a channel which may serve either as an inlet channel or as an outlet channel.
  • Figures 1, la, and lb show a preferred embodiment of a hydrostatic variator of the invention.
  • Figures 2-5 show various sections of a preferred embodiment of a hydrostatic variator of the invention.
  • variator 1 consists of first radial piston machine 2 and second radial piston machine 3 contained in a housing 5. Each radial piston machine 2, 3 is arranged around rotation axis 4.
  • one of the radial piston machines acts as a pump and the other as a motor.
  • First radial piston machine 2 comprises:
  • First radial cylinder block 8 comprises first and second side walls 8c and 8d respectively which are roughly concave in shape.
  • a plurality of radial bores 8b which extend from the outer enveloping surface 8e into an interior of the radial cylinder block and are evenly distributed over a circumference of the radial cylinder block.
  • a plurality of axial pass through channels 8a extend from side wall 8c to side wall 8d and connect with corresponding radial bores 8b.
  • First radial cylinder block 8 is arranged around and is rotatable about rotation axis 4. The greatest axial width of first cylinder block 8 is defined by faces 8g and 8h respectively.
  • a center plane 8f perpendicular to rotation axis 4 defines the center plane of radial cylinder block 8.
  • a first cam ring 9 circumferentially envelopes first radial cylinder block 8. As shown in Figure 2, the cam ring 9 may be displaced up to a total positive eccentric displacement El as measured from the rotation axis 4. In a preferred embodiment, the cam ring 9 may also be displaced up to a total negative eccentric displacement E2 also as shown in Figure 2.
  • First cam ring 9 comprises an inner enveloping surface 9a which is continuously spherically cambered in shape.
  • a plurality of pistons 11 corresponding to the plurality of radial bores 8b are movably supported and free to slide and tilt in the radial bores 8b.
  • a plurality of piston seals 12 hydraulically seal the pistons 11 against the walls of the radial bores 8b.
  • Each piston 11 and its corresponding radial bore 8b define an operating cavity 39 for hydraulic fluid.
  • fluid pressure in the operating cavity 39 forces the ends of the pistons 11 that are oriented away from the radial cylinder block 8 against the inner enveloping surface 9a of first cam ring 9.
  • the pistons 11 are held against the inner enveloping surface 9a by piston guide rings 13.
  • a first control plate element 10 is arranged around rotation axis 4 adjacent to first side wall 8c of first radial cylinder block 8. As shown in Figures 1, la, and 6a, first control plate element 10 comprises a roughly convex bearing face lOe the shape of which complements the first wall of radial cylinder block 8. As shown in Figure 6a, A-control port lOf and B-control port lOg are formed in the face of bearing face lOe are located opposite each other and are kidney shaped. Two closing surfaces lOj and 10k are created between A-control port lOf and B-control port lOg. A plurality of small bores and large bores 10c and lOd respectively are located on the face opposite bearing face lOe.
  • First control plate element 10 is radially supported in first end cap 6 by radial bearing portion lOh and opposite radial surface 6a and is free to slide axially but not permitted to rotate. First control plate element 10 is preloaded axially against first radial cylinder block 8 by preload spring 38 installed between first control plate element 10 and first end cap 6.
  • a plurality of small and large compensation pistons 14 and 15 are moveably supported in small and large bores 10c and lOd.
  • fluid pressure in large and small bores 10c and lOd forces the small and large compensation pistons 14 and 15 against first end cap 6.
  • first control plate element 10 is located axially in housing 5 against first radial cylinder block 8.
  • Alternate embodiments may vary in size and quantities of compensation bores and pistons.
  • only a single upper kidney shaped compensation bore and piston and a single lower kidney shaped compensation bore and piston are used in each control plate element.
  • An intermediate control plate element 24 is arranged around rotation axis 4 adjacent to second side wall 8d of first radial cylinder block 8.
  • intermediate control plate element 24 comprises a first and second bearing face 24f and 24g the shape of which is roughly convex and complements the second wall of radial cylinder block 8.
  • an upper first A-control port 24j and a lower first B-control port 24k are formed in the face of first bearing face 24f are located opposite each other and are kidney shaped.
  • an upper second A- control port 24m and a lower second B-Control Port 24n are formed in the face of second bearing face 24g are located opposite each other and are kidney shaped.
  • First A-control port 24j and second A- control port 24m are connected by A-inlet/outlet channel 24a.
  • First B-control port 24k and second B- control port 24n are connected by B-inlet/outlet channel 24b.
  • intermediate control plate element 24 is fully fixed within the housing 5, that is it cannot rotate nor translate relative to the housing.
  • First drive shaft 25 is coupled to first radial cylinder block 8.
  • First radial cylinder block 8 is supported on first control plate element 10 and intermediate control plate element 24 at interfaces Fl and F2 where interface Fl is defined by first side wall 8c and bearing face lOe; F2 is defined by second side wall 8d and first bearing face 24f.
  • Faces 8g and 8h define the greatest width of first cylinder block 8 and are oriented towards control plate 10 and intermediate control plate 24 respectively.
  • a center plane 8f perpendicular to rotation axis 4 defines the center plane of radial cylinder block 8.
  • Interfaces Fl and F2 are symmetric to each other across center plane 8f.
  • Bearing faces lOe and 24f extend past planes formed by faces 8g and 8h and are oriented towards the center plane 8f .
  • the radial forces generated by first radial cylinder block 8 are transferrable to first control plate element 10 and intermediate control plate element 24 at interfaces Fl and F2.
  • the radial forces in the first control plate element 10 are transferrable to the first endcap 6 through direct contact of radial bearing portion lOh and opposite radial surface 6a.
  • the radial forces in the intermediate control plate element 24 are transferrable to the housing 5 through direct contact of radial bearing portion 24h and opposite radial surface 5a.
  • the radial forces generated by first radial cylinder block 8 are transferrable to housing 5 and first end cap 6; only torque loads from first radial cylinder block 8 are transferable to first drive shaft 25.
  • first control plate element 10 and intermediate control plate element radially and axially support radial cylinder block 8 at two interfaces Fl and F2.
  • first radial piston machine 2 also comprises a means for adjusting fluid displacement shown as first displacement control 28 in Figure 2.
  • Second radial piston machine 3 comprises:
  • second radial piston machine 3 The components of second radial piston machine 3 are arranged in an analogous manner to those of first radial piston machine 2 and having second drive shaft 26 coupled to second radial cylinder block 16.
  • Cam ring 17 may be displaced to any portion of a total positive eccentric displacement of second cam ring E3 as shown in Figure 4.
  • cam ring 17 may also be displaced to any portion of a total negative eccentric displacement of second cam ring E4 also as shown in Figure 4.
  • second control plate element 118 is constructed similarly to first control plate element 10.
  • second radial piston machine 3 also comprises a means for adjusting fluid displacement shown as second displacement control 29 in Figure 4.
  • Figure la shows a detail of interface Fl between first radial cylinder block 8 and first control plate element 10 and interface F2 between first radial cylinder block 8 and intermediate control plate element 24.
  • interface F3 between second radial cylinder block 16 and second control plate element 118 and interface F4 between second radial cylinder block 16 and intermediate control plate element 24.
  • the shape of these four interfaces Fl, F2, F3, F4 may be any of a conical or conical ring shape and is roughly spherical in a preferred embodiment.
  • A-inlet/outlet channel 24a and B-inlet/outlet channel 24b are shown axially positioned in intermediate control plate element 24.
  • one inlet/outlet channel will be at a relatively high pressure delivering fluid from the radial piston machine operating as a pump to the radial piston machine operating as a motor while the other inlet/outlet channel will be at a relatively low pressure delivering fluid in the opposite direction.
  • A-tap line 24d connects A-inlet/outlet channel 24a with boost inlet port 24c while B-tap line 24e connects B-inlet/outlet channel 24b with boost inlet port 24c.
  • Control valves 27 are installed in A-tap line 24d and B-tap line 24e.
  • control valves 27 function as relief valves in the event that over pressure occurs and also as check valves allowing makeup fluid to enter the drive circuit from boost inlet port 24c.
  • an optional loop flushing valve which can also be incorporated into intermediate control plate element 24 with similar porting as provided for in control valves 27.
  • a loop flushing valve is not required as heat is removed from the system by conduction through the components as well as leakage from the pistons 11 and 19 and interfaces Fl, F2, F3, and F4..
  • one radial piston machine will act as a pump and the other as a motor.
  • first radial cylinder block 8 is forced to rotate in a clockwise direction as well and first radial piston machine 2 will act as a pump. Pass through channels 8a that are connected control ports lOg and 24k at that moment and the corresponding operating cavities 39 allow pistons 11 to draw fluid into the operating cavities 39.
  • B-inlet/outlet channel 24b functions as the inlet channel for first radial piston machine 2 in this example.
  • each pass through channel 8a passes the control ports lOg and 24k and is closed off by closing surfaces 10k and 24q.
  • the operating cavity 39 will be at its maximum volume at that portion of rotation.
  • each pass through channel 8a in turn are next connected to control ports lOf and 24j.
  • the pistons 11 push fluid out of operating cavities 39 into A- inlet/outlet channel 24a which functions as the outlet channel for first radial piston machine 2 in this example.
  • the fluid expelled from first radial piston machine 2 is pushed into second A- control port 24m through A-inlet/oulet channel 24a.
  • A-inlet/outlet channel 24a functions as an inlet channel for first radial piston machine 3 in this example.
  • second cam ring 17 is eccentrically displaced by some percentage of E3. Pass through channels 16a connected to corresponding operating cavities 40 and to control ports 24m and 118f allow fluid to enter operating cavities 40.
  • the fluid pressure acting against the pistons 19 and the radial bores 16b force radial cylinder block 16 and second drive shaft 26 to rotate in a clockwise direction.
  • second radial piston machine will act as a motor.
  • each pass through channel 16a in turn is closed off by closing surfaces 24r and the corresponding closing surface (not shown) on control plate element 118.
  • the operating cavity 40 will be at its maximum volume at that portion of rotation.
  • each of the pass through channels 16a are now connected to control ports 24n and 118g.
  • the pistons 19 push fluid out of operating cavities 40 into B-inlet/outlet channel 24b which functions as an outlet channel for second radial piston machine 3 in this particular example. Fluid is returned to first radial piston machine 2.
  • first and second cam rings 9 and 17 By varying one or both eccentricities of first and second cam rings 9 and 17 the fluid displacements of first and second radial piston machines 2 and 3. As such, variable speed and torque ratios between first and second drive shafts 25 and 26 respectively may be obtained.
  • first radial piston machine 2 and a second radial piston machine 3 are of different sizes and maximum displacements.
  • intermediate control plate element 24 is fixed from rotating but allowed to move axially within housing 5.
  • Second radial piston machine 3 is replaced with alternate second piston machine 103; no compensating pistons or preload spring are used.
  • Second radial piston machine 103 comprises:
  • Second control plate element 18 is constructed similarly to second control plate element 118 but does not contain bores and passages for any compensation pistons. Second control plate 18 is axially support directly by second end cap 7. A preload spring 39 between is not required between second control plate 18 and second end cap 7. In alternate this embodiment, the gaps at interfaces Fl, F2 F3 and F4 are all controlled simultaneously by the compensating pistons 14 and 15 in first control plate element 10. Additionally, if first radial piston machine 2 and second radial piston machine 103 are not of the same size and displacement, interfaces Fl and F2 need to be of a geometry yielding the same axial force as generated by the geometry at interfaces F3 and F4. In yet another alternate embodiment, intermediate control plate element 24 is fixed from rotating but allowed to move axially within housing 5.
  • First and second control plate elements 10 and 118 are used in first and second radial piston machines respectively with compensating pistons installed in both control plate elements.
  • a centering mechanism (not shown) is used to bias the intermediate control plate element to a desired neutral position.
  • first radial piston machine 2 or second radial piston machine 3 is variable with the other set at a fixed displacement.
  • a third radial piston machine is hydraulically connected to the first and second radial piston machines 2 and 3, respectively.
  • the displacement control may be of pivoting versus sliding design.
  • cam ring 9 or 17 pivots about a pin located parallel to the rotational axis.
  • a drive pin attached to the cam ring engages a linear actuator which controls the eccentric displacement of the cam ring.
  • variator 1 is integrated into a transmission housing. Housing 5 and end caps 6 and 7 are not present because all the structural requirements of the variator are supplied by the transmission housing.
  • an accumulator system may be connected at either or both of A-tap line 24d and B-tap line 24e allowing energy to be stored in and released from the accumulator system.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne un système d'entraînement hydrostatique comprenant un boîtier, deux machines à pistons radiaux hydrostatiques à l'intérieur du boîtier et en communication fluidiques l'une avec l'autre, et un élément plaque de commande intermédiaire commun à chacune des deux machines à pistons radiaux hydrostatiques. Chacune de ces machines à pistons radiaux hydrostatiques comprend un bloc-cylindre radial comprenant une pluralité d'alésages, une pluralité de pistons correspondant à la pluralité d'alésages, un anneau de came, deux éléments plaque de commande dans lesquels un des deux éléments plaque de commande est l'élément plaque de commande intermédiaire, et une pluralité de canaux traversants dans le bloc-cylindre radial. Chacun des deux éléments plaque de commande dans chacune des deux machines à pistons radiaux hydrostatiques comprend un total d'au moins deux orifices de commande. En outre, l'élément plaque de commande intermédiaire est fixé en rotation dans le boîtier entre les blocs-cylindres radiaux dans les deux machines à pistons radiaux hydrostatiques. L'invention concerne également une transmission à division de puissance et à variation continue comprenant le système d'entraînement hydrostatique.
PCT/CA2018/050528 2017-05-06 2018-05-03 Variateur hydrostatique basé sur des machines à pistons radiaux WO2018205015A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201762502629P 2017-05-06 2017-05-06
US62/502,629 2017-05-06

Publications (1)

Publication Number Publication Date
WO2018205015A1 true WO2018205015A1 (fr) 2018-11-15

Family

ID=64104086

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CA2018/050528 WO2018205015A1 (fr) 2017-05-06 2018-05-03 Variateur hydrostatique basé sur des machines à pistons radiaux

Country Status (1)

Country Link
WO (1) WO2018205015A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110617214A (zh) * 2019-10-03 2019-12-27 丁先虎 一种双芯并联泵的泵液输送方法

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2993339A (en) * 1958-03-11 1961-07-25 Angus George Co Ltd Rotary, hydraulic pump and motor transmission
DE1776238A1 (de) * 1965-05-31 1974-02-28 Breinlich Richard Dr Axial beaufschlagte rotationsfluidmaschine
US3969986A (en) * 1971-07-06 1976-07-20 Danfoss A/S Radial piston pump
EP0523384A1 (fr) * 1991-07-17 1993-01-20 Robert Bosch Gmbh Machine à piston hydrostatique
US5374165A (en) * 1992-09-04 1994-12-20 J. M. Voith Gmbh Pump with hydrostatic piston elements and with axial thrust compensation
US5452646A (en) * 1992-07-02 1995-09-26 J. M. Voith Gmbh Hydrostatic motor with axial thrust offset
US5473894A (en) * 1993-06-14 1995-12-12 Poclain Hydraulics Combination of two pressurized fluid motors
US5622052A (en) * 1993-10-19 1997-04-22 J.M. Voith Gmbh Double-flow hydrostatic radial piston engine with axial flow, thrust compensation, and shaft bearing
US20130145929A1 (en) * 2009-12-11 2013-06-13 Juergen Berbuer Hydrostatic radial piston machine

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2993339A (en) * 1958-03-11 1961-07-25 Angus George Co Ltd Rotary, hydraulic pump and motor transmission
DE1776238A1 (de) * 1965-05-31 1974-02-28 Breinlich Richard Dr Axial beaufschlagte rotationsfluidmaschine
US3969986A (en) * 1971-07-06 1976-07-20 Danfoss A/S Radial piston pump
EP0523384A1 (fr) * 1991-07-17 1993-01-20 Robert Bosch Gmbh Machine à piston hydrostatique
US5452646A (en) * 1992-07-02 1995-09-26 J. M. Voith Gmbh Hydrostatic motor with axial thrust offset
US5374165A (en) * 1992-09-04 1994-12-20 J. M. Voith Gmbh Pump with hydrostatic piston elements and with axial thrust compensation
US5473894A (en) * 1993-06-14 1995-12-12 Poclain Hydraulics Combination of two pressurized fluid motors
US5622052A (en) * 1993-10-19 1997-04-22 J.M. Voith Gmbh Double-flow hydrostatic radial piston engine with axial flow, thrust compensation, and shaft bearing
US20130145929A1 (en) * 2009-12-11 2013-06-13 Juergen Berbuer Hydrostatic radial piston machine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110617214A (zh) * 2019-10-03 2019-12-27 丁先虎 一种双芯并联泵的泵液输送方法
CN110617214B (zh) * 2019-10-03 2021-02-19 浙江青霄科技股份有限公司 一种双芯并联泵的泵液输送方法

Similar Documents

Publication Publication Date Title
US4493189A (en) Differential flow hydraulic transmission
US3223046A (en) Rotary radial piston machines
US4075933A (en) Hydraulic pump or motor
CA1232822A (fr) Compensateur des fluctuations de couple entre un volant et une transmission hydraulique sans paliers de vitesses
EP0078513B1 (fr) Dispositif transformateur d'énergie d'un fluide à mouvement rotatoire
EP0015127B1 (fr) Appareil hydraulique comportant un moteur et une pompe
US2220636A (en) Hydraulic transmission gear
US3785250A (en) Piston-type machine
WO2018205015A1 (fr) Variateur hydrostatique basé sur des machines à pistons radiaux
US8052401B2 (en) Double-acting radial piston hydraulic apparatus
US3233555A (en) Variable displacement fluid device
JPH0313588Y2 (fr)
US9488050B2 (en) Radial cylinder hydraulic machine with improved oscillating radial cylinder
EP0234631B1 (fr) Moteur hydraulique
US3277834A (en) Rotary radial piston machine with enlarged piston stroke
US3796525A (en) Energy translation devices
US3656407A (en) Radial piston pump
US5989001A (en) Planetary rotation machine with hydrostatically mounted control part, and control part for this purpose
US3561328A (en) Rotary piston machine
US5161961A (en) Gear pump with counterbalanced radial forces and two piece radial seals
CA2667689C (fr) Machine de pale de rotor
JP6951590B2 (ja) 油圧システム
US20190316572A1 (en) Hydrostatic Axial Piston Machine
KR100287915B1 (ko) 무한 가변 링 기어 펌프
JPH0212307B2 (fr)

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18798219

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18798219

Country of ref document: EP

Kind code of ref document: A1