EP2598747B1 - A rotary hydraulic machine with radial pistons. - Google Patents
A rotary hydraulic machine with radial pistons. Download PDFInfo
- Publication number
- EP2598747B1 EP2598747B1 EP11716053.1A EP11716053A EP2598747B1 EP 2598747 B1 EP2598747 B1 EP 2598747B1 EP 11716053 A EP11716053 A EP 11716053A EP 2598747 B1 EP2598747 B1 EP 2598747B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- cylinder
- hydraulic machine
- rotary hydraulic
- housing
- piston
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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- 239000012530 fluid Substances 0.000 claims description 11
- 238000004891 communication Methods 0.000 claims description 7
- 238000006243 chemical reaction Methods 0.000 description 3
- 210000000056 organ Anatomy 0.000 description 3
- 238000013519 translation Methods 0.000 description 3
- 230000014616 translation Effects 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 244000261422 Lysimachia clethroides Species 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000001747 exhibiting effect Effects 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 238000009424 underpinning Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C1/00—Reciprocating-piston liquid engines
- F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
- F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
- F03C1/0403—Details, component parts specially adapted of such engines
- F03C1/0415—Cylinders
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- 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
- F04B1/0404—Details or component parts
- F04B1/0421—Cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
- F04B53/162—Adaptations of cylinders
Definitions
- the present invention relates to a rotary hydraulic machine having radial pistons.
- Hydraulic machines are devices which transform kinetic energy from a shaft into pressurising energy of a liquid, and vice versa.
- the hydraulic machine functions as a pump, while in the second case the hydraulic machine functions as a motor.
- the operating liquid is oil.
- Rotary hydraulic machines are those in which the element transmitting the kinetic energy to the outside (in the case of motors) or which introduces the kinetic energy to the inside (in the case of pumps) is a shaft provided with continuous rotary motion.
- Rotary hydraulic motors with pistons are constituted by one or more chambers in which a volume is continually varied by the motion of a piston internally of a cylindrical seating.
- the chambers are placed periodically in fluid communication with the supply environment and with the discharging environment by means of holes which are freed by the relative motion between the piston and the cylinder.
- the pistons translate along axes which are arranged perpendicularly to the rotation axis of the drive shaft.
- Rotary hydraulic motors with radial pistons which have a static cylinder block internally of which a plurality of housing seatings for the cylinders are afforded. These seatings are arranged radially equidistanced (in a star fashion) with respect to the axis of the drive shaft.
- the cylinders are constrained to the cylinder block by means of pins which enable the cylinders to oscillate in "pendulum fashion" about axes that are parallel to the drive shaft.
- Respective pistons are arranged internally of the cylinders, which pistons can slide along directions that are perpendicular to the drive shaft.
- the pistons are active on a crank of the drive shaft, which crank rotates eccentrically with respect to the drive shaft.
- An annular crown is keyed rotatably on the crank and is associated to the pistons.
- the crown transmits a force to the crank of the drive shaft directed perpendicularly to the rotation axis thereof.
- the pistons perform translations along directions which intersect in the centre of the annular crown, the centre of which crown does not coincide (but as mentioned, it is eccentric) with the rotation axis of the drive shaft.
- the cylinders are arranged in a star-fashion concentrically to the rotation axis of the drive shaft.
- the translation of the pistons generates a torque on the cylinders which induce the cylinders to oscillate in a "pendulum fashion" during functioning of the motor.
- the pressure transmitted by the pistons to the cylinders (responsible for the torque mentioned above) is identical (net of friction) to the force transmitted by the piston to the annular crown (a force which sets the drive shaft in rotation).
- This pressure is unloaded on the cylinder body only via the two pins which constrain each cylinder to the cylinder body.
- a rotary hydraulic machine according to the preamble of claim 1 is shown in SU615248 or SU733386 .
- the technical objective underpinning the present invention is to provide a rotary hydraulic machine according to claim 1 having radial pistons which obviates the drawbacks in the prior art as cited herein above.
- an aim of the present invention is to provide a rotary hydraulic machine having radial pistons which requires only small reconditioning operations.
- a further aim of the present invention is to provide a rotary hydraulic machine with radial pistons which is dimensionable for any power.
- the set technical objective and the set aims are substantially attained by a rotary hydraulic machine having radial pistons, comprising the technical characteristics set out in one or more of the appended claims.
- 1 denotes in its entirety a rotary hydraulic machine having radial pistons of the present invention.
- the machine 1 comprises a rotating shaft 2 which, in the case of a motor, is a drive shaft and in the case of a pump is the shaft introducing energy into the pump.
- the rotating shaft 2 rotates with a continuous motion about a rotation axis R (illustrated in figure 4 ).
- the machine 1 further comprises a fixed cylinder body 3 exhibiting a plurality of housing seatings 4.
- the housing seatings 4 are arranged radially equidistanced to the axis R of rotation of the rotating shaft 2, such as to realise a star-configuration.
- the housing seatings are five in number (see figures 1 , 2 and 3 ).
- a relative cylinder 5 is provided internally of each housing seating 4, which cylinder 5 is able to rotate internally of the housing seating 4 about an axis C which is parallel to the rotation axis R of the rotating shaft 2.
- a relative piston 6 is provided internally of each cylinder 5.
- Each piston 6 is slidably coupled to the respective cylinder 5 along a sliding axis P (in the accompanying figures, and in particular in figures 1 , 2 and 3 a cylinder 5 and the respective piston 6 have been removed so that the housing seating 4 can be more clearly illustrated).
- the sliding axes P are perpendicular to the rotation axis R of the rotating axis 2 and perpendicular to the rotation axes C of the cylinder 5 internally of the respective housing seatings 4.
- Each piston 6 is further coupled to a crank 7 of the rotating shaft 2.
- the crank 7 is eccentric with respect to the rotation axis R of the rotating shaft 2 (see figure 4 ).
- crank in the context of the present invention, reference is made to a portion of the rotating shaft 2 which develops in a "goose-neck" shape with respect to the rotating shaft, i.e. which forms a hook shape with respect to the straight development of the rotating shaft.
- An annular crown 8 is keyed on the crank 7, which crown 8 is rotatable with respect to the crank about an axis that is parallel to the rotation axis R of the rotating shaft 2.
- Each piston 6 is constrained to the annular crown 8 along a direction coinciding with the sliding axis P, while it is free to slide with respect to the annular crown 8 along a perpendicular direction to the sliding axis P.
- each piston 6 cannot distance from the annular crown 8 but the crown 8 can rotate with respect to the piston 6.
- the annular crown 8 comprises retaining organs 9 which retain the base of the piston 6 on the external surface 8a of the annular crown 8 (as illustrated in figure 4 ).
- the retaining organs 9 are, for example, constituted by a pair of skids acting between the base of the piston 6 and the external surface 8a of the annular crown 8.
- Rollers 10 ( figure 4 ) are interposed between the annular crown 8 and the crank 7, which rollers 10 enable the annular crown 8 to rotate on the crank 7.
- the piston 6 transmits a force to the annular crown 8 which sets the rotating shaft 2 in rotation (according to the mechanism as described above).
- conduits 12 are enslaved to each cylinder 5, which conduits 12 are delivery conduits of pressurised oil, and one or more discharge conduits 13 of the oil (see figure 4 ).
- crank 7 is translated, bringing it into a distanced position by 120° in a clockwise direction with respect to the original position thereof.
- the same type of motion differentiates figure 2 from figure 3 and figure 3 from figure 1 .
- the cylinders 5 perform a pendular oscillation during a complete revolution of the rotating shaft 2.
- the cylinders 5 and the housing seatings 4 have a cylindrical-sector conformation (see figures 1 , 2 and 3 ).
- each cylinder 5 comprises an external wall 14 having a cylindrical-sector development and each housing seating 4 comprises a surface 15 having a cylindrical-sector development.
- the external wall 14 of the cylinder 5 is slidably in contact with the surface 15 of the housing seating 4, i.e. it slides along the surface 15.
- the surface 15 of the housing seating 4 and the external wall 14 of the cylinder 5 have a greater development than the development of a semi-cylinder (as illustrated in figures from 1 to 3).
- the cylinder 5 is retained in the housing seating 4 by mechanical interference between the cylinder 5 and the seating 4.
- the machine 1 advantageously comprises a compensating chamber 16, afforded between each cylinder 5 and the respective housing seating 4, set in fluid communication with a source of pressurised fluid (see in particular figure 5 ).
- the compensating chamber 16 creates a thrust on the cylinder 5 which is able to compensate, at least in part, the thrust that is exerted on the cylinder during the travel run of the piston.
- This force is the main one responsible for the friction forces which oppose the rotation of the cylinder 5 in the housing seating 4.
- the compensating chamber 16 enables a force to be generated on the cylinder 5 which is opposite the above-mentioned reaction force.
- the compensating chamber 16 is preferably in fluid communication with the expansion chamber 11 such as to receive pressurised fluid directly from the expansion chamber 11.
- the cylinder 5 comprises a conduit 17 which, by crossing the whole breadth of the chamber 5, connects the expansion chamber 11 and the compensating chamber 16.
- the chamber 16 is set in a position such that the sliding axis P of the piston 6 crosses the compensating chamber 16 (see figure 5 ).
- the compensating chamber 16 preferably exhibits a maximum dimension at the sliding axis P of the piston 6.
- the compensating chamber 16 is symmetrical with respect to the sliding axis P.
- the efficiency of the compensating chamber 16 is maximised since the force transmitted to the cylinder 5 by the compensating chamber 16 is perfectly aligned with and in an opposite direction to the reaction force (see above) transmitted to the cylinder 5.
- the compensating chamber 16 is defined by a rectified portion of the external wall 14 of the cylinder 5 in combination with the surface 15 of the housing seating 4 (as shown in figure 5 ).
- the external wall 14 of the cylinder 5 exhibits a straight portion which, in combination with the curvature of the surface 15 of the housing seating 4, creates a space which defines the compensating chamber 16.
- the position of the compensating chamber 16 is fixed with respect to the cylinder 5 and varies with respect to the housing seating 4 as a function of the relative position of the cylinder internally of the seating 4 (compare figures 1 , 2 and 3 ).
- the machine 1 also comprises a further compensating chamber 18 active between the piston 6 and the external surface 8a of the annular crown 8.
- the further compensating chamber 18 performs the same function as the above-described compensating chamber 16, though it is active between the base of the piston 6 and the annular crown 8.
- the further compensating chamber 18 reduces the friction between the piston 6 and the annular crown 8.
- the further compensating chamber 18 too is crossed by the sliding axis P of the piston 6 and exhibits a maximum dimension at the sliding axis P.
- the further compensating chamber 18 is in fluid communication with the expansion chamber 11 via a conduit 19.
- the invention thus attains the set aims.
- the compensating chamber 16 in combination with the cylindrical-sector development of the housing seatings 4 and the cylinders 5 rotating therein, guarantee avoiding a concentration of forces at a few points (for example the pins in the prior art) and thus reduce wear on the machine and as a consequence limit the need for reconditioning operations.
- the force transmitted to the cylinder by the piston 6 is in fact well distributed over a wide surface and is compensated (at least partially) by the compensating chamber 16.
- the compensating chamber 16, the housing seatings 4, the cylinders 5 and the pistons 6 can be dimensioned as required without incurring any drawbacks, so that the machine 1 can be dimensioned for any power rating.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Hydraulic Motors (AREA)
- Reciprocating Pumps (AREA)
- Soil Working Implements (AREA)
Description
- The present invention relates to a rotary hydraulic machine having radial pistons.
- Hydraulic machines are devices which transform kinetic energy from a shaft into pressurising energy of a liquid, and vice versa.
- In the first case the hydraulic machine functions as a pump, while in the second case the hydraulic machine functions as a motor. In both cases, the operating liquid is oil.
- Rotary hydraulic machines are those in which the element transmitting the kinetic energy to the outside (in the case of motors) or which introduces the kinetic energy to the inside (in the case of pumps) is a shaft provided with continuous rotary motion.
- For the sake of simple presentation, from here on explicit reference will be made to the case of motors, as motors are differentiated from pumps only in regard to the direction of energy flow and not in regard to constructional mechanisms.
- Rotary hydraulic motors with pistons are constituted by one or more chambers in which a volume is continually varied by the motion of a piston internally of a cylindrical seating.
- The chambers are placed periodically in fluid communication with the supply environment and with the discharging environment by means of holes which are freed by the relative motion between the piston and the cylinder.
- In rotary hydraulic motors having radial pistons, to which the present invention relates, the pistons translate along axes which are arranged perpendicularly to the rotation axis of the drive shaft.
- Rotary hydraulic motors with radial pistons are known which have a static cylinder block internally of which a plurality of housing seatings for the cylinders are afforded. These seatings are arranged radially equidistanced (in a star fashion) with respect to the axis of the drive shaft.
- The cylinders are constrained to the cylinder block by means of pins which enable the cylinders to oscillate in "pendulum fashion" about axes that are parallel to the drive shaft.
- Respective pistons are arranged internally of the cylinders, which pistons can slide along directions that are perpendicular to the drive shaft.
- The pistons are active on a crank of the drive shaft, which crank rotates eccentrically with respect to the drive shaft.
- An annular crown is keyed rotatably on the crank and is associated to the pistons.
- When the chamber defined between the piston and the head of the respective cylinder is placed under pressure, the piston translates distancingly from the cylinder head and transmits a force to the annular crown.
- The crown transmits a force to the crank of the drive shaft directed perpendicularly to the rotation axis thereof.
- This force is clearly offset with respect to the rotation axis of the drive shaft, and thus generates a torque which sets the drive shaft in rotation. The combined action of the various cylinders guarantees a continuous rotary drive of the rotating shaft.
- These types of motors and, equally, pumps, exhibit an important drawback. The pistons perform translations along directions which intersect in the centre of the annular crown, the centre of which crown does not coincide (but as mentioned, it is eccentric) with the rotation axis of the drive shaft.
- On the contrary, the cylinders are arranged in a star-fashion concentrically to the rotation axis of the drive shaft.
- Therefore, the translation of the pistons generates a torque on the cylinders which induce the cylinders to oscillate in a "pendulum fashion" during functioning of the motor.
- The pressure transmitted by the pistons to the cylinders (responsible for the torque mentioned above) is identical (net of friction) to the force transmitted by the piston to the annular crown (a force which sets the drive shaft in rotation).
- Thus the pressure transmitted by the pistons to the cylinders is of considerable entity (directly proportional to the power of the motor).
- This pressure is unloaded on the cylinder body only via the two pins which constrain each cylinder to the cylinder body.
- Therefore great attention must be paid during the design stage with regard to the dimensioning and mechanical properties of the cited pins.
- Further, the inevitable wear on these pins (or the relative seatings) creates play in the coupling between the cylinder and the cylinder body which play requires the rectification of the motor.
- What is more, the maximum power of these motors has physical limitations in the possibility of realising pins and relative seatings which are able to guarantee an adequate working life of the motor.
- A rotary hydraulic machine according to the preamble of
claim 1 is shown inSU615248 SU733386 - In this context, the technical objective underpinning the present invention is to provide a rotary hydraulic machine according to
claim 1 having radial pistons which obviates the drawbacks in the prior art as cited herein above. - In particular, an aim of the present invention is to provide a rotary hydraulic machine having radial pistons which requires only small reconditioning operations.
- A further aim of the present invention is to provide a rotary hydraulic machine with radial pistons which is dimensionable for any power.
- The set technical objective and the set aims are substantially attained by a rotary hydraulic machine having radial pistons, comprising the technical characteristics set out in one or more of the appended claims.
- Further characteristics and advantages of the present invention will more clearly emerge from the following non-limiting description of a preferred but not exclusive embodiment of a rotary hydraulic machine having radial pistons, as illustrated in the accompanying drawings, in which:
-
figure 1 is a section view of a rotary hydraulic machine having radial pistons of the present invention, with some parts removed better to evidence others; -
figure 2 is a view of the machine offigure 1 in a different operating configuration; -
figure 3 is a view of the machine offigure 1 in a further different operating configuration; -
figure 4 is a section according to plane IV-IV of the machine offigure 1 ; and -
figure 5 is an enlarged view of a detail of the machine offigure 1 . - With reference to the figures of the drawings, 1 denotes in its entirety a rotary hydraulic machine having radial pistons of the present invention.
- The
machine 1 comprises a rotating shaft 2 which, in the case of a motor, is a drive shaft and in the case of a pump is the shaft introducing energy into the pump. - The rotating shaft 2 rotates with a continuous motion about a rotation axis R (illustrated in
figure 4 ). - The
machine 1 further comprises a fixedcylinder body 3 exhibiting a plurality ofhousing seatings 4. - The
housing seatings 4 are arranged radially equidistanced to the axis R of rotation of the rotating shaft 2, such as to realise a star-configuration. - In the preferred embodiment of the invention the housing seatings are five in number (see
figures 1 ,2 and3 ). - A
relative cylinder 5 is provided internally of eachhousing seating 4, whichcylinder 5 is able to rotate internally of thehousing seating 4 about an axis C which is parallel to the rotation axis R of the rotating shaft 2. - A
relative piston 6 is provided internally of eachcylinder 5. Eachpiston 6 is slidably coupled to therespective cylinder 5 along a sliding axis P (in the accompanying figures, and in particular infigures 1 ,2 and3 acylinder 5 and therespective piston 6 have been removed so that thehousing seating 4 can be more clearly illustrated). - The sliding axes P are perpendicular to the rotation axis R of the rotating axis 2 and perpendicular to the rotation axes C of the
cylinder 5 internally of therespective housing seatings 4. - Each
piston 6 is further coupled to acrank 7 of the rotating shaft 2. Thecrank 7 is eccentric with respect to the rotation axis R of the rotating shaft 2 (seefigure 4 ). - By crank, in the context of the present invention, reference is made to a portion of the rotating shaft 2 which develops in a "goose-neck" shape with respect to the rotating shaft, i.e. which forms a hook shape with respect to the straight development of the rotating shaft.
- An
annular crown 8 is keyed on thecrank 7, whichcrown 8 is rotatable with respect to the crank about an axis that is parallel to the rotation axis R of the rotating shaft 2. - Each
piston 6 is constrained to theannular crown 8 along a direction coinciding with the sliding axis P, while it is free to slide with respect to theannular crown 8 along a perpendicular direction to the sliding axis P. - In other words, each
piston 6 cannot distance from theannular crown 8 but thecrown 8 can rotate with respect to thepiston 6. - For this purpose, the
annular crown 8 comprises retainingorgans 9 which retain the base of thepiston 6 on theexternal surface 8a of the annular crown 8 (as illustrated infigure 4 ). - Note that the
retaining organs 9 guarantee however that the base of thepiston 6 can slide along the external surface of theannular crown 8. - The
retaining organs 9 are, for example, constituted by a pair of skids acting between the base of thepiston 6 and theexternal surface 8a of theannular crown 8. - Rollers 10 (
figure 4 ) are interposed between theannular crown 8 and thecrank 7, whichrollers 10 enable theannular crown 8 to rotate on thecrank 7. - In this way, when a force is applied on the external surface of the
annular crown 8 directed towards the centre thereof, this force generates a torque with respect to the rotation axis R of the rotating shaft 2 which causes rotation thereof. - To this end, note that the sliding axes P of the
pistons 6 converge at a point coinciding with the centre of the annular crown 8 (and therefore eccentric with respect to the rotation axis R of the rotating shaft 2). - When the pressure increases in the expansion chamber 11 (the variable-volume chamber which is created between the
piston head 6 and the cylinder 5), thepiston 6 transmits a force to theannular crown 8 which sets the rotating shaft 2 in rotation (according to the mechanism as described above). - In this regard one or
more conduits 12 are enslaved to eachcylinder 5, whichconduits 12 are delivery conduits of pressurised oil, and one ormore discharge conduits 13 of the oil (seefigure 4 ). - In particular, when a
piston 6 transmits the above-cited force to theannular crown 8, thecrown 8 sets thecrank 7 in motion and thepiston 6 translates internally of thecylinder 5. - Since, as mentioned, the sliding axis P of the
pistons 6 passes through the centre of theannular crown 8 while thecylinders 5 are free to rotate internally of theseatings 4 arranged equidistanced from the rotation axis R of the rotating shaft 2, the sliding of thepiston 6 internally of thecylinder 5 causes a rotation of thecylinder 5. - In other words, the
pistons 6 near and distance from the rotation axis R of the rotating shaft 2, while thecylinders 5 are always at the same distance from the rotation axis R. - Therefore, in order to have a sliding motion of the
piston 6 internally of thecylinder 5, the cylinder must be able to rotate internally of theseating 4. By comparingfigures 1 ,2 and3 with one another, the entity of the rotation can be noted, as a function of thepiston 5 run and thus of the translation of thecrank 7. - In particular, between
figure 1 and2 thecrank 7 is translated, bringing it into a distanced position by 120° in a clockwise direction with respect to the original position thereof. The same type of motion differentiatesfigure 2 fromfigure 3 and figure 3 fromfigure 1 . - As can be observed, the
cylinders 5 perform a pendular oscillation during a complete revolution of the rotating shaft 2. - The rotation of the
cylinders 5 is guaranteed by the coupling between thecylinder 5 and therespective housing seating 4. - In particular, the
cylinders 5 and thehousing seatings 4 have a cylindrical-sector conformation (seefigures 1 ,2 and3 ). - In detail, each
cylinder 5 comprises anexternal wall 14 having a cylindrical-sector development and eachhousing seating 4 comprises asurface 15 having a cylindrical-sector development. - The
external wall 14 of thecylinder 5 is slidably in contact with thesurface 15 of thehousing seating 4, i.e. it slides along thesurface 15. - Note that there are no pins present active between the
cylinder 5 and therespective housing seating 4 for to guaranteeing relative rotation between the two elements. - The
surface 15 of thehousing seating 4 and theexternal wall 14 of thecylinder 5 have a greater development than the development of a semi-cylinder (as illustrated in figures from 1 to 3). - In this way, the
cylinder 5 is retained in thehousing seating 4 by mechanical interference between thecylinder 5 and theseating 4. - The
machine 1 advantageously comprises a compensatingchamber 16, afforded between eachcylinder 5 and therespective housing seating 4, set in fluid communication with a source of pressurised fluid (see in particularfigure 5 ). - The compensating
chamber 16 creates a thrust on thecylinder 5 which is able to compensate, at least in part, the thrust that is exerted on the cylinder during the travel run of the piston. - Note that the pressure internally of the
expansion chamber 11 generates a thrust on thepiston 6 that is directed towards the centre of the annular crown 8 (as mentioned above) and, contemporaneously, generates a reaction force which is equal and opposite on thecylinder 5. - This force is the main one responsible for the friction forces which oppose the rotation of the
cylinder 5 in thehousing seating 4. - As mentioned herein above, the compensating
chamber 16 enables a force to be generated on thecylinder 5 which is opposite the above-mentioned reaction force. - The compensating
chamber 16 is preferably in fluid communication with theexpansion chamber 11 such as to receive pressurised fluid directly from theexpansion chamber 11. - This enables the same source of pressurised oil to be used for supplying both the
expansion chamber 11 and the compensatingchamber 16. Further, as the pressure internally of theexpansion chamber 11 varies during the functioning of the machine, the pressure internally of the compensatingchamber 16 also varies in the same way. - In order to guarantee fluid communication between the
expansion chamber 11 and the compensatingchamber 16, thecylinder 5 comprises aconduit 17 which, by crossing the whole breadth of thechamber 5, connects theexpansion chamber 11 and the compensatingchamber 16. - In order to guarantee maximum efficiency of the compensating
chamber 16, thechamber 16 is set in a position such that the sliding axis P of thepiston 6 crosses the compensating chamber 16 (seefigure 5 ). - The compensating
chamber 16 preferably exhibits a maximum dimension at the sliding axis P of thepiston 6. - In particular, the compensating
chamber 16 is symmetrical with respect to the sliding axis P. - In this way, the efficiency of the compensating
chamber 16 is maximised since the force transmitted to thecylinder 5 by the compensatingchamber 16 is perfectly aligned with and in an opposite direction to the reaction force (see above) transmitted to thecylinder 5. - In the preferred embodiment of the invention, the compensating
chamber 16 is defined by a rectified portion of theexternal wall 14 of thecylinder 5 in combination with thesurface 15 of the housing seating 4 (as shown infigure 5 ). - In other words, the
external wall 14 of thecylinder 5 exhibits a straight portion which, in combination with the curvature of thesurface 15 of thehousing seating 4, creates a space which defines the compensatingchamber 16. - Note that the position of the compensating
chamber 16 is fixed with respect to thecylinder 5 and varies with respect to thehousing seating 4 as a function of the relative position of the cylinder internally of the seating 4 (comparefigures 1 ,2 and3 ). - The
machine 1 also comprises a further compensatingchamber 18 active between thepiston 6 and theexternal surface 8a of theannular crown 8. The further compensatingchamber 18 performs the same function as the above-described compensatingchamber 16, though it is active between the base of thepiston 6 and theannular crown 8. - In other words, the further compensating
chamber 18 reduces the friction between thepiston 6 and theannular crown 8. - The further compensating
chamber 18 too is crossed by the sliding axis P of thepiston 6 and exhibits a maximum dimension at the sliding axis P. The further compensatingchamber 18 is in fluid communication with theexpansion chamber 11 via aconduit 19. - The invention thus attains the set aims.
- The compensating
chamber 16, in combination with the cylindrical-sector development of thehousing seatings 4 and thecylinders 5 rotating therein, guarantee avoiding a concentration of forces at a few points (for example the pins in the prior art) and thus reduce wear on the machine and as a consequence limit the need for reconditioning operations. - The force transmitted to the cylinder by the
piston 6 is in fact well distributed over a wide surface and is compensated (at least partially) by the compensatingchamber 16. - Further, the compensating
chamber 16, thehousing seatings 4, thecylinders 5 and thepistons 6 can be dimensioned as required without incurring any drawbacks, so that themachine 1 can be dimensioned for any power rating.
Claims (11)
- A rotary hydraulic machine having radial pistons, comprising a rotating shaft (2), a cylinder-housing body (3) having a plurality of housing seatings (4) arranged radially and equidistanced from a rotation axis (R) of the rotating shaft (2), a cylinder (5) housed in each of the plurality of housing seatings (4) and rotating with respect to the respective housing seating of the plurality of housing seatings (4) about an axis (C) which is parallel to the rotation axis (R) of the rotating shaft (2), a slidable piston (6) in the cylinder (5) housed in each of the plurality of housing seatings (4) coupled to a crank (7) of the rotating shaft (2), the crank (7) being offset with respect to the rotation axis (R) of the rotating shaft (2), wherein the cylinder (5) housed in each of the plurality of housing seatings (4) and each housing seating (4) have a cylindrical-section sector, a compensating chamber (16) being afforded between the cylinder (5) housed in each of the plurality of the housing seatings (4) and the respective housing seating (4), set in fluid communication with a pressurised fluid source,
characterized in that an annular crown (8) is keyed on the crank (7), said crown (8) is rotatable with respect to the crank about an axis that is parallel to the rotation axis (R) of the rotating shaft (2) and in that rollers (10) are interposed between the annular crown (8) and the crank (7), said rollers (10) enable the annular crown (8) to rotate on the crank (7). - The rotary hydraulic machine of claim 1, wherein the cylindrical-section sectors defining the development of the cylinders (5) and the housing seatings (4) exhibit respective axes of development which are parallel to one another, parallel to the axis (C) of rotation of the cylinders (5) and perpendicular to the rotation axis (R) of the rotating shaft (2).
- The rotary hydraulic machine of claim 2, wherein each cylinder (5) comprises an external wall (14) having a cylindrical-sector development and each housing seating (4) comprises a surface (15) having a cylindrical-sector development; the external wall (14) being slidably in contact with the surface (15).
- The rotary hydraulic machine of claim 3, wherein the surface (15) of the housing seating (4) and the external wall (14) of the cylinder (5) have a development that is greater than a development of a semi-cylinder.
- The rotary hydraulic machine of claim 3, wherein the compensating chamber (16) is defined by a flattened portion of the external wall (14) of the cylinder (5) in combination with the surface (15) of the housing seating (4).
- The rotary hydraulic machine of any one of the preceding claims, wherein the compensating chamber (16) is in fluid communication with an expansion chamber (11), defined between the piston (6) and the cylinder (5), in order to receive pressurised fluid supplied to the expansion chamber (11).
- The rotary hydraulic machine of any one of the preceding claims, wherein each piston (6) is slidably coupled to the respective cylinder (5) along a sliding axis (P); the compensating chamber (16) being crossed by the sliding axis (P).
- The rotary hydraulic machine of claim 7, wherein the compensating chamber (16) exhibits a maximum dimension at the sliding axis (P).
- The rotary hydraulic machine of any one of the preceding claims, comprising the annular crown (8) which is rotatably keyed on the crank (7) of the rotating shaft (2); each piston (6) in each cylinder (5) being constrained to an external surface (8a) of the annular crown (8) along a direction which coincides with a sliding axis (P) of said each piston (6).
- The rotary hydraulic machine of claim 9, comprising a further compensating chamber (18) acting between the piston (6) and the external surface (8a) of the annular crown (8).
- The rotary hydraulic machine of claim 10, wherein the further compensating chamber (18) is crossed by the sliding axis (P) and exhibits a maximum dimension at the sliding axis (P).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
ITMO2010A000216A IT1401175B1 (en) | 2010-07-27 | 2010-07-27 | ROTARY HYDRAULIC HYDRAULIC MACHINE. |
PCT/IB2011/051218 WO2012014090A1 (en) | 2010-07-27 | 2011-03-23 | A rotary hydraulic machine with radial pistons |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2598747A1 EP2598747A1 (en) | 2013-06-05 |
EP2598747B1 true EP2598747B1 (en) | 2018-02-14 |
Family
ID=43734001
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11716053.1A Active EP2598747B1 (en) | 2010-07-27 | 2011-03-23 | A rotary hydraulic machine with radial pistons. |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2598747B1 (en) |
IT (1) | IT1401175B1 (en) |
WO (1) | WO2012014090A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102852708B (en) * | 2012-09-20 | 2014-12-17 | 台州帕克兰液压机械有限公司 | Hydraulic motor with flushing function |
IT201800003452A1 (en) * | 2018-03-12 | 2019-09-12 | Italgroup S R L Con Unico Socio | Rotary hydraulic machine |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
SU615248A1 (en) * | 1977-01-03 | 1978-07-15 | Всесоюзный научно-исследовательский и проектно-конструкторский институт промышленных гидроприводов и гидроавтоматики | Radial piston hydraulic machine |
SU626241A1 (en) * | 1977-04-04 | 1978-09-30 | Всесоюзный научно-исследовательский и проектно-конструкторский институт промышленных гидроприводов и гидроавтоматики | Radial piston hydraulic machine |
SU733386A1 (en) * | 1977-12-22 | 1981-11-23 | Всесоюзный научно-исследовательский и проектно-конструкторский институт промышленных гидроприводов и гидроавтоматики | Radial piston hydromachine |
SU769070A1 (en) * | 1978-01-04 | 1980-10-07 | Всесоюзный научно-исследовательский и проектно-конструкторский институт промышленных гидроприводов и гидроавтоматики | Radial-piston-type hydraulic machine |
SU1753016A1 (en) * | 1990-05-15 | 1992-08-07 | Всесоюзный научно-исследовательский и проектно-конструкторский институт промышленных гидроприводов и гидроавтоматики | Radial-piston eccentric hydraulic motor |
-
2010
- 2010-07-27 IT ITMO2010A000216A patent/IT1401175B1/en active
-
2011
- 2011-03-23 WO PCT/IB2011/051218 patent/WO2012014090A1/en active Application Filing
- 2011-03-23 EP EP11716053.1A patent/EP2598747B1/en active Active
Also Published As
Publication number | Publication date |
---|---|
IT1401175B1 (en) | 2013-07-12 |
WO2012014090A1 (en) | 2012-02-02 |
ITMO20100216A1 (en) | 2012-01-28 |
EP2598747A1 (en) | 2013-06-05 |
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