EP0270181A2 - Groupe de distribution rotatif pour des moteurs hydrauliques avec étanchéité par portée superficielle à révolution - Google Patents

Groupe de distribution rotatif pour des moteurs hydrauliques avec étanchéité par portée superficielle à révolution Download PDF

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Publication number
EP0270181A2
EP0270181A2 EP87202354A EP87202354A EP0270181A2 EP 0270181 A2 EP0270181 A2 EP 0270181A2 EP 87202354 A EP87202354 A EP 87202354A EP 87202354 A EP87202354 A EP 87202354A EP 0270181 A2 EP0270181 A2 EP 0270181A2
Authority
EP
European Patent Office
Prior art keywords
recesses
distributor disc
distributor
disc
ducts
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.)
Granted
Application number
EP87202354A
Other languages
German (de)
English (en)
Other versions
EP0270181B1 (fr
EP0270181A3 (en
Inventor
Ivano De Vietro
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Riva Calzoni SpA
Original Assignee
Riva Calzoni SpA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from IT8622592A external-priority patent/IT1214575B/it
Priority claimed from IT22344/87A external-priority patent/IT1222951B/it
Application filed by Riva Calzoni SpA filed Critical Riva Calzoni SpA
Priority to AT87202354T priority Critical patent/ATE76166T1/de
Publication of EP0270181A2 publication Critical patent/EP0270181A2/fr
Publication of EP0270181A3 publication Critical patent/EP0270181A3/en
Application granted granted Critical
Publication of EP0270181B1 publication Critical patent/EP0270181B1/fr
Expired legal-status Critical Current

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Classifications

    • 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
    • F03C1/0435—Particularities relating to the distribution members
    • F03C1/0444—Particularities relating to the distribution members to plate-like distribution members

Definitions

  • the invention relates to a rotary distribution group for hydraulic motors, more particularly of the radial piston kind, with orbiting sealing surfaces.
  • radial-piston hydraulic motors require a rotary distributor for successfully supplying and discharging the propulsors and thus driving the motor in rotation.
  • the distributor substantially comprises a disc rotating integrally with the drive shaft and formed with a pair of orifices communicating between an external manifold connected to the hydraulic ducts from the pressure supply and the discharge respectively, and the ducts supplying the individual propulsors in the motor body, thus connecting some of the ducts to the supply and some to the discharge.
  • the distributor disc has to slide between the flat surfaces of the members formed with the hydraulic ducts to be connected, and must ensure sealing-tightness to avoid a short-circuit of hydraulic fluid on the distributor surfaces.
  • the distributor disc is formed with surfaces exposed to the pressure of the hydraulic fluid so as to clasp together the sealing surfaces and also particularly during the starting-up phase, the outer casing of the distributor, constituting the supply manifold, advantageously has a ring formed with separate supply and discharge passages and resiliently urged against the surface of the distributor disc.
  • the surfaces in contact between the distributor disc and the components between which it is clamped are in contact with the hydraulic fluid in which the entire distributor group is immersed but owing to the axial thrust, which is brought about to ensure sealing­tightness, the lubricating fluid in known embodiments tends to flow away from the flat surfaces in contact.
  • the surfaces in order to obtain an optimum seal, are made very smooth, e.g. by lapping, and therefore cannot effectively retain the lubricating fluid. Owing to the friction the fluid becomes less viscous and is therefore even easier to expel from the surfaces in contact.
  • the distributor disc and the parts clamped against it must therefore be made of special materials with anti-wear characteristics, which are expensive.
  • the problem therefore is to provide a distributor for hydraulic motor which ensures optimum lubrication conditions on all the sliding surfaces thereof and also guarantees that the hydraulic thrust on its components is balanced in each phase of rotation.
  • the problem therefore is to provide a distributor for hydraulic motors which ensures optimum lubrication conditions on all the sliding surfaces thereof and also guarantees that the hydraulic thrust on its components is balanced in each phase of rotation.
  • the invention provides a rotary distribution group for hydraulic motors which comprises a revolving distributor disc coupled for rotation to the drive shaft and clamped between an axially movable reaction ring formed with separate passages connected to the ducts for supplying and discharging the hydraulic fluid, and a fixed distribution plate formed with outlet orifices for the ducts supply­ing and discharging hydraulic fluid to the motor propulsors, the distributor disc being formed with at least two independent orifices communicating between its opposite flat surfaces and respectively in contact with the reaction ring and with the distribution plate, corresponding to and the separate passages in the reaction ring and to the distribution plate, and thus driving the motor in rotation, continuous surfaces being present for bounding and separating the respective inlet areas of the orifices in the disc towards the reaction ring and towards the distribution plate, the surfaces having cross-sections shaped so that they are immersed in the hydraulic fluid at least once per revolution, ducts being also present for balancing the hydraulic pressure on the surfaces of the distributor disc, with respect to a
  • the surfaces of the distributor disc facing the reaction ring is formed with an annular cavity facing the orifices in the reaction ring which communicate with one of the ducts supplying hydraulic fluid, the cavity having an internal depression facing the passage or passages in the reaction ring which communicate with the other duct supplying hydraulic fluid, the cavity and the depression being separated from one another and bounded from the exterior by thin annular flanges abutting the surface of the reaction ring and sealing it, the cavity, the depression and the associated boundary flanges being eccentric relative to the axis of rotation of the distributor disc.
  • the eccentricity of the depression, the annular cavity and the associated boundary flanges is equal to or greater than the width of the flanges, in order to uncover the flange surfaces completely at each revolution.
  • the reaction ring has a central orifice communicating with one of the ducts supplying hydraulic fluid and a plurality of orifices disposed on a circumference concentric with the central orifice and communicating with the other duct supplying hydraulic fluid, the annular cavity in the distributor disc facing the plurality of orifices and the depression concentric therewith communicating with the central orifice.
  • the annular cavity in the distributor disc has a width greater than or equal to the diameter of the orifices along the circumference of the reaction ring plus twice the eccentricity thereof relative to the axis of rotation of the distributor disc, so that the apertures disposed along the circumference of the reaction ring remain facing the interior thereof during each phase of rotation.
  • the flat of the distributor facing the distribution plate is formed with a pair of arcuate-shaped cavities extending in diametrically opposite positions along a circumference and facing the outlet apertures of the ducts in the distributor plate, the shaped cavities being connected to the outlets of a duct coming from the eccentric annular cavity and a duct from the cavity inside the first cavity on the opposite surface of the distributor, arcuate recesses also being present and externally surrounding the shaped cavities along their entire length and communicating with the annular cavity or the depression opposite those communicating with the adjacent cavity, and blind recesses also being formed in the facing surfaces of the distributor disc and, the distribution plate opposite the boundary edges of the shaped cavities and the arcuate recesses and communicating at least once per revolution with a zone supplied with hydraulic fluid and adapted at least once per revolution to immerse the entire front surface of the distributor disc and the plate.
  • a first array of blind recesses is formed on the distribution plate corresponding to the arcuate recesses in the distributor disc and the outer edge thereof, the recesses being equal in number and diametrically opposite the outlet orifices of the ducts in the plate.
  • a second array of blind recesses is formed on the distribution plate and open on to the outer edge thereof and are disposed so as to correspond to and be separate from the first array of blind recesses and their inner edge extends radially corresponding to the outer edge of the first array of recesses.
  • a pair of blind recesses is formed on the distributor disc in the spaces between the arcuate recesses therein and extend radially towards the exterior as far as the outer edge of the arcuate recesses and towards the interior as far as the outer edge of the arcuate-shaped cavities.
  • a pair of blind recesses are formed on the surface of the distributor disc and open into the central orifice therein and are disposed in the space between the arcuate shaped cavities and extend radially corresponding to the inner edge thereof.
  • the flat surfaces of the distributor disc facing the distribution plate has a pair of arc-shaped cavities extending in diametrically opposite positions along a circumference eccentric with respect to the axis of rotation of the distributor disc and facing the outlet orifices of the ducts in the distribution plate, ducts coming from the opposite surface of the distributor opening into the arc-shaped cavities, and likewise eccentric arcuate recesses also being present and externally surrounding the arc cavities along their entire length and communicating with that one of the ducts which supplies the arc cavity opposite the adjacent cavity, blind recesses also being formed in the facing surfaces of the distributor disc and the distribution plate corresponding to the boundary edges of the shaped cavities and the arcuate recesses and communicating at least once per revolution with an area supplied with hydraulic fluid and with a proportion of the boundary surface of the shaped cavities and the arcuate recesses, and supplying hydraulic fluid at each revolution to the entire surface of the distributor disc facing the plate as a result of the eccentric motion of the cavities and recesses in the distributor
  • the shaped cavities and the arcuate recesses in the distributor disc have the same eccentricity and are concentric, the eccentricity being in the diametral plane of symmetry of the cavities and recesses.
  • a group of blind recesses are present on the distribution plate and aligned along a circumference having its centre on the axis of rotation of the distributor disc, corresponding to the arcuate recesses in the distributor disc and the outer edge thereof, the blind recesses being equal in number and in diametrically opposite positions to the outlet orifices of the ducts of the plate.
  • a pair of shaped blind recesses are present on the distributor disc in the spaces between the arcuate recesses and have a portion extending radially towards the exterior as far as the outer edge of the arcuate recesses and a portion extending internally as far as the central area of the arc-shaped cavities.
  • the recesses and cavities in the distributor disc and the distribution plate under conditions where hydraulic fluid is supplied under pressure to one of the supply ducts of the motor, are under conditions of equilibrium thrust on the disc with respect to its diametral planes in each phase of rotation.
  • rotary distributor in a radial-piston motor has an outer casing 1 secured to the motor body 2 and internally formed with ducts 3, 4 for supplying and discharging hydraulic fluid to and from the motor propulsors.
  • a distribution plate 5 is formed with orifices 6 connected to the ducts 7 supplying the individual propulsors, the plate abutting the distributor disc 8.
  • An external reaction ring 9 also abuts disc 8 on the opposite side from plate 5 and is coupled to an internal reaction ring 10 and comprises a preloading spring 11 adapted to clamp the reaction ring against the distributor disc.
  • Plate 5 is coupled for rotation to the motor body 2 by pins 12 or the like, whereas the distributor 8 is connected for rotation to the drive shaft via a splined shaft 13. Screws 14 secure the distributor casing 1 to the motor body 2.
  • the outer reaction ring 9 which can also in some embodiments be constructed in one piece with the internal reaction ring 10, is connected for rotation to the distributor casing 1 by a pin 15 or the like and is sealed by gaskets 16. It is formed with a plurality of orifices 17 for connecting an annular chamber 18 supplying body 2 to an annular cavity 19 in the rotary distributor, separately from the connection via its central passage 20.
  • the side of distributor 8 facing ring 9 is formed with an annular cavity 19 disposed so as to correspond to orifices 17, which are laid out as shown by a chain­dotted line in Fig. 2.
  • orifices 17 are disposed along a circumference centred on the axis of rotation of the distributor disc, whereas cavity 19 is disposed eccentrically with an eccentrically value "e".
  • the annular cavity 19 in disc 8 has a width greater than or equal to the diameter of the orifices along the circumference of the reaction ring plus twice the eccentricity "e".
  • a drainage groove 21 and associated discharge channels 22 are disposed concentrically with cavity 19 and are separated therefrom by an annular flange 23 which externally bounds cavity 19.
  • Cavity 19 is internally bounded by an annular flange 24 surrounding the central depression 25 opposite the outlet of the central passage 20 in the reaction ring.
  • Distributor 8 has through orifices 26, 27 opening respectively into one end of the central depression 25 and into the annular cavity 19 and communicating at the opposite end with shaped cavities 28 and 29, shown more clearly in Figs. 4 and 5.
  • Cavities 28, 29 are adapted to define the propulsor supply cycle and are surrounded by static-equilibrium recesses 30 and 31.
  • the recesses receive the outlets of secondary ducts 32 and 33, the other ends of which open respectively into cavity 19 and depression 25.
  • One recess is supplied with pressure fluid when the adjacent cavity 28 or 29 is discharged whereas the opposite cavity is under pressure. In this manner, the thrust given by the liquid to the surface of the recess balances the thrust of the liquid on the opposite side in cavity 28 or 29, thus balancing the distributor disc in every phase of rotation.
  • Fig. 6 is a front view of the distribution plate. It is formed with outlet orifices 34 of ducts 6 and recesses 35 and 36, recesses 35 being disposed inside the plate periphery whereas recesses 36 open towards the exterior of the periphery.
  • orifices 34 are disposed so as to correspond to the cavities 28 and 29i, which are respectively connected to the supply of pressure hydraulic fluid and to the discharge, thus controlling the rotation cycle or the motor.
  • Recesses 35 are disposed to correspond to recesses 30 and 31 and, since the hydraulic operating fluid present in recesses 30, 31 flows into them, the surface 37 of the distributor disc, which externally bounds recesses 30 and 31, is immersed in the hydraulic fluid and consequently lubricated.
  • Recesses 36 are used for immersing the outer flange of the disc in hydraulic fluid, by placing its surface in contact with the fluid present outside the distributor disc, at the drainage pressure.
  • the surfaces 38 separating recesses 30, 31 from cavities 28, 29 are lubricated by means of circular recesses 39 which at each revolution are connected to one of the orifices 34, as shown in the left part of Fig. 4, so that the fluid in the recesses immerses the surface of plate 5 corresponding to the circular recess 39, the surface of which is in contact with surfaces 38 during the rotation of disc 8.
  • recesses 40 are also present and open towards the central orifice 41 of the disc.
  • a spindle 13 is keyed in orifice 41, which contains hydraulic fluid at the drainage pressure, supplied via a duct 42.
  • Recesses 35 serve another purpose besides lubricating the respective surfaces. As shown on the right of Fig. 4, one recess 35 (reference 35a) is in the diametrically opposite position to an orifice 34a in plate 5. Consequently, when orifice 34a is hydraulically connected to the cavity 28 or 29 under pressure and adds its area to that of the cavity so as to exert thrust on the distributor disc, the recess 35a becomes correspondingly connected to the corresponding static equilibrium recess 30 or 31, thus adding its area to that of the recess and balancing the thrust. To this end, as shown in Fig. 6, a recess 35 is provided to correspond to each orifice 34.
  • FIGs. 8, 9, 10 and 11 show the distributor 8 according to an alternative embodiment of the invention; its surface facing the distributor plate 5 is formed with shaped cavities 28, 29a disposed on a circumference which is eccentric with respect to the axis of rotation of the distributor, the eccentricity being e1.
  • Recesses 39a which serve a similar purpose to the recesses 39 in the preceding embodiment, are disposed on a circumference concentric with the shaped cavities 28a, 29a and, in the present embodiment, have a shape comprising an oblong-section portion 39b extending along an arc of the aforementioned circumference and communicating with a circular portion 39c towards the interior.
  • Static balancing recesses 30a, 31a extend along the same circumference as portion 39b of recesses 39a, whereas a central cavity 41a, likewise eccentric, is present inside cavities 28a, 29a.
  • Recesses 35b disposed along a circumference coaxial with shaft 13 are present on the corresponding surface of distribution plate 5 facing the distributor 8 and illustrated in this embodiment in Figs. 10 and 11.
  • Recesses 35b are narrower than in the preceding embodiment and are disposed so as to correspond to the balancing recesses 30a, 31a or distributor 8; the balance recesses 30a, 31a are given a width in the radial direction such that in every phase of rotation they communicate with recesses 35b and also move orbitally owing to their eccentricity e.
  • the peripheral recesses 36 are not necessary in the present embodiment.
  • the lubrication obtained by orbital motion of the surfaces in contact between distributor 8 and plate 5 is particularly efficient and is particularly suitable for high-performance hydraulic motors which have to operate under difficult conditions, since at each revolution it ensures optimum exchange of lubricating fluid between the surfaces, resulting in optimum cooling and lubrication, in the same way as for the opposite surface of distributor 8 in contact with ring 9.
  • the distributor disc is lubricated on all its sliding surfaces, while separating the hydraulic-fluid supply areas from the drainage areas, thus eliminating the risk of seizing between the surfaces in contact.
  • the surfaces can therefore be made of lower-cost material e.g. hardened by heat treatment only, without the need for special alloys or facings of anti-wear material.
  • the distributor disc and the associated distribution plate are shaped so that the thrust is completely balanced during the entire revolution, thus ensuring that the wear on the sliding surfaces does not reduce the flatness thereof, and thus prolonging their life.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
EP19870202354 1986-12-05 1987-11-30 Groupe de distribution rotatif pour des moteurs hydrauliques avec étanchéité par portée superficielle à révolution Expired EP0270181B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87202354T ATE76166T1 (de) 1986-12-05 1987-11-30 Rotierende verteilungsgruppe fuer hydraulische motoren mit umlaufender flaechendichtung.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
IT2259286 1986-12-05
IT8622592A IT1214575B (it) 1986-12-05 1986-12-05 Gruppo di distribuzione rotante per motori idraulici dotato di lubrificazione continua sulle superfici di tenuta a strisciamento.
IT22344/87A IT1222951B (it) 1987-10-20 1987-10-20 Gruppo di distribuzione rotante per motori idraulici con superfici di tenuta orbitanti
IT2234487 1987-10-20

Publications (3)

Publication Number Publication Date
EP0270181A2 true EP0270181A2 (fr) 1988-06-08
EP0270181A3 EP0270181A3 (en) 1990-01-31
EP0270181B1 EP0270181B1 (fr) 1992-05-13

Family

ID=26328164

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19870202354 Expired EP0270181B1 (fr) 1986-12-05 1987-11-30 Groupe de distribution rotatif pour des moteurs hydrauliques avec étanchéité par portée superficielle à révolution

Country Status (3)

Country Link
EP (1) EP0270181B1 (fr)
DE (1) DE3779062D1 (fr)
ES (1) ES2030714T3 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007122644A1 (fr) * 2006-04-20 2007-11-01 S.A.I. Societa' Apparecchiature Idrauliche S.P.A. Moteur hydraulique à cylindres radiaux
CN102345554A (zh) * 2006-04-20 2012-02-08 S.A.I会水利设备股份公司 星形缸体液压
US20130125844A1 (en) * 2010-07-30 2013-05-23 Wanhua Su Self-adaptive hydraulic variable valve timing system for diesel engine and control method
CN114320730A (zh) * 2021-12-23 2022-04-12 宁波丹顿液压传动有限公司 一种双列十缸径向柱塞马达配油系统

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2052305A1 (fr) * 1969-11-07 1971-05-13
FR2381173A1 (fr) * 1977-02-17 1978-09-15 Riva Calzoni Spa Distributeur pour moteurs hydrauliques

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2052305A1 (fr) * 1969-11-07 1971-05-13
FR2381173A1 (fr) * 1977-02-17 1978-09-15 Riva Calzoni Spa Distributeur pour moteurs hydrauliques

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007122644A1 (fr) * 2006-04-20 2007-11-01 S.A.I. Societa' Apparecchiature Idrauliche S.P.A. Moteur hydraulique à cylindres radiaux
EP2249026A3 (fr) * 2006-04-20 2011-02-09 S.A.I. Societa' Apparecchiature Idrauliche S.P.A. Moteur hydraulique doté de cylindres radiaux
CN102345554A (zh) * 2006-04-20 2012-02-08 S.A.I会水利设备股份公司 星形缸体液压
US8206130B2 (en) 2006-04-20 2012-06-26 S.A.I. Societa' Apparecchiature Idrauliche S.P.A. Hydraulic motor having radial cylinders capable of high speed rotation
CN101421510B (zh) * 2006-04-20 2013-01-30 S.A.I会水利设备股份公司 星形缸体液压马达
CN102345554B (zh) * 2006-04-20 2014-05-07 S.A.I会水利设备股份公司 星形缸体液压马达
US20130125844A1 (en) * 2010-07-30 2013-05-23 Wanhua Su Self-adaptive hydraulic variable valve timing system for diesel engine and control method
US9163531B2 (en) * 2010-07-30 2015-10-20 Wanhua Su Self-adaptive hydraulic variable valve timing system for diesel engine and control method
CN114320730A (zh) * 2021-12-23 2022-04-12 宁波丹顿液压传动有限公司 一种双列十缸径向柱塞马达配油系统
CN114320730B (zh) * 2021-12-23 2023-11-24 宁波丹顿液压传动有限公司 一种双列十缸径向柱塞马达配油系统

Also Published As

Publication number Publication date
DE3779062D1 (de) 1992-06-17
EP0270181B1 (fr) 1992-05-13
ES2030714T3 (es) 1992-11-16
EP0270181A3 (en) 1990-01-31

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