EP0269474A1 - Hydrostatisches Werkzeugbauteil mit Axialschieber und Axialanpressung - Google Patents

Hydrostatisches Werkzeugbauteil mit Axialschieber und Axialanpressung Download PDF

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Publication number
EP0269474A1
EP0269474A1 EP87402326A EP87402326A EP0269474A1 EP 0269474 A1 EP0269474 A1 EP 0269474A1 EP 87402326 A EP87402326 A EP 87402326A EP 87402326 A EP87402326 A EP 87402326A EP 0269474 A1 EP0269474 A1 EP 0269474A1
Authority
EP
European Patent Office
Prior art keywords
pallet
carrier
track
pallets
chambers
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
EP87402326A
Other languages
English (en)
French (fr)
Other versions
EP0269474B1 (de
Inventor
Daniel Leroy
Jean-Louis Maupu
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.)
Compagnie de Construction Mecanique Sulzer
Institut National de Recherche sur les Transports et leur Securite INRETS
Original Assignee
Compagnie de Construction Mecanique Sulzer
Institut National de Recherche sur les Transports et leur Securite INRETS
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 Compagnie de Construction Mecanique Sulzer, Institut National de Recherche sur les Transports et leur Securite INRETS filed Critical Compagnie de Construction Mecanique Sulzer
Publication of EP0269474A1 publication Critical patent/EP0269474A1/de
Application granted granted Critical
Publication of EP0269474B1 publication Critical patent/EP0269474B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3448—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member with axially movable vanes

Definitions

  • the present invention relates to a hydrostatic component with axial vanes such as a pump or motor.
  • a hydrostatic component with axial vanes is formed by two coaxial parts which are free to present a relative speed of rotation about their common axis.
  • One of the parts called in practice pallet carriers, comprises at least one annular series of housings in which are engaged pallets adapted to slide axially therein.
  • the other of the parts called track carrier, carries axially opposite the housings an annular guide track against which the pallets are intended to be axially resiliently pressed; this track comprises an annular series of recesses or working chambers alternating with rest surfaces; at the circumferential ends of each chamber open channels ensuring either a supply or a discharge of fluid.
  • Known pallets are thin parallelepipeds applied by a section on the track, most often by elastic members bearing on the bottom of the housings.
  • the pallets either retract into the housings when they run along the rest surfaces, or protrude into the working chambers: the track acts on these pallets like cams.
  • pressurized fluid arriving in a chamber acts circumferentially on the sides of the pallets projecting in this chamber, and causes the rotation of the pallet carrier relative to the track carrier, fluid at lower pressure being evacuated to the other end circumferential of the chamber.
  • pump mode the rotation of the pallet carrier relative to the track carrier causes, via the vanes projecting from a chamber, a suction of low pressure fluid at a circumferential end of the chamber and a discharge of fluid at higher pressure at the other circumferential end of this chamber.
  • the pallets In order to properly maintain the pallets perpendicular to the track it is necessary that they remain permanently engaged in their housing over a significant fraction of their height (dimension oriented perpendicular to the track). As a result, the pallets must have a significant height and a significant mass: this implies for the pallet carrier a sometimes considerable bulk perpendicular to the track, therefore a high mass, and this too can limit the maximum admissible pressure.
  • the present invention aims to overcome the aforementioned drawbacks by ensuring, in a hydrostatic component with axial vanes, an improved seal between the pallet carrier and the track carrier, near the guide track, the pallets and their housings.
  • a hydrostatic component comprising in a chamber two coaxial parts admitting a relative rotation, including a track carrier on which is formed an annular generally transverse guide track determining working chambers, and a pallet holder determining jointly with the holder -track an annular fluid vein and in which are formed housings opening axially opposite this track, pallets being engaged in the housings and being axially pressed by a edge against the track by circumferentially dividing the fluid vein, characterized in that the pallet holder comprises, on a transverse face opposite a support flange and axially opposite to the track carrier, an annular plurality of chambers insulated in a sealed manner with respect to the rest of the flange / pallet carrier interface at least in the direction residual interface chamber hydraulically communicating with the fluid vein, the total transverse area of this plurality of chambers being greater than the transverse area of the fluid vein, by a value sufficient for the pallet carrier and the track carrier are faced, by substantially transverse spans.
  • the pallet holder advantageously has an axial clearance, for example using grooves.
  • the hydraulic insulation limited to only the residual chamber-interface direction offers the possibility of a possible force-feeding of the pallet housing.
  • the plurality of chambers is the same number as the pallets. It can also correspond to a submultiple of this number.
  • the component is advantageously split in symmetry with respect to a transverse plane passing through the track carrier.
  • Such a component is described in the European patent application of the same day filed under priority of the French application 86-14.385 of October 16, 1986.
  • Each pallet housing opens into one of said chambers, the communication of each chamber with the fluid stream taking place through a pallet housing thus passing axially right through the pallet holder; machining is thereby simplified and the pallet application springs bear on the support flange independently of the pallet holder; -
  • the chambers alternate angularly with the pallet housings, channels being provided between the housings to connect the chambers and the fluid stream; a very good balance is thus obtained;
  • the fluid stream is delimited by a toroidal recess of the pallet holder into which penetrates a crown of the track holder on which the track is formed; all or part of the fluid stream can also be cleaned in the track carrier;
  • the pallet carrier is faced axially with the track carrier by coplanar annular bearing surfaces radially arranged on either side of the crown; these spans are generally very flat or conical (centering effect), coplanar or not.
  • the static sealing of the chambers relative to the residual interface can be obtained, in practice, either by O-rings (with anti-extrusion part if necessary), or by cups with flexible edges forming lips.
  • the invention also aims to overcome other aforementioned drawbacks by making it possible to lighten the pallets (and therefore to reduce the thrust of the associated springs, the contact pressure of these pallets on the opposite track as well as the mechanical losses by friction in resulting, while increasing the retraction speeds of the pallets in their housings or protruding and therefore reducing the acceleration forces) as well as the associated pallet carrier, to improve the guidance of the pallets during retraction, to allow the use of elastic ramps on the track, to simplify the machining of the pallet carrier, to reduce pressure losses in transfer conduits, to reduce creepage distances and to improve the resistance of the pallets under the pressure.
  • the invention proposes, according to an original characteristic in itself, a pallet for hydrostatic component comprising a wafer intended to be applied against a track determining working chambers and to slide along it, characterized in that it has the shape of a C, said edge being formed on a pallet body between two parallel branches oriented perpendicularly to this edge and intended to laterally follow said track on either side thereof.
  • the invention also provides a hydrostatic component of the aforementioned type including such paddles.
  • Such a pallet reduces the functional games which generate leaks (it runs along the track on three sides). Deformations of the pallet carrier do not increase leakage at the pallet; moreover, these leaks are further reduced with a one-piece pallet carrier. It should be noted that a single pallet may be sufficient in the working position in each chamber, thereby saving space for the cams, or reducing the number of pallets. This also allows an increase in working pressure.
  • the pallet can be hollowed out at the rear: the volume of the pallet can be little more than the strict necessary for closing the fluid stream in the working chambers.
  • the reduction in the weight of the pallets reduces the shocks which can occur on cams in several sections in the case of hydrostatic components with variable displacement.
  • this reduction in weight allows a reduction in the cam surfaces (with increased passage for the fluid entering and leaving the vein) and a reduction in the force of the veneer springs for the pallets on the track, (d ' where a reduction in the friction torque of empty pallets).
  • the machining of the pallets according to the invention is simplified thanks to a possible widening of the tolerances (possible clearances of the pallets in their housings); they can be obtained by molding or sintering then rectification on the two support faces in the pallet carrier, and rectification of the support edges on the track carrier. There is also a reduction in the liveliness of several edges or angles.
  • the pallet comprises, in its part facing the bottom of the housing, two longitudinal support wings bordering a longitudinal central groove communicating by balancing channels with the support edge against the track; - This support edge is locally convex in the vicinity of its connection to said branches; - the branches of the pallet are hollowed out (or even drilled) in their faces laterally bordering the track carrier.
  • Two components of the aforementioned type are advantageously matched so as to include two pallet carriers on either side of a central track carrier (or two track carriers on either side of a central pallet carrier; rooms on the pallet carrier then no longer have a raison d' desire but there are some at the rear of the track carrier).
  • Such an application in the very general context of a hydrostatic differential with variable displacement, is described in a parallel application filed the same day.
  • Figures 1 to 3 show a hydrostatic component with axial vanes suitable for operating as a motor or pump.
  • this component can, in a variant not shown, constitute only a hydrostatic module within a more complex hydrostatic component.
  • This component has two coaxial parts 1 and 2 adapted to have a relative rotation relative to their common axis.
  • Part 1 called pallet carrier
  • Part 2 is here coupled in rotation to an outer casing 3 by means of grooves 4 allowing an axial play of the pallet carrier.
  • This envelope has a cylindrical wall 5 and a transverse flange 6.
  • the part 2, called track carrier, here is integral with a shaft or axis 7 and the envelope is held axially in position relative to the track carrier 2 by means not shown of any known type, or by simple symmetry.
  • the track carrier 2 has a transverse face with respect to which a ring 8 projects axially in the pallet carrier. This transverse face is thus divided into two annular surfaces 9 and 10.
  • the crown 8 has a generally transverse face 11 called track, which has in known manner, parallel to the axis, an annular series of recesses or pressure chambers 12 (see FIG. 2B ), in the circumferential ends of which open 12 ⁇ channels for supplying or discharging fluid from a hydraulic circuit internal to the track carrier of any known type (not shown).
  • a chamber 12 has a bottom 12A connected to plates 12B, circumferentially separating the chambers 12, by ramps 12 C inclined relative to the axis, arranged radially on either side cavities 12D into which the channels 12 ⁇ open.
  • This track is connected to surfaces 9 and 10 by lateral faces 13 and 14, here cylindrical.
  • the pallet carrier 1 has a toroidal recess 15 of complementary cross section, apart from clearances, to the cross section of the crown 8 outside a recess.
  • This toroidal recess has a bottom 16 and two side walls 17 and 18, here cylindrical, along the side faces 13 and 14.
  • This recess 15 is bordered radially by two transverse annular bearings 19 and 20 adapted to come axially into abutment against the surfaces 9 and 10 of the track carrier.
  • this pallet carrier (see Figure 9) are housed 21 which pass through it right through and which are regularly distributed angularly. These housings have a radial dimension greater than the width of the toric recess and therefore extend towards the track carrier, on either side radially of this toric recess, by facing grooves or grooves 22 and 23 whose depth radial is less than the radial dimension of the annular bearings 19 and 20.
  • chambers 25 On the transverse face 24 of the pallet carrier opposite the track carrier are formed chambers 25 of larger cross section than the housings. These chambers are each and individually in hydraulic communication with the transverse bottom of the toroidal recess 15, here through the associated housing 21.
  • the total cross-sectional area of this series of chambers 25 is greater than the cross-sectional area of the bottom of the toroidal recess as a result of which, whatever the local value, high or low, of the pressure, there is plating without deformation of the pallet carrier on the track carrier by the transverse annular bearings 19 and 20 also forming sealing surfaces for the fluid stream, a possible deformation being in fact transferred to the flange 6 of the envelope, without consequences for leaks.
  • Each chamber 25 is sealed with respect to the residual flange 6 / pallet carrier interface by a seal 27 associated with an anti-extrusion part 26 provided with a recess 41.
  • This part 26 comprises blind holes 40 whose role will appear more far and a flange 42 projecting laterally from the recess which prevents the seal from extruding out of the chamber 25.
  • This chamber is at variable pressure while the flange interface 6 / pallet carrier 1 is at the drainage pressure ; this part is pierced with at least one hole 43 establishing in a basin 44 provided at the rear of the part 26 the same pressure as in the housing: this prevents the part 26 from sinking into the housing 21 in if the drainage pressure comes to be higher than that of the housing. After reversing the pressure, the pressure drop in this bore produces a rapid priming of the sealing plating of the collar 42 on the flange 6.
  • a pallet 29 has two parallel branches 30 adapted to slide in the grooves 22 and 23, connected by a pallet body 31.
  • the spacing of the branches 30 is equal to the radial width of the 'O-ring recess 15 (see Figure 2C).
  • the pallet body 31 comprises a section 32 intended to come into abutment against the track and has curved chamfers 33 near the branches 30 facilitating the circumferential sliding of the pallet on the inclined ramps 12C.
  • these ramps may be inserts, preferably elastic (in spring steel for example).
  • the pallet body 31 includes, behind this edge 32, a longitudinal groove 34 bordered by flanks 35 and 36 intended to guide the pallet in a housing 21 and to obstruct the fluid stream.
  • Ports or channels 37 allow a transfer of hydraulic oil during the axial movements of the pallet in its housing: they connect the edge 32 to the groove 34. They also reduce the placing of the pallets against the track by means of hydraulic balancing.
  • a pallet 29 is shown in a projecting configuration: the hatching oriented downwards to the right designate section 32, the tight hatching designates the support area of the pallet in the housing and the grooves of the pallet carrier (it is supported on three sides of the fluid stream), and the hatching oriented downwards at left designating faces 30A of the branches which run along the lateral faces of the crown 8 (not shown).
  • Recesses 38, or even holes 39 can be made in the branches 30 of the pallets (see FIGS. 7 and 8) to reduce the force of radial plating of these branches against the crown 8 and the deformation of these branches under the effect of pressure.
  • Figure 6 describes an alternative embodiment of the pallet carrier where the grooves 22 ⁇ and 23 ⁇ do not open on the runway side so as not to affect the seal.
  • the O-ring and the associated anti-extrusion part are replaced by a sealing cup 50 provided with a flexible peripheral edge forming a lip 51 extending towards the pallet 52 and the door -track, adapted to be pressed towards the wall of the chamber 25, as well as lugs 53 adapted to engage inside the springs 29 A. It comprises also at least one bore 55 and a rear chamber 54.
  • the pallet 52 has parallel rear flanks and have holes 39 in its branches.
  • the housings 21 ⁇ of the pallets (here closed at their rear part) and the chambers 25 ⁇ , provided with parts 50 ⁇ , are angularly offset, the latter being directly supplied with pressure by conduits 60 opening into the bottom 16 of the toroidal recess 15. This results in better balancing in deformation of the pallet holder (bending in a transverse plane).
  • the pallets 52 are not supported on the parts 50 ⁇ , but on the bottom of the housings 21 ⁇ provided with ergors 53.
  • Figures 16 to 19 show a variant of Figures 1 to 10 (with the addition of the index ⁇ to the corresponding reference figures) in which the pallets 70 have no branches and have a radial dimension equal to that of the crown 8 or the O-ring recess 15. There are no longer grooves 22 or 23 running along the crown 8.
  • Figures 20 and 21 show the pressure distributions within the pallet carriers of the above embodiments. It is checked that the pallets in the retraction phase are axially balanced while, because the overall section of the chambers 25 or 25 ⁇ is greater than that of the bottom 16 of the toroidal recess 15, there is axial plating at any point of the pallet carrier against the track carrier, without significant local contact pressure.
  • FIGS. 1 and 3, and 7 and 8 have been represented and described very schematically for all that relates to their characteristics known per se which do not interact with the invention.
  • such modules are paired so as to comprise two pallet carriers on either side of a central track carrier with two tracks, the vertical lines in dashed lines bordering on the right the figures. 1 and 3, in particular corresponding to planes of symmetry.
  • a plurality of hydrostatic modules of the type shown between the vertical dashed lines in these figures can be combined as desired.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
EP19870402326 1986-10-16 1987-10-16 Hydrostatisches Werkzeugbauteil mit Axialschieber und Axialanpressung Expired - Lifetime EP0269474B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8614386 1986-10-16
FR8614386A FR2605360B1 (fr) 1986-10-16 1986-10-16 Palette pour composant hydrostatique et composant hydrostatique le comportant

Publications (2)

Publication Number Publication Date
EP0269474A1 true EP0269474A1 (de) 1988-06-01
EP0269474B1 EP0269474B1 (de) 1991-04-17

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ID=9339907

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19870402326 Expired - Lifetime EP0269474B1 (de) 1986-10-16 1987-10-16 Hydrostatisches Werkzeugbauteil mit Axialschieber und Axialanpressung

Country Status (3)

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EP (1) EP0269474B1 (de)
DE (1) DE3769439D1 (de)
FR (1) FR2605360B1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008054244A1 (fr) 2006-10-30 2008-05-08 Stroganov Alexander Anatolievi Machine rotative à palette coulissante

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL270691A (de) * 1900-01-01
FR1073297A (fr) * 1953-03-27 1954-09-21 Nouveau moteur actionné par un fluide, sous pression, liquide ou gazeux
US3099964A (en) * 1958-03-13 1963-08-06 Eickmann Karl Vanes for rotary vane machine supported in balance and in stability and in less friction
FR1428760A (fr) * 1965-03-18 1966-02-18 Towler Brothers Patents Ltd Perfectionnements aux pompes à palettes
US3250223A (en) * 1962-05-14 1966-05-10 Trojan Corp Vane impulsion apparatus
DE2100032A1 (de) * 1970-01-15 1971-07-22 Eickmann, Karl, Hayama, Kanagawa (Japan) Selbstandruckendes, axialbestromtes von Druckfluid durchstromtes Zellenaggre gat
BE787353A (fr) * 1972-08-09 1972-12-01 Savikurki Auvo A Compresseur axial.
DE2319496A1 (de) * 1973-04-17 1974-11-07 Regar Karl Nikolaus Dipl Ing Fluegelzellenpumpe axialer bauart
FR2283307A1 (fr) * 1974-08-28 1976-03-26 Karpisek Ladislav Machines rotatives a fluide, generatrices ou motrices
US4089305A (en) * 1975-04-03 1978-05-16 Gregg Oscar P Rotary internal combustion engine
DE2914668A1 (de) * 1979-04-11 1980-11-06 Wolfhart Neun Axialfluegelkammerpumpe
EP0048673A1 (de) * 1980-09-19 1982-03-31 COMPAGNIE DE CONSTRUCTION MECANIQUE SULZER Société anonyme dite: Schieber-Statorwand-Kombination für hydraulische Drehkolben

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL270691A (de) * 1900-01-01
FR1073297A (fr) * 1953-03-27 1954-09-21 Nouveau moteur actionné par un fluide, sous pression, liquide ou gazeux
US3099964A (en) * 1958-03-13 1963-08-06 Eickmann Karl Vanes for rotary vane machine supported in balance and in stability and in less friction
US3250223A (en) * 1962-05-14 1966-05-10 Trojan Corp Vane impulsion apparatus
FR1428760A (fr) * 1965-03-18 1966-02-18 Towler Brothers Patents Ltd Perfectionnements aux pompes à palettes
DE2100032A1 (de) * 1970-01-15 1971-07-22 Eickmann, Karl, Hayama, Kanagawa (Japan) Selbstandruckendes, axialbestromtes von Druckfluid durchstromtes Zellenaggre gat
BE787353A (fr) * 1972-08-09 1972-12-01 Savikurki Auvo A Compresseur axial.
DE2319496A1 (de) * 1973-04-17 1974-11-07 Regar Karl Nikolaus Dipl Ing Fluegelzellenpumpe axialer bauart
FR2283307A1 (fr) * 1974-08-28 1976-03-26 Karpisek Ladislav Machines rotatives a fluide, generatrices ou motrices
US4089305A (en) * 1975-04-03 1978-05-16 Gregg Oscar P Rotary internal combustion engine
DE2914668A1 (de) * 1979-04-11 1980-11-06 Wolfhart Neun Axialfluegelkammerpumpe
EP0048673A1 (de) * 1980-09-19 1982-03-31 COMPAGNIE DE CONSTRUCTION MECANIQUE SULZER Société anonyme dite: Schieber-Statorwand-Kombination für hydraulische Drehkolben

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008054244A1 (fr) 2006-10-30 2008-05-08 Stroganov Alexander Anatolievi Machine rotative à palette coulissante
EP2090782A1 (de) * 2006-10-30 2009-08-19 Alexander Anatolyevich Stroganov Drehschiebermaschine
EA013809B1 (ru) * 2006-10-30 2010-08-30 Александр Анатольевич СТРОГАНОВ Роторная шиберная машина
EP2090782A4 (de) * 2006-10-30 2012-03-07 Alexander Anatolyevich Stroganov Drehschiebermaschine
CN101636587B (zh) * 2006-10-30 2012-08-08 亚历山大·阿纳托莱维齐·斯特罗加诺夫 转子叶片机

Also Published As

Publication number Publication date
FR2605360B1 (fr) 1991-04-12
EP0269474B1 (de) 1991-04-17
FR2605360A1 (fr) 1988-04-22
DE3769439D1 (de) 1991-05-23

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