WO2009046558A1 - Dispositif de lubrification des points d'appui d'une bielle, son procédé de fonctionnement et pompe à piston(s) plongeur(s) munie d'un tel dispositif - Google Patents

Dispositif de lubrification des points d'appui d'une bielle, son procédé de fonctionnement et pompe à piston(s) plongeur(s) munie d'un tel dispositif Download PDF

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Publication number
WO2009046558A1
WO2009046558A1 PCT/CH2008/000420 CH2008000420W WO2009046558A1 WO 2009046558 A1 WO2009046558 A1 WO 2009046558A1 CH 2008000420 W CH2008000420 W CH 2008000420W WO 2009046558 A1 WO2009046558 A1 WO 2009046558A1
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WO
WIPO (PCT)
Prior art keywords
bearing
lubricant
connecting rod
lubricating
gap
Prior art date
Application number
PCT/CH2008/000420
Other languages
German (de)
English (en)
Inventor
Anton Steiger
Original Assignee
Anton Steiger
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 Anton Steiger filed Critical Anton Steiger
Publication of WO2009046558A1 publication Critical patent/WO2009046558A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0082—Details
    • F01B3/0085—Pistons
    • F01B3/0088—Piston shoe retaining means
    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • 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
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/144—Adaptation of piston-rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J1/00—Pistons; Trunk pistons; Plungers
    • F16J1/10—Connection to driving members
    • F16J1/14—Connection to driving members with connecting-rods, i.e. pivotal connections
    • F16J1/22—Connection to driving members with connecting-rods, i.e. pivotal connections with universal joint, e.g. ball-joint
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J7/00—Piston-rods

Definitions

  • the invention relates to a device for lubricating the bearing points of a connecting rod with oscillating load and an operating method therefor according to claims 1 and 14.
  • the invention further relates to a connecting rod pump with such a lubricating device according to claim 11 and a bearing assembly according to claim 19.
  • Dynamic plain bearings with two bearing elements which move continuously relative to one another and a lubricant which flows through a lubricating gap between the bearing elements and which builds up a lubricant film, in particular oil, are generally known. They are used in particular for non-reciprocating movements of the bearing elements, e.g. For lubricating bearings with rotating, approximately constantly loaded axles. The lubricant is supplied continuously and taken from the relative to each other in always the same direction moving bearing elements and distributed over the lubrication gap, which thereby has an approximately constant thickness. Only by the uniform rotational movement of the bearing elements succeed in these cases, the structure of a lubricant film.
  • the above-mentioned problem means that the load on the bearings of those elements which transmit force to the plugs must be kept low.
  • This relates in particular to a power transmission with reciprocating moving, in particular pivoted about an axis connecting rods.
  • the pressures to be generated by such pumps for liquids are limited to a few hundred bars because of the load limits of the hitherto existing transmission elements between the drive and the plunger.
  • GB 694,521 discloses a floating bearing for a substantially constant loaded rotating shaft in which continuously introduced lubricant from a plurality of circumferentially equidistant feeds in a lubrication gap between the cylindrical shaft and the hollow cylindrical bearing bush and over compared to the circumference relatively wide axially extending grooves drains off in the axial direction.
  • check valves are arranged in each case, which serve to prevent short-term disturbances, such as a deflection of the shaft in the radial direction, the lubricant drain and to avoid contact of the shaft with the bearing bush.
  • This arrangement is not suitable for oscillating moving and loaded bearings, since here the lubricant film is built up in the circumferential direction only by the relative movement of shaft and bearing bush. At a standstill or with small reciprocating movements, therefore, the lubricant flows off in the axial direction, so that no coherent lubricant film is built up.
  • the invention is therefore an object of the invention to provide a device for lubricating the bearings of pendulum moving and oscillating stress exposed connecting rods, in which a secure lubrication is ensured even under high load.
  • the transverse forces arising as a result of the connecting-rod deflection and acting on the plungers, consisting, on the one hand, of frictional forces are largely eliminated due to a lack of lubricant film thickness and those due to the con-rod deflection should be kept as low as possible.
  • an operating method for such a device is to be specified.
  • Particularly advantageous is a plunger pump with a lubricating device according to the invention according to claim 11.
  • plunger is used synonymously with piston or plunger and plunger pump synonymous with axial piston pump.
  • the invention uses a different mechanism of action for the production of a lubricant film which does not tear off at the reversal points despite alternating load and regular stoppage of motion.
  • By appropriate geometric design ensures that the lubricant can flow only through the lubrication gap. It is therefore forced out of the lubricant supply into the lubrication gap and flows off at the periphery of the bearing surface or the lubrication gap.
  • the bearings and their abutment are therefore preferably designed so that the flow resistance for the lubricant from the mouth region of the lubricant supply from in all directions is substantially equal.
  • the mouth region is such that even under load a largely symmetrical force and thus gap thickness distribution is realized, ie on the axis of the connecting rod.
  • the preferred spring-loaded check valve prevents the backflow of lubricant from the lubricant pocket into the lubricant supply when the pressure of the lubricant in the lubricant pocket exceeds the supply pressure of the lubricant, ie in the phases of heavier loading of a cycle of movement. In this way it can be prevented that the thickness of the lubricating gap decreases to zero and it is ensured that the lubricant flows only through the lubricating gap, but not through the supply.
  • the lubricant pocket serves as a reservoir for the lubricant and facilitates the preferably very rapid refilling of the lubrication gap with decreasing load.
  • a lubricating film is thus present in the lubrication gap, lubrication is improved, thus increasing the service life of the bearing points and the load capacity.
  • Undesirable lateral forces cause mechanical shear friction, due to temporarily missing lubricating film, are completely avoided.
  • the inventive lubricating device is designed in particular for the bearing points of a connecting rod, which is exposed during a movement cycle alternately stronger and weaker load on pressure or train, in particular in the direction of the connecting rod. At the same time, the relative movements between the bearings on the connecting rod are limited to small angles.
  • the design of the bearings with a check valve in the lubricant supply and a lubricant bag with sharp-edged crossing to increase the Abströmwiderstands is basically suitable for all articulated arrangements of two with a limited angular range with one or two degrees of freedom against each other pivotable elements.
  • phase of heavier load is, for example, the phase in which the connecting rod pushes the plunger into its guide and thus the bearing is subjected to pressure.
  • phase of weaker loading is accordingly the phase in which the plunger is pulled out of the guide again.
  • the geometric characteristics of the lubricating gap or the lubricant pocket influencing the flow properties, the elastic properties of the lubricant, such as its viscosity and compressibility, and the actual load on the bearing arrangement and their temporal distribution within a movement cycle are matched to one another during the phase Load does not run through the narrowing lubrication gap all the lubricant present in the lubrication gap.
  • the thickness of the lubricating gap, despite the lubricant flowing through the lubricating gap is greater than a predetermined minimum thickness at any point in time of the movement cycle. This is for example between 0.001 and 0.01 mm and is preferably 0.005 mm.
  • the flow rate of the lubricant is determined, inter alia, by the shaping of the lubricating gap and the lubricant pocket influencing the flow characteristics.
  • the lubricant pocket in the border region to the lubrication gap preferably has a clearly trained transition edge (in contrast to a smooth transition).
  • the surface of the lubricating gap adjoining the lubricant pocket and a side wall of the lubricant pocket strike one another at a non-zero angle ⁇ , which is preferably approximately 80 to 90 °.
  • the lubricant flows along said surface of the lubricating gap, so that a pronounced contraction effect arises with respect to the lubricant flowing into the lubricating gap.
  • the bag or its side wall is located within the active bearing surface, ie that surface within the contact surface of the bearing and its counter bearing, which is exposed to the load.
  • one of the bearing elements has a drain groove which surrounds the lubricant pocket in its circumferential direction and is spaced therefrom.
  • the groove can be located in that bearing element in which the lubricant pocket is also formed, or in the other bearing element.
  • the groove is located in particular transversely to the outflow direction of the lubricant.
  • the depth of the lubricant bag is preferably such that a clear transition edge can be formed.
  • the lubricant pocket is not so deep that its volume completely absorbs the pressurized lubricant during the period of heavier loading so that drainage through the lubrication gap would be suppressed.
  • the pocket diameter largely determines the pressure prevailing in the pocket.
  • the ratio of plunger diameter to pocket diameter is one of the possible delivery pressure. size.
  • the optimum ratio between delivery pressure and pocket pressure depends on various considerations, for example, a smaller pocket diameter leads to a larger bag pressure, but also reduces the cross section when flowing into the lubrication gap and thus increases its flow resistance. Other parameters include the compressibility of the lubricant.
  • the supply pressure of the lubricant is preferably selected so that the lubricant during the phase weaker load within this Movement cycle acting on the bearing elements hydraulic force is greater than the sum of all other forces that press the bearings and counter-bearing during this phase against each other.
  • the feed amount of the lubricant is selected so that the thickness of the lubricating gap increases again during the phase of the weaker load up to a maximum thickness.
  • the bearings and abutments of the connecting rod lead relative to each other through a pendulum movement with a limited maximum deflection. This is many times smaller than the circumferential extent of the active bearing surface.
  • the invention a significant increase in the pressure on the plunger up to 1000 bar and more can be achieved in particular with plunger pumps with swash plate drive and a power transmission by means of connecting rods between swash plate and plungers.
  • the maximum deflection relative to the central axis of the connecting rod is preferably about +/- 2-5% of the stroke of the plunger.
  • the basic structure of such a compressor with a drive of the plunger on a swash plate and connecting rod is known for example from DE-A 44 20 680; The production of high pressures was with such a device, however, because of the previously unsolved problem of oscillating burden- th bearing problematic.
  • Another preferred application is an eccentric drive and power transmission by means of roller and lever assembly on the connecting rods. Both variants are described below with reference to the drawings.
  • the invention is characterized in that it ensures a lubricant layer with a certain minimum thickness analogous to the hydrostatic bearing concept. It can be worked with low lubricant pressure in the order of a few bar and can be dispensed with a high-pressure lubricant supply. Finally, no throttle modules are needed to stabilize the lubrication gap thickness.
  • a further advantage of connecting rod-driven plunger pumps with a lubricating device according to the invention is that the frictional forces transmitted by the connecting rod bearing to the plunger are negligibly small in contrast to conventional bearings, since these, as already described, are in each operating state ensure hydrodynamic lubrication and thus produce only a negligible friction torque due to the extremely low sliding speeds of the connecting rod bearings.
  • the completely different friction conditions prevent a purely axially symmetrical force distribution from being achieved on the plunger foot. If the hydraulic displacement forces between the plunger and its guide arising from the transverse pendulum movements are greater than the lateral forces acting on the plunger, contact between the plunger and the guide can be avoided.
  • the parameters influencing this effect are frequency, delivery pressure range and viscosity of the pumped medium as well as the gap thickness.
  • the swashplate type of drive known per se can also be used for high-pressure pumps.
  • a preferred field of application is fuel injection pumps.
  • a swash plate assembly eliminates the otherwise required drive systems with cranks and crossheads. Such an arrangement is space-saving and can be due to the cy- cylindrical shape are placed directly on the end flange of a stationary drive motor.
  • Warehousing is simplified, as per engine type a single pump unit is needed, which can be easily adjusted by changing the swash plate angle of attack to each cylinder number.
  • Fig. 2 shows an example of a plunger pump with a swash plate and a connecting rod for power transmission in section
  • Fig. 3 is a detail view of a connecting rod with an inventive
  • Lubricating device for use in a plunger pump according to FIG. 2,
  • FIG. 4 shows the dependence of the thickness of the lubricating gap on the angle of rotation of the swash plate in a device according to FIG. 2
  • FIG. 5 shows the dependence of the transverse stability of the plunger on the angle of rotation of the swash plate in a device according to FIG. 2 compared to conventional bearing arrangements
  • FIGS. 7 and 8 show detailed views of a connecting rod with a plunger according to the invention
  • Fig. 1 shows an example of an inventive bearing assembly with a bearing 10 in the form of a ball with center M or spherical cap and an anvil 20 with complementary shape in section along a longitudinal axis A of the connecting rod.
  • the bearing assembly is substantially rotationally symmetrical to the axis A, so that a relative movement with two degrees of freedom is possible.
  • the bearing arrangement is designed around the point M in the manner of a ball joint with pivoting capability.
  • the representation can also be viewed as a section through cylindrical bearings or abutments, ie bearings and abutments can be arranged in the manner of a swivel joint with pivotability about an axis perpendicular to the plane through M (see Fig .. 7+ 8th).
  • both connecting rod heads and their abutments have the shape shown in FIG.
  • Bearings and thrust bearings 10, 20 can be inserted into each other substantially accurately, but with a certain play and can relative to each other perform a pendulum motion around the center M (one or two degrees of freedom).
  • the maximum deflection of the axis of symmetry A of the bearing 10 from its rest position by an angle ⁇ of about ⁇ 1 ° is shown in dashed lines and denoted by A '.
  • the direction of the action of force on the bearing for example given by the orientation of a plunger coupled to the connecting rod, is denoted by B and coincides in the rest position with the direction of the axis A.
  • a lubricant is introduced into the lubrication gap 30 formed between them due to the play via a lubricant supply 32.
  • the lubricant is pressed during operation of the discharge point 32 'of the lubricant supply 32 into the lubrication gap 30 and flows out of this peripherally in the flow direction S again.
  • the lubricating gap 30 has a variable thickness d due to the changing load.
  • the Münungsstelle 32 'in the lubricant pocket 34 is located in the region of the axis of symmetry A.
  • the area 32 ' is located in the area of the outlet Lubricant supply 32, a check valve 40.
  • the check valve 40 has a spherical valve body 42, which is biased by a second bearing element 20 anchored or supported spring 44 against a valve seat 46 acting as a conical region of the discharge point 32 '.
  • the valve seat 46 is shaped so that the above-mentioned oscillating movement of the bearing elements 10, 20 is possible. But it is also possible that the check valve 40 is anchored completely in the first bearing element 20 (see Fig. 3, lower bearing assembly).
  • the flow resistance of the lubricating gap 30 must not be too low, so that the thickness of the lubricant film is not too small.
  • a lubricant pocket 34 is formed in the bearing 10 by a recess in the region around the discharge point 32 ', which has a circumferential transition edge 36 at the transition to the actual lubrication gap 30.
  • the angle ⁇ has a value of 80-90 °.
  • a circumferential groove 38 This defines the outer edge of the lubricating gap 30 and the active, i. the exposed bearing surface.
  • the surfaces 12, 22 are not loaded beyond the groove or to a lesser extent.
  • the lubricant can i.a. drain through the groove 38.
  • FIG. 2 shows a swash plate drive plunger pump 100, in particular for a fuel pump.
  • the rotational movement of a shaft 114 is transmitted to the inclined disc 108 and thus sets the swash plate 109 in a corresponding up-and-down movement.
  • the swash plate 109 in turn imparted via the connecting rod 106 to the plunger 102, in the cylindrical Guide sleeve 104 is stored, the lifting movements.
  • the axis A of the connecting rod 106 is substantially coincident with the axis of the plunger 102 and thus the axis B of the force with the exception of small oscillating transverse movements of the connecting rod 106 to compensate for the different radial position in the upper and lower positions of the swash plate 109.
  • Fig. 3 shows a connecting rod 106 with two Pleuelköpfen 110, 121 and associated plunger and drive side thrust bearings 120, 111, which are constructed to smaller details as shown in Fig. 2. Differences are that the lubricant pockets 134, 135 and the circumferential grooves 138, 139 are arranged in one case on the Pleuelköpfen 110, 121 and in the other case in the abutments 120, 111, since both variants represent equivalent solutions.
  • the plunger-side connecting rod 110 is mounted to form a spherical surface lubricating gap 130 in a connected to the plunger 102 thrust bearing 120 with an inverse spherical surface (center M).
  • the basic structure corresponds to Fig. 1 with the difference that the lubricant bag 134 is not formed in the connecting rod 110, but in the counter-bearing 120 here. Their shape and function, however, is as described above with reference to FIG.
  • the lubricant supply 133 extends inside the connecting rod 106 along its axis A. In the mouth region, a check valve 140 is arranged.
  • the drive-side lower connecting rod 121 is also mounted in an adapted to its shape abutment 111, wherein also a spherical surface-shaped lubricating gap 131 (center M ') is formed.
  • a spherical surface-shaped lubricating gap 131 center M '
  • the main lubricant supply 132 which feeds through the lubricating gap 131 and extending through the connecting rod 106 lubricant supply 133. Return into the feed 132 is prevented by means of a further check valve 141.
  • FIG. 4 shows, by way of example, the gap thickness d as a function of the angle of rotation of the swashplate or of the shaft driving it in a connecting-rod bearing arrangement according to FIG. 2 or 3, ie as a function of the load of these bearings for an oil viscosity of SEA20.
  • the gap thickness d decreases from initially approximately 0.06 mm first very strongly, then more slowly sloping down to approximately 0.005 mm.
  • the lubricating gap thickness changes only imperceptibly, since the decompression of the lubricant continues up to 225 °. Thereafter, the gap thickness d abruptly increases again to about 0.06 mm and remains at this level during the rest of the weaker loaded movement phase (225-360 °).
  • the feed amount of the lubricant is preferably selected so that the distance between the surfaces
  • the bearing elements also corresponds to the actual thickness of the lubricant film, ie that no foreign substances such as air are trapped.
  • FIG. 5 shows the transverse stability of the plunger with a lubricating device according to the invention in comparison to a conventional bearing.
  • the torque relative to the center of the plunger (bold curve), which is due to the practically missing frictional forces caused exclusively by the Pleuelauslenkung changes sinusoidally and completely symmetrically with respect to the central axis of the plunger over the entire stroke range with the rotation angle of the drive shaft.
  • the plunger thus executes a gentle pendulum motion about its axis. This can therefore be stabilized by the pumping medium, which is present between the plunger and its guide, so that a metallic contact between the piston and guide surface is excluded.
  • a pressure of about 1000 bar are constructed.
  • a supply pressure of the lubricant in particular oil, is sufficient for example 10 bar.
  • a pump speed of 1500 rpm can be achieved, which should not be undercut, since otherwise the minimum required lubrication gap thickness would no longer be ensured.
  • the lateral relative movements of the centers of bearing and thrust bearing must be small; Preferably, the maximum displacement between the centers M, M 'of the Pleuelköpfe 110, 121 in the transverse direction only +/- 1, 5% to 2% of the stroke of the plunger.
  • the lubricating gap 130, 131 has a function of the viscous It has a minimum thickness of eg 0.01 mm (for oil according to SAE50) or 0.005 mm (for oil according to SAE20).
  • FIG. 6 shows a further plunger pump 200 in section, in which the lubricating device according to the invention leads to a significant improvement in operating safety.
  • It is an eccentric-type plunger pump in which the axes A, B and C are chosen with respect to their relevant distances so as to increase the stroke of the connecting rods 206 to the desired value.
  • the present concept is particularly suitable as a water pump.
  • the rotation of a drive shaft 214 is converted by means of an eccentric 208 in a synchronous pivotal movement of two levers 216. These are arranged on different sides of the eccentric 208 and braced against each other with a spring 218.
  • the levers 216 are respectively connected to the plungers 202, so that the pivoting movement of the levers 216 is converted into an axial movement of the plungers 202 in their cylindrical guides 204.
  • the pivot point D of the lever 216 must be positioned so that it has reached half the arc height of its pivoting profile when reaching half the target value of the Plungerhubs. Because of the reciprocal movement, there are also special requirements for the conrod bearings, which have led to the fact that eccentric drives with reciprocating connecting rods have not yet been used with plunger pumps. By using the lubricating device according to the invention, however, it is possible to improve the lubrication to such an extent that this technique can also be used for high-performance pumps.
  • the connecting rod 206 has two cylindrical connecting rod ends 210, 221 with an annular base. These act as a respective bearing and are mounted on a pin-like cylindrical counter bearing 220, 211 with a circular base. These are firmly connected to the lever 216 and the plunger 202. It will therefore be one cylinder jacket-shaped lubricating gap 230, 231 formed.
  • the Pleuelköpfe 210, 221 and their abutment 220, 211 are coupled in the manner of swivel joints.
  • lubricant is supplied to the lubricating gap 230 via a lubricant supply 232.
  • a check valve 240 is again arranged in the lubricant supply 232;
  • a lubricant bag 234 is present - here in the counter bearing 211, alternatively in the connecting rod 221. Construction and function correspond in principle Fig. 1.
  • the lubricant is passed through a further supply 233 to the plunger-side lubrication gap 231.
  • a check valve 241 is disposed in front of the junction and a lubricant pocket 235 available.
  • the entire suction stroke i. the schisse- rather loaded movement phase
  • the lubricant pressure required for this purpose is at the relevant time, i. the end of the suction stroke, determined because then the sum of all the bearing elements loading forces assumes the highest value.
  • the feed quantity of the lubricant is given by the gap losses occurring during this time as well as the gap filling volume.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Rolling Contact Bearings (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne un dispositif de lubrification des points d'appui d'une bielle (106, 206), comprenant un palier (10, 110, 210, 121, 221), réalisé sur chacune des têtes de la bielle (106, 206), et un contre-palier (20, 120, 220, 111, 211) coopérant avec ledit palier. Le palier (10, 110, 210, 121, 221) et le contre-palier correspondant (20, 120, 220, 111, 211) peuvent effectuer un mouvement oscillant l'un par rapport à l'autre et sont soumis à une forte et à une faible contrainte, en alternance, au cours d'un cycle de mouvement. Un espace de lubrification (30, 130, 131, 230, 231) d'épaisseur variable (d), dans lequel débouche une conduite d'alimentation en lubrifiant (32, 132, 133, 232, 233), est réalisé entre le palier (10, 110, 210, 121, 221) et le contre-palier correspondant (20, 120, 220, 111, 211). Un clapet antiretour (40, 140, 141, 240, 241) est placé dans la conduite d'alimentation en lubrifiant (32, 132, 133, 232, 233). De plus, un évidement à lubrifiant (34, 134, 135, 234, 235) est formé dans l'espace de lubrification (30, 130, 131, 230, 231). L'invention permet de produire un film lubrifiant, largement indépendant du mouvement, dans l'espace de lubrification et de diminuer ainsi le frottement à une valeur presque insignifiante dans des systèmes de paliers à mouvement oscillant et soumis à des contraintes oscillantes. L'application aux points d'appui de pompes à piston(s) plongeur(s) à entraînement par bielle est particulièrement avantageuse.
PCT/CH2008/000420 2007-10-11 2008-10-08 Dispositif de lubrification des points d'appui d'une bielle, son procédé de fonctionnement et pompe à piston(s) plongeur(s) munie d'un tel dispositif WO2009046558A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH15872007 2007-10-11
CH1587/07 2007-10-11

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WO2009046558A1 true WO2009046558A1 (fr) 2009-04-16

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3290753A1 (fr) 2016-09-01 2018-03-07 PSA Automobiles SA Ensemble piston bielle rotulee avec augmentation de vitesse d'un flux d huile interne
CN115370567A (zh) * 2022-09-23 2022-11-22 北京天玛智控科技股份有限公司 柱塞泵

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Publication number Priority date Publication date Assignee Title
NL273108A (fr) *
US878783A (en) * 1907-08-13 1908-02-11 Keystone Driller Co Engine.
US1931969A (en) * 1931-08-26 1933-10-24 Hans Thoma Hydraulic gear
FR883348A (fr) * 1942-06-17 1943-07-01 Schlafhorst & Co W Mécanisme de commande à disque oblique
CH304830A (de) * 1941-11-26 1955-01-31 Schlafhorst & Co W Schiefscheibentriebwerk.
EP0280622A1 (fr) * 1987-02-20 1988-08-31 Jean Frédéric Melchior Piston pour moteurs à combustion interne et machines analogues
EP0451011A1 (fr) * 1990-04-06 1991-10-09 Jean Frédéric Melchior Piston pour moteurs à combustion interne et machines analogues
WO1996010706A1 (fr) * 1994-10-04 1996-04-11 Melchior Jean F Dispositif de lubrification d'un assemblage entre deux pieces mecaniques mobiles l'une par rapport a l'autre, notamment articulation bielle-piston

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL273108A (fr) *
US878783A (en) * 1907-08-13 1908-02-11 Keystone Driller Co Engine.
US1931969A (en) * 1931-08-26 1933-10-24 Hans Thoma Hydraulic gear
CH304830A (de) * 1941-11-26 1955-01-31 Schlafhorst & Co W Schiefscheibentriebwerk.
FR883348A (fr) * 1942-06-17 1943-07-01 Schlafhorst & Co W Mécanisme de commande à disque oblique
EP0280622A1 (fr) * 1987-02-20 1988-08-31 Jean Frédéric Melchior Piston pour moteurs à combustion interne et machines analogues
EP0451011A1 (fr) * 1990-04-06 1991-10-09 Jean Frédéric Melchior Piston pour moteurs à combustion interne et machines analogues
WO1996010706A1 (fr) * 1994-10-04 1996-04-11 Melchior Jean F Dispositif de lubrification d'un assemblage entre deux pieces mecaniques mobiles l'une par rapport a l'autre, notamment articulation bielle-piston

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3290753A1 (fr) 2016-09-01 2018-03-07 PSA Automobiles SA Ensemble piston bielle rotulee avec augmentation de vitesse d'un flux d huile interne
CN115370567A (zh) * 2022-09-23 2022-11-22 北京天玛智控科技股份有限公司 柱塞泵

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