WO2013053900A1 - Systeme de guidage d'un arbre vertical de machine tournante et installation de conversion d'energie incorporant un tel systeme - Google Patents
Systeme de guidage d'un arbre vertical de machine tournante et installation de conversion d'energie incorporant un tel systeme Download PDFInfo
- Publication number
- WO2013053900A1 WO2013053900A1 PCT/EP2012/070287 EP2012070287W WO2013053900A1 WO 2013053900 A1 WO2013053900 A1 WO 2013053900A1 EP 2012070287 W EP2012070287 W EP 2012070287W WO 2013053900 A1 WO2013053900 A1 WO 2013053900A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- shim
- housing
- pad
- axis
- shaft
- Prior art date
Links
Classifications
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- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/02—Sliding-contact bearings
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- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
- F16C17/03—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings
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- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
- F16C17/03—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings
- F16C17/035—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings the segments being integrally formed with, or rigidly fixed to, a support-element
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- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/02—Sliding-contact bearings
- F16C23/04—Sliding-contact bearings self-adjusting
- F16C23/041—Sliding-contact bearings self-adjusting with edge relief
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- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/02—Sliding-contact bearings
- F16C23/04—Sliding-contact bearings self-adjusting
- F16C23/043—Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings
- F16C23/045—Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings for radial load mainly, e.g. radial spherical plain bearings
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- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/08—Attachment of brasses, bushes or linings to the bearing housing
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- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/1075—Wedges, e.g. ramps or lobes, for generating pressure
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- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/108—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid with a plurality of elements forming the bearing surfaces, e.g. bearing pads
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- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/02—Rigid support of bearing units; Housings, e.g. caps, covers in the case of sliding-contact bearings
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- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
Definitions
- the invention relates to an adjustable system for guiding a shaft, rotating about a vertical axis.
- the invention may, in particular, be implemented with a hydraulic machine which may comprise a turbine, a pump or a pump turbine used in a hydraulic energy conversion installation into electrical energy, or vice versa.
- the invention intends to remedy more particularly by proposing an adjustable system for guiding a machine shaft which makes it possible to obtain improved rigidity of the support of its skids and to limit, consequently, the deformed shapes. of the tree in use.
- the invention also aims at reducing the transverse dimensions of the labyrinth wheel seals used in a hydraulic installation incorporating this guidance system.
- the invention also aims to reduce the cost and simplify the adjustment of the play of the roller bearing with the consequence of assembly and maintenance time reducing downtime of the machine.
- the invention relates to an adjustable system for guiding a shaft, in rotation about a vertical axis, this system comprising pads each provided with a surface intended to form a bearing with the shaft and, for each shoe, a wedge provided with a cam surface whose trace, in a radial plane relative to the vertical axis of rotation, is inclined relative to this axis.
- each pad is in direct support, by a portion of its outer radial face, against the cam surface of the wedge, while each cam is provided with an elongated housing whose largest dimension is parallel to the vertical axis of rotation and in which is housed a prison nut guided in translation by the longitudinal edges of the housing and whose position in the housing is controlled by means of a threaded rod engaged with an internal thread of the nut prisoner.
- axial or radial are defined with reference to the vertical axis of rotation of the shaft for which the guide system is envisaged.
- a direction is said to be axial if it is parallel to this axis, a surface is said to be axial if it is perpendicular to this axis.
- a direction is called radial if it is perpendicular to, and secant with, this axis.
- a surface is said to be radial if it is centered on this axis.
- a plane is said to be radial if it includes a radial direction and the axis of rotation.
- the position of each pad, in a radial direction is defined by the direct cooperation between this pad and the cam surface of the hold, without the need to use a joint with a ball joint and a force recovery block as in the equipment of the prior art.
- the invention thus takes the opposite of the technique used in systems comprising a ball with an outer surface in a sphere section, insofar as, in these known systems, a sliding contact between the ball and the force recovery block is favored. .
- the direct support provided in the invention between the portion of the outer radial face of the shoe and the cam surface of the wedge induces a possible matting of the surfaces in abutment against each other, which is accommodates during the life of the hydraulic machine equipped with the adjustable guide system of the invention.
- the guidance of the pads with the nut trapped in the oblong housing is accurate, while the adjustment elements of the position of the pads undergo acceptable mechanical stresses.
- such a guidance system may incorporate one or more of the following features, taken in any technically permissible combination:
- each wedge makes it possible to adjust the radial position of the pad bearing against this surface, by a vertical translation of the cam.
- the aforementioned housing is preferably a light which passes through the shim of its cam surface to an opposite surface by which the shim is in abutment against the fixed member.
- Each pad is in direct support against the cam surface of the corresponding shim, on either side of the housing of this wedge, in a horizontal direction.
- Each pad is provided on its outer radial face, a heel which defines a direct bearing surface located against the cam surface of the corresponding shim.
- the bearing surface of the heel is polygonal contour, including square. As a variant, this bearing surface is circular in outline.
- the heel is provided with a housing for receiving a portion of the prisoner nut.
- the parts in direct support of a pad and the corresponding wedge are provided to be matted one by the other during use of the guidance system.
- the system comprises a fixed force recovery ring, an inner radial surface facing the vertical axis of rotation is cut grooves in each of which is engaged a shim, with the possibility of vertical sliding.
- the captive nut comprises a head which protrudes from the cam surface of the wedge and which is engaged in a housing of the pad bearing against this surface.
- the housing is drilled in the heel of the pad and the localized direct bearing surface surrounds the outlet of the housing.
- the wedge is pierced with two orifices aligned along the largest dimension of the elongated housing, while the threaded rod is successively engaged in a first hole among these two orifices, in an internal thread of the captive nut and in the second orifice.
- the invention also relates to a plant for converting hydraulic energy into electrical energy, or vice versa, which comprises a turbine wheel, pump or pump impeller integral, in rotation about a vertical axis, a shaft guided by skates.
- this installation comprises a system for guiding a tree as mentioned above.
- FIG. 1 is a diagrammatic representation, in axial section, of an installation according to the invention
- FIG. 2 is a perspective view, partially broken away, corresponding to detail II in FIG. 1;
- FIG. 3 is an enlarged view of detail III in FIG. 2,
- FIG. 4 is an exploded perspective view of certain elements of a skid guide system according to the invention.
- FIG. 5 is a basic section along line V-V in FIG. 2, in a radial plane with respect to the axis of rotation of the wheel of the installation,
- FIG. 6 is a section along line VI-VI in FIG. 5;
- FIG. 7 is a section along the line VII-VII in FIG. 5, and
- FIG. 8 is a section along line VIII-VII I in Figure 5.
- the installation 200 shown in the figures comprises a Francis-type turbine 1 whose wheel 2 is intended to be rotated around a vertical axis X2 by a forced flow of water E coming from a water reservoir. not shown.
- a shaft 3 is integral, in rotation about the axis X2, with the wheel 2.
- This shaft 3 is coupled to an alternator 4 which delivers an alternating current to a not shown network, as a function of the rotation of the wheel 2.
- the installation 200 thus makes it possible to convert the hydraulic energy of the flow E into electrical energy.
- the plant 200 may comprise one or more turbines 1 fed from the same water reservoir.
- the turbine Francis 1 can be replaced by a pump turbine which, when it operates as a pump, is driven by an electric motor installed in place of the alternator 4 and converts the electrical energy into hydraulic energy of a flow set in motion by the pump wheel.
- a supply line 5 makes it possible to bring the flow E to the wheel 2 and extends between the water reservoir and a tank 6 equipped with guides 61 which regulate the flow E.
- a duct 8 is provided downstream of the turbine 1 to evacuate the flow E and return it to the bed of a river or river from which the water reservoir is fed.
- This duct 8 is sometimes called suction duct.
- the conduit 8 comprises an upstream portion 81 substantially vertical, frustoconical and centered on the axis X2, and a downstream portion 82 centered on a substantially horizontal axis X82.
- a bend 83 at 90 ° connects the parts 81 and 82 of the condu 8.
- the shaft 3 is held in position relative to a masonry structure not shown by two oil bearings 100 and 101 formed respectively in the upper part and in the lower part of the shaft 3, around it.
- three oil bearings may be used to guide the shaft 3.
- a skid-mounted hydraulic bearing can be implemented, with a guiding system according to the invention, at the level of the alternator 4.
- the fixed structure of the installation 200 comprises a ring 102 of force recovery disposed around the shaft 3 and which is secured to the masonry of the installation 200 which is not shown.
- This force recovery ring 102 is metallic and is welded to a ferrule 103A itself welded to a strip 103B bolted to a not shown flange and itself fixed on the masonry by other parts not shown.
- the outer radial surface 32 of the shaft 3 is stepped and comprises, in the vicinity of the ring 102, a circumferential band 34 around which several pads 104 are arranged, the number of which varies according to the size of the shaft 3. In the example of the figures, the skates are ten in number.
- Each pad 104 comprises an inner radial surface 1042 which faces the axis X2 in the mounted configuration of the installation 200 and which is in a cylinder section centered on this axis X2, with a radius substantially equal to, or slightly greater than, that of the band 34. It is thus possible to define, between each shoe 104 and the surface 34 a portion of the hydraulic bearing 100 in which a film of oil provides lubrication and recovery of the shoe force.
- Y104 denotes a radial axis with respect to the axis X2 and which passes through the center of the surface 1042 of a shoe 104.
- a shoe 104 extends between its surface 1042 and a radial surface external plane 1044 which is turned away from the axis X2.
- the surface 1044 of a shoe 104 is equipped with a heel 1046 which is integral with the rest of the shoe 1044 and which projects from the surface 1044.
- heel 1046 is square. Alternatively, it may be circular or rectangular, or polygonal with another form.
- the heel 1046 is pierced with a housing 1048 which is blind, circular section and centered on the axis Y104.
- the surface 1047 surrounds the outlet of the housing 1048.
- a shim 106 is associated with each pad 104.
- Each shim 106 is of generally parallelepipedal shape with an inner radial surface 1062 intended to be turned towards the axis X2 in the mounted configuration of the installation 200, and an outer radial surface 1064, oriented opposite the surface 1062 and which bears against the surface 1022 of the force recovery ring 102, in the mounted configuration of the installation 200.
- the surfaces 1062 and 1064 are flat but not parallel. Indeed, these surfaces form between them an angle whose value is less than 5 °.
- the surfaces 1062 and 1064 move toward each other in a downward direction when the shim 106 is in place in the installation 200. More precisely, in the plane of FIG. 5 which is radial with respect to the X2 axis, the trace of the surface 1062 is inclined, with respect to this axis, the angle a.
- the surface 1062 converges towards the X2 axis towards the top of FIG. 5, while the surface 1064 is parallel to the X106 axis.
- the surface 1062 of the shim 106 forms a cam surface which allows to adjust the radial position of the pad 104 bearing against this surface by a vertical translation of the shim 106.
- the shim 106 may be described as "wedge".
- the surface 1022 is cut with ten flat-bottomed grooves 1024, in each of which a shim 106 is engaged, with the possibility of vertical sliding.
- the shim 106 is pierced with an oblong opening 1066 along the generally rectangular axis X106 and whose largest dimension is centered on an axis X106 parallel to the axis X2 in mounted configuration and perpendicular to the axis Y104 .
- 1066A and 1066B respectively denote the large edges of the opening 1066 which are parallel to the axis X106.
- the opening 1066 is formed by a lumen which passes through the shim 106 of the surface 1062 to the surface 1064. Alternatively, the lumen 1066 may be replaced by a hollow housing opening on the surface 1062 but not on the surface 1064.
- the length of the light 1066 along the axis X106 is adapted to allow the assembly of the assembly 150 and the adjustment of the bearing clearance
- the shim 106 is pierced with two orifices 1067 and 1068 aligned on the axis X106.
- a nut 107 is mounted prisoner in the oblong opening 1066 of each shim 106 and comprises two flats 1072 and 1074 slidingly bearing on the sides 1066A and 1066B of this opening.
- the nut 107 is also provided with an internal thread 1076 intended to cooperate with the threaded portion 1086 of a screw 108 whose head 1082 abuts against a lower surface of the shim 106 in which the orifice 1068 opens.
- 1084 end of the screw 108 opposite the head 1082 is square section, which allows to drive it in rotation about the axis X106 when the screw 108 is in place in the orifices 1067 and 1068.
- the captive nut 107 comprises a head 1078 protruding from the surface 1062 of the shim 106 and which is engaged in the housing 1048 of the associated shoe 104.
- the introduction of the head 1078 in the housing 1048 ensures that the nut 107 does not slide vertically relative to the pad 104 when the shim 106 slides around the nut 107 parallel to the axis X106.
- the screw 108 is rotated about its axis X108, then coincides with the axis X106, the shim 106 slides, upwards or downwards, along the surfaces 1047 and 1022 against which it is supported sliding, respectively by its surfaces 1062 and 1064.
- the pad 104 is in direct abutment against the surface 1062, at its surface 1047 which protrudes from to the rest of the surface 1044. More specifically, the surface 1047 is in localized support against the surface 1062, on either side of the opening 1066 in a horizontal direction D106 defined in the shim 106 as perpendicular to the axis X106 and parallel to surfaces 1062 and 1064.
- each pad 104 is in direct abutment on the surface 1062 of the associated shim 106, which is supported by its surface 1064 against the stress-absorbing ring 102, the radial position of each pad 104, that is to say to say its position along its axis Y104, is precisely controlled by the vertical translation of the corresponding shim 106, without manufacturing tolerances of the elements 104, 106 and 102 inducing significant positional variations.
- the inclined nature of the surface 1062 makes it possible to adjust the radial position of the pad 104 by a vertical translation of the shim 106.
- the direct support of the surfaces 1062 and 1047 against each other ensures a transmission of effort without play and by flat surfaces. This is a substantial advance over known devices in which ball joints and force-absorbing blocks were interposed between the pads and a part comparable to the ring 102 of the invention.
- the mounting of the head 1078 in the housing 1048 is performed with a slight clearance, so that the possible sliding of the shoe 104 around the head 1078, parallel to the axis Y104, does not risk be limited to interfere with the support of the surface 1047 on the surface 1062.
- the material of the elements 104, 106 and 107 may be chosen to support, or even facilitate, such matting. These parts may, for example, be made of carbon steel, especially in the European grade S275, S355 or equivalent.
- the constituent material of the shim 106 is chosen so that its surface 1062 is matted under the effect of contact with the heel 1046 of the associated shoe before the surface 1047 of this heel is itself matted. The material of the shim 106 is thus more flexible than the material of the pad 104. In fact, in case of important matting following abnormal stresses or vibrations, it is easier and less expensive to change a shim 106 than a pad 104.
- the gray portion of the surface 1062 represents a portion 1062A of this matted surface under the effect of the pressure exerted by the surface 1047 of the heel 1046.
- the surface 1047 can also be matted. This is not required, however.
- the transmission of radial forces between the parts 104 and 106 is achieved by means of the surfaces 1047 and 1062 which are flat, which is substantially easier to implement than in the case where surfaces in section spheres must be made, with large radii, as in the joints of the prior art.
- D108 denotes a line orthoradial with respect to the axis X2 and passing through the axis X106 of the shim 106 associated with each pad 104.
- the tangential force exerted between the shaft 3 and the pad 104 tends to move the nut 107 and the shim 106 along the line 108, downwards in FIG. 6.
- this tangential force is transmitted thanks to the contact pressure between the surfaces 1047 and 1062, in support of the head 1078 in the housing 1048 and bearing the flat 1072 against the side 1066A of the opening 1066.
- This tangential force is taken up by the side of the groove 1024 against the bottom of which rests the surface 1064 of the hold 6.
- the invention is shown in the figures in the case where the surface 1047 has a square contour.
- a circular contour can be envisaged as mentioned above.
- the geometry of the portion 1062A of the surface 1062 changes accordingly.
- the geometry of the heel 1046 and surfaces 1062 and 1064 is adapted according to the intensity of the forces to be transmitted.
- the geometry of the head 1078 and the housing 1048 can be changed. They may, alternatively, be square or rectangular section.
- the invention also has an advantage in terms of safety. Indeed, even if, under the effect of vibrations, the counter-nut 109 is loosened, to the point that the screw 108 is driven out of the orifices 1067 and 1068, the shim 106 is not likely to slide completely downwards or upwards because the prisoner nut 107 forms a stop to the vertical movement of the shim 106. The pad 104 can not therefore become completely free and disengaged from the support 102, causing serious damage if that were the case.
- the invention makes it possible to envisage a standardization of the elements 104 to 110 constituting the system 150 for guiding the shaft 3, which can be designed according to the intensity of the forces to be transmitted.
- the constituent parts of the system 150 are easily accessible for inspection, including after complete assembly, which facilitates the monitoring and maintenance operations.
- the invention can be implemented at the lower bearing 100, the upper bearing 101 or an intermediate bearing of the installation 200.
- the invention is described above when it is implemented in a hydraulic installation. However, it can be used in any rotating machine with vertical axis, provided with at least one roller bearing. It can, for example, be an alternator or a motor.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Sliding-Contact Bearings (AREA)
- Automatic Cycles, And Cycles In General (AREA)
- Braking Arrangements (AREA)
- Mounting Of Bearings Or Others (AREA)
Abstract
Description
Claims
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
RU2014118940/11A RU2014118940A (ru) | 2011-10-13 | 2012-10-12 | Система для направления вертикального вала вращающейся машины и установка для преобразования энергии, содержащая такую систему |
EP12770161.3A EP2766618A1 (fr) | 2011-10-13 | 2012-10-12 | Systeme de guidage d'un arbre vertical de machine tournante et installation de conversion d'energie incorporant un tel systeme |
CA2851578A CA2851578A1 (fr) | 2011-10-13 | 2012-10-12 | Systeme de guidage d'un arbre vertical de machine tournante et installation de conversion d'energie incorporant un tel systeme |
BR112014008992A BR112014008992A8 (pt) | 2011-10-13 | 2012-10-12 | sistema de orientação de uma árvore vertical de máquina giratória e instalação de conversão de energia, incorporando esse sistema |
CN201280061691.5A CN104040196A (zh) | 2011-10-13 | 2012-10-12 | 用于引导旋转机器的竖向轴的系统和包括此类系统的功率转换装备 |
US14/250,855 US20140219592A1 (en) | 2011-10-13 | 2014-04-11 | System for guiding a vertical shaft of a rotary machine, and power-conversion equipment including such a system |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1159274A FR2981417B1 (fr) | 2011-10-13 | 2011-10-13 | Systeme de guidage d'un arbre vertical de machine tournante et installation de conversion d'energie incorporant un tel systeme |
FR1159274 | 2011-10-13 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/250,855 Continuation US20140219592A1 (en) | 2011-10-13 | 2014-04-11 | System for guiding a vertical shaft of a rotary machine, and power-conversion equipment including such a system |
Publications (1)
Publication Number | Publication Date |
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WO2013053900A1 true WO2013053900A1 (fr) | 2013-04-18 |
Family
ID=47008634
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2012/070287 WO2013053900A1 (fr) | 2011-10-13 | 2012-10-12 | Systeme de guidage d'un arbre vertical de machine tournante et installation de conversion d'energie incorporant un tel systeme |
Country Status (8)
Country | Link |
---|---|
US (1) | US20140219592A1 (fr) |
EP (1) | EP2766618A1 (fr) |
CN (1) | CN104040196A (fr) |
BR (1) | BR112014008992A8 (fr) |
CA (1) | CA2851578A1 (fr) |
FR (1) | FR2981417B1 (fr) |
RU (1) | RU2014118940A (fr) |
WO (1) | WO2013053900A1 (fr) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ITFI20130234A1 (it) * | 2013-10-10 | 2015-04-11 | Nuovo Pignone Srl | "hydraulic power recovery turbine with integrated bearing-clutch housing" |
US9587672B1 (en) * | 2015-08-11 | 2017-03-07 | Lufkin Industries, Llc | Adjustable offset pivot journal pad |
DE102016211236A1 (de) * | 2016-06-23 | 2017-12-28 | Robert Bosch Gmbh | Kippsegmentlager |
CN106149892B (zh) * | 2016-08-17 | 2019-03-22 | 福建龙溪轴承(集团)股份有限公司 | 一种单向滑移的关节轴承节点 |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1880353A (en) | 1929-09-09 | 1932-10-04 | Anthony G M Michell | Journal bearing |
FR1388194A (fr) * | 1964-02-07 | 1965-02-05 | Schmidt Gmbh Karl | Palier à glissement ou coussinet à coquilles multiples |
US4032199A (en) * | 1974-09-25 | 1977-06-28 | Allis-Chalmers Corporation | Apparatus for equalizing radial load on plurality of pivoted bearing pads |
US5772334A (en) * | 1994-04-27 | 1998-06-30 | British Technology Group Limited | Fluid film bearings |
US5885007A (en) * | 1997-06-30 | 1999-03-23 | The United States Of America As Represented By The Secretary Of The Navy | Adjustable bearing system with selectively optimized installational clearances |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US130373A (en) * | 1872-08-13 | Improvement in bushes for mill-spindles | ||
US780781A (en) * | 1904-12-16 | 1905-01-24 | Henry H Curtis | Spoon. |
US1161721A (en) * | 1913-06-02 | 1915-11-23 | Charles Algernon Parsons | Journal-bearing. |
JPS5544134A (en) * | 1978-09-22 | 1980-03-28 | Hitachi Ltd | Guide bearing |
CN100591932C (zh) * | 2008-11-14 | 2010-02-24 | 南京高精齿轮集团有限公司 | 推力轴承 |
-
2011
- 2011-10-13 FR FR1159274A patent/FR2981417B1/fr not_active Expired - Fee Related
-
2012
- 2012-10-12 WO PCT/EP2012/070287 patent/WO2013053900A1/fr active Application Filing
- 2012-10-12 CN CN201280061691.5A patent/CN104040196A/zh active Pending
- 2012-10-12 CA CA2851578A patent/CA2851578A1/fr not_active Abandoned
- 2012-10-12 EP EP12770161.3A patent/EP2766618A1/fr not_active Withdrawn
- 2012-10-12 RU RU2014118940/11A patent/RU2014118940A/ru not_active Application Discontinuation
- 2012-10-12 BR BR112014008992A patent/BR112014008992A8/pt not_active IP Right Cessation
-
2014
- 2014-04-11 US US14/250,855 patent/US20140219592A1/en not_active Abandoned
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1880353A (en) | 1929-09-09 | 1932-10-04 | Anthony G M Michell | Journal bearing |
FR1388194A (fr) * | 1964-02-07 | 1965-02-05 | Schmidt Gmbh Karl | Palier à glissement ou coussinet à coquilles multiples |
US4032199A (en) * | 1974-09-25 | 1977-06-28 | Allis-Chalmers Corporation | Apparatus for equalizing radial load on plurality of pivoted bearing pads |
US5772334A (en) * | 1994-04-27 | 1998-06-30 | British Technology Group Limited | Fluid film bearings |
US5885007A (en) * | 1997-06-30 | 1999-03-23 | The United States Of America As Represented By The Secretary Of The Navy | Adjustable bearing system with selectively optimized installational clearances |
Also Published As
Publication number | Publication date |
---|---|
FR2981417A1 (fr) | 2013-04-19 |
EP2766618A1 (fr) | 2014-08-20 |
CA2851578A1 (fr) | 2013-04-18 |
BR112014008992A8 (pt) | 2017-06-20 |
CN104040196A (zh) | 2014-09-10 |
US20140219592A1 (en) | 2014-08-07 |
FR2981417B1 (fr) | 2014-08-08 |
RU2014118940A (ru) | 2015-11-20 |
BR112014008992A2 (pt) | 2017-06-13 |
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