US20140075916A1 - Method and device for supplying a lubricant - Google Patents

Method and device for supplying a lubricant Download PDF

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Publication number
US20140075916A1
US20140075916A1 US13/980,696 US201213980696A US2014075916A1 US 20140075916 A1 US20140075916 A1 US 20140075916A1 US 201213980696 A US201213980696 A US 201213980696A US 2014075916 A1 US2014075916 A1 US 2014075916A1
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Prior art keywords
lubricant
bearings
circuit
temperature
flow
Prior art date
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Abandoned
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US13/980,696
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English (en)
Inventor
Philippe Alain François Augros
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.)
Safran Helicopter Engines SAS
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Turbomeca SA
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
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Assigned to TURBOMECA reassignment TURBOMECA ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AUGROS, PHILIPPE ALAIN FRANCOIS
Publication of US20140075916A1 publication Critical patent/US20140075916A1/en
Assigned to SAFRAN HELICOPTER ENGINES reassignment SAFRAN HELICOPTER ENGINES CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: TURBOMECA
Abandoned 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
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M5/00—Heating, cooling, or controlling temperature of lubricant; Lubrication means facilitating engine starting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/06—Arrangements of bearings; Lubricating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/08—Cooling; Heating; Heat-insulation
    • F01D25/10—Heating, e.g. warming-up before starting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/08—Cooling; Heating; Heat-insulation
    • F01D25/12—Cooling
    • F01D25/125—Cooling of bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/18—Lubricating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/18—Lubricating arrangements
    • F01D25/20—Lubricating arrangements using lubrication pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M5/00—Heating, cooling, or controlling temperature of lubricant; Lubrication means facilitating engine starting
    • F01M5/001—Heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M5/00—Heating, cooling, or controlling temperature of lubricant; Lubrication means facilitating engine starting
    • F01M5/002—Cooling
    • 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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/30—Application in turbines
    • F05D2220/32—Application in turbines in gas turbines
    • F05D2220/329—Application in turbines in gas turbines in helicopters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/98—Lubrication

Definitions

  • the present specification relates to the field of methods, systems, and devices for feeding lubricant, in particular to turbomachines.
  • turbomachines In many turbomachines, and in particular turboshaft engines, turbojets, turboprops, turbopumps, or turbocompressors, it is possible to distinguish between two zones at temperatures that are clearly different. Thus, in turboshaft engines, turbojets, and turboprops for aviation purposes, it is normally possible to distinguish between a relatively cool zone having a compressor and a relatively hot zone having the combustion chamber and the turbine.
  • Such turbomachines also normally include bearings, both in the low temperature zone and in the high temperature zone for the purpose of supporting rotary parts, and in particular the drive shaft.
  • a first set of bearings operates at a relatively low temperature while a second set of bearings operates at a relatively high temperature.
  • the term “set of bearings” does not necessarily have a plurality of bearings, but could optionally equally well comprise a set with only one unit.
  • a common feed circuit is used for feeding lubricant to both the first and the second sets of bearings.
  • the feed circuit normally includes a heat exchanger, and the lubricant is fed to the bearings after being cooled in the heat exchanger, which may for example be an air/lubricant heat exchanger or a fuel/lubricant heat exchanger, thus dumping heat from the lubricant respectively to ambient air or to a fuel circuit.
  • Such a heat exchanger is a part that is comparatively complex, heavy, and bulky. Unfortunately, in particular in aviation applications, it is desirable to minimize those drawbacks, and in particular to minimize weight.
  • the invention seeks to provide a method of feeding a turbomachine with lubricant that makes it possible to reduce the cooling requirements of the lubricant, and also the weight, the volume, and the complexity of the heat exchanger(s) associated therewith.
  • this object is achieved by the fact that, in a turbomachine having a first set of bearings and a second set of bearings operating at a temperature substantially higher than the first set, the second set of bearings is fed with lubricant at a temperature that is substantially higher than the first set.
  • a flow of lubricant is cooled in a heat exchanger upstream from the first set of bearings.
  • at least some of the heat absorbed by the lubricant can be removed in order to stabilize its temperature without necessarily cooling the flow of lubricant to the second set of bearings.
  • a lubricant flow is heated upstream from the second set of bearings, this heating being obtained by exchanging heat with a flow of lubricant returning from the second set of bearings. It is thus possible to increase the temperature of the lubricant delivered to the second set of bearings, while cooling the lubricant recovered from the second set of bearings, thereby contributing to reducing the overall transfer of heat from the second set of bearings to the lubricant.
  • the first set of bearings is fed with lubricant by a first circuit
  • the second set of bearings is fed with lubricant by a second circuit branching from the first circuit, thus making it possible to treat the lubricant for each of the sets of bearings in different manners, and in particular specifically to cool the lubricant delivered to the first set by the first circuit, and/or specifically to heat the lubricant delivered to the second set, e.g. by exchanging heat with a flow of lubricant returning from the second set.
  • the present specification also relates to a device for feeding a turbomachine with lubricant, said turbomachine having a first set of bearings and a second set of bearings, and said second set being suitable for operating at a temperature that is substantially higher than said first set.
  • the device is configured to feed the second set with lubricant at a temperature that is substantially higher than the first set.
  • the transfer of heat between the hotter second set of bearings and the lubricant can be decreased, thereby reducing the overall needs for cooling the lubricant.
  • the device has a first circuit for feeding lubricant to the first set of bearings, and a second circuit for feeding lubricant to the second set of bearings, the first circuit having a branch point leading to the second circuit. It is thus possible at this branch point to separate two distinct flows of lubricant, a first flow being delivered to the first set of bearings by the first circuit and a hotter second flow being delivered to the second set by the second circuit.
  • the first circuit may include a heat exchanger between said branch point and the first set of bearings in order to cool the lubricant for feeding the first set of bearings so as to cool the lubricant for feeding to the first set of bearings separately without affecting the temperature of the lubricant for feeding to the hotter second set of bearings.
  • the second circuit may also include a heat exchanger for transferring heat from a flow of lubricant returning from the second set of bearings to a flow of lubricant for feeding to the second set of bearings, thereby increasing the temperature of the lubricant delivered to the second set of bearings while reducing the temperature of the lubricant returned from the second set of bearings.
  • the second circuit could be entirely separate from the first circuit and not branched therefrom.
  • the heat exchangers of the first and second circuits could also be incorporated in the device independently from each other. It is even possible to envisage incorporating a heat exchanger for cooling the lubricant upstream from the branch point between the first and second circuits so as to cool at least a portion of the flow of lubricant for the second set of bearings.
  • the present specification also relates to a turbomachine having a first set of bearings, a second set of bearings suitable for operating at a temperature that is substantially higher than the first set, and a device configured to feed the second set with lubricant at a temperature that is substantially higher than the first set, and also a turbine engine assembly including such an engine, in particular for aviation purposes.
  • turbine engine assembly is used not only for a turboshaft engine, but for a turboprop or a turbojet, with or without a bypass.
  • FIG. 1 is a longitudinal section of a turbomachine
  • FIG. 2 is a diagram of a prior art lubricant feed device
  • FIGS. 3A , 3 B, 3 C, and 3 D are diagrams showing lubricant feed devices respectively constituting first, second, third, and fourth embodiments.
  • FIG. 4 is a diagram of a regenerative heat exchanger.
  • a turbomachine 1 more specifically forming part of a turboshaft engine assembly of a rotary wing aircraft is shown by way of illustration in FIG. 1 .
  • the turbomachine 1 comprises a low temperature section L including the compressor 2 , and a high temperature section H including the combustion chamber 3 and the turbine 4 .
  • the turbine 4 and the compressor 2 are connected together by the drive shaft 5 , which is supported by a plurality of bearings comprising a first set of bearings 6 L in the low temperature section L and a second set of bearings 6 H in the high temperature section H. Given their position, the bearings 6 H in the high temperature section H are at a temperature that is significantly higher than the temperature of the bearings 6 L in the low temperature section L.
  • Such an engine normally also includes a device for feeding the bearings with lubricant.
  • a device for feeding the bearings with lubricant is shown in FIG. 2 .
  • That lubricant feed device 110 comprises a tank 111 and a common lubricant circuit 112 for feeding the bearings 6 L of the low temperature section and the bearings 6 H of the high temperature section H, together with a circuit 113 for returning lubricant from the bearings 6 L and 6 H to the tank 111 .
  • Both the lubricant feed circuit 112 and the lubricant return circuit 113 may include conventional control and/or monitoring means (not shown) for circulating the lubricant and monitoring the pressure, the temperature, the presence of particles, etc.
  • the feed circuit 112 has a heat exchanger 114 for cooling the lubricant and removing the heat absorbed in the bearings 6 L and 6 H.
  • the heat exchanger 114 may be a lubricant/air heat exchanger for dumping the heat of the lubricant to ambient air, a lubricant/fuel heat exchanger for dumping the heat from the lubricant to a fuel circuit of the engine, or a combination of both.
  • the lubricant is thus delivered to the bearings 6 L and 6 H at substantially the same temperature. Nevertheless, since the bearings 6 H in the high temperature section H are at a temperature that is significantly higher than the bearings 6 L in the low temperature section L, the lubricant will be heated more intensely in the bearings 6 H than in the bearings 6 L.
  • the flow D L receives heat power P L from the bearings 6 L, e.g. of 1.7 kilowatts (kW), thereby heating up to a temperature T o,L equal to 121° C., for example, whereas the flow D H receives heat power P H from the bearings 6 H, e.g.
  • the heat exchanger 114 In order to cool the overall flow D g down to the initial temperature T i , the heat exchanger 114 must therefore remove a heat power P T that is approximately equivalent to summing the heat powers P L and P H , i.e. 6.6 kW for the values given above by way of example. In order to remove the heat flux that is transferred to the lubricant in particular by the bearings 6 H, and thus avoid overheating and potential coking and/or accelerated aging of the oil, the heat exchanger 114 needs to be of dimensions that are considerable.
  • FIG. 3A shows a first embodiment of a lubricant feed device 10 enabling lubricant cooling requirements to be reduced compared with the prior art.
  • This lubricant feed device 10 has a tank 11 , a first feed circuit 12 L for feeding lubricant to the set of bearings 6 L in the low temperature section L, a second feed circuit 12 H for feeding lubricant to the set of bearings 6 H in the high temperature section H, a first return circuit 13 L for returning lubricant from the set of bearings 6 L to the tank 11 , and a second return circuit 13 H for returning lubricant from the set of bearings 6 H to the tank 11 .
  • the second feed circuit 12 H branches from the first feed circuit 12 L at a branch point 20 .
  • each circuit 12 H, 12 L, 13 H, and 13 L may be fitted with conventional means (not shown) for driving and controlling lubricant circulation via the circuits 12 H, 12 L, 13 H, and 13 L, such as pumps, valves, check valves, and/or filters.
  • the first feed circuit 12 L includes a heat exchanger 14 upstream from the branch point 20 for the purpose of cooling the lubricant that is to be delivered to both sets of bearings 6 H and 6 L.
  • this heat exchanger 14 may be a lubricant/air heat exchanger in order to dump heat from the lubricant to ambient air, a lubricant/fuel heat exchanger in order to dump heat from the lubricant to a fuel circuit of the engine, or a combination of both.
  • Another the exchanger 30 is interposed between the feed circuit 12 H and the return circuit 13 H in order to heat the lubricant that is to feed the bearings 6 H, using heat taken from the lubricant returning from the bearings 6 H.
  • Such a regenerative heat exchanger 30 may be made in particularly simple manner by coaxial ducts 31 and 32 serving respectively in the go and the return directions of the lubricant, as shown in FIG. 4 .
  • the bearings 6 H of the high temperature section H of the engine 1 and the bearings 6 L of the low temperature section L can be fed with lubricant at temperatures that are substantially different. More specifically, the lubricant delivered by the circuit 12 H to the bearings 6 H is substantially hotter than the lubricant delivered by the circuit 12 L to the bearings 6 L. Consequently, the temperature difference between the bearings 6 H and the lubricant that is delivered thereto in operation by the circuit 12 H is less than in the prior art device 110 , thereby reducing the transfer of heat from the bearings 6 H to the lubricant, and thus reducing the overall requirements for cooling the lubricant.
  • the heat exchanger 14 may thus be dimensioned to be smaller than the heat exchanger 114 of the prior art device 110 .
  • the set of bearings 6 L of the low temperature section L and the set of bearings 6 H of the high temperature section H thus receive respective flow rates D L and D H of lubricant equal to 300 L/h and 150 L/h, respectively.
  • the heat power P T to be removed by the heat exchanger 14 can nevertheless be reduced, e.g. to 5.8 kW, thus representing a reduction of 12% compared with the heat exchanger 114 of the prior art device 110 .
  • T R for the lubricant in the tank 11 138° C.
  • the overall flow rate D g is cooled in the heat exchanger 14 only down to a temperature T i,L that is higher than the temperature T i of the comparative device 110 , e.g. to a temperature T i,L of 115° C.
  • the flow D L delivered to the bearings 6 L is at this temperature T i,L and on receiving in the bearings 6 L a heat power P L that may likewise be 1.7 kW of heat from the bearings 6 L , is returned to the tank 11 at a temperature T o,L that is higher than in the comparative example of the prior art, e.g. a temperature T o,L of 125° C.
  • the flow D H delivered to the bearings 6 H is heated in the heat exchanger 30 by lubricant returning from those bearings 6 H up to a temperature T i,H that is higher than the temperature T i,L .
  • the temperature T i,H may be 135° C.
  • the flow D H will absorb perceptibly less heat power P L because of the smaller temperature difference.
  • this heat power P L may be no more than 4.1 kW.
  • the lubricant will also reach a temperature T o,H that is higher than in the comparative example of the prior art.
  • the temperature T o,H may be 185° C., for example. Nevertheless, since a fraction of the heat from the lubricant returning from the bearings 6 H is then transferred to the lubricant arriving in the heat exchanger 30 , the temperature T r,H of this flow D H on returning to the tank can be lower than the temperature T o,H of the comparative example of the prior art. For example, the temperature T r,H may be 165° C.
  • the lubricant thus reaches higher temperatures in the bearings 6 H in order to reduce the amount of heat power that is absorbed, the main limiting factor at present for reducing the heat power that is absorbed is the maximum temperature that may be reached by the lubricant. Since aviation lubricant typically has a coking temperature lying in a range of 180° C. to 210° C., the temperature T o,H should normally lie in this range, immediately below the coking temperature of the lubricant used.
  • the other limiting factor on the maximum temperature of the lubricant in the bearings 6 H is the highest temperature the bearings 6 H can themselves withstand, given that these bearings may be made out of materials that are particularly good at withstanding high temperatures, such as for example low-carbon steels such as M50 and M50NiL steels, nitrided steels such as 32 CDV 13 steel as defined by French aviation standard AIR 9160, or ceramics.
  • FIG. 3B shows an alternative embodiment that does not have the heat exchanger 30 upstream and downstream from the bearings 6 H, but in which the heat exchanger 14 is placed in the circuit 12 L downstream from the branch point 20 .
  • the heat exchanger 14 therefore cools only the flow of lubricant delivered to the bearings 6 L.
  • the lubricant delivered to the bearings 6 H is hotter than the lubricant delivered to the bearings 6 L, since it is only that lubricant which is cooled by the heat exchanger 14 .
  • the cooling requirements for the lubricant are therefore more moderate.
  • the set of bearings 6 L of the low temperature section L and the set of bearings 6 H of the high temperature section H thus receive respective flow rates D L and D H that may likewise be 300 L/h and 150 L/h for example.
  • the heat power P T to be removed by the heat exchanger 14 can thus likewise be reduced, e.g. to 5.5 kW, thus presenting a reduction of 16% compared with the heat exchanger 114 of the prior art device 110 .
  • T R for the lubricant in the tank 11 138° C.
  • the heat exchanger 14 cooling only the flow D L can nevertheless cause the temperature T i,L to drop below the prior art description T i , e.g. down to 104° C.
  • this lubricant flow D L returns to the tank 11 at a temperature T o,L that is substantially lower than the prior art temperature.
  • the temperature T o,L of the flow D L returning to the tank 11 in this embodiment may be 114° C.
  • the flow of lubricant D H is delivered to the bearings 6 H at a temperature T i,H that is hardly any lower than the temperature T R of the lubricant in the tank 11 , and that is thus substantially higher than the temperature T i,L .
  • the temperature T i,H in this embodiment may be 135° C.
  • T o,H that is significantly higher at the outlet from the bearings 6 H, e.g. a temperature of 185° C.
  • the flow D H will therefore absorb only a relatively limited amount of heat power P L from the bearings 6 H.
  • the power P L is limited to 4.2 kW.
  • FIG. 3C shows a third embodiment combining the characteristics of the first and second embodiments.
  • the heat exchanger 14 is situated downstream from the branch point 20 , as in the second embodiment, but the device 10 also includes a heat exchanger 30 interposed between the feed circuit 12 H and the return circuit 13 H, as in the first embodiment. It therefore serves to cool both the lubricant going to the bearings 6 L and the lubricant going to the bearings 6 H.
  • This third embodiment is more advantageous for devices that present a larger ratio between the flow rate of oil delivered to the bearings 6 H and the flow rate of oil delivered to the bearings 6 L.
  • FIG. 3D shows a fourth embodiment similar to the first embodiment, but with the heat exchanger 14 being situated between the first and second return circuits 13 L and 13 H and the tank 11 .
  • the lubricant is thus cooled upstream rather than downstream of the tank, which, depending on the thermal characteristics of the tank 11 , on its capacity, and on the flow rate of the circulating lubricant, may be more or less effective than the arrangement of the first embodiment.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Rolling Contact Bearings (AREA)
US13/980,696 2011-01-19 2012-01-10 Method and device for supplying a lubricant Abandoned US20140075916A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR1150421A FR2970504B1 (fr) 2011-01-19 2011-01-19 Procede et dispositif d'alimentation en lubrifiant
FR1150421 2011-01-19
PCT/FR2012/050057 WO2012098324A1 (fr) 2011-01-19 2012-01-10 Procede et dispositif d'alimentation en lubrifiant

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EP (1) EP2665900B1 (zh)
JP (1) JP5897602B2 (zh)
KR (1) KR101907228B1 (zh)
CN (1) CN103328779B (zh)
CA (1) CA2823670C (zh)
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US20160348583A1 (en) * 2011-01-19 2016-12-01 Safran Helicopter Engines Method and device for supplying a lubricant
US9909453B2 (en) 2015-05-19 2018-03-06 General Electric Company Lubrication system for a turbine engine
US10234018B2 (en) 2015-10-19 2019-03-19 General Electric Company Planet gearbox with cylindrical roller bearing with under race lube scheme
US10415429B2 (en) 2015-09-25 2019-09-17 General Electric Company Planet gearbox with cylindrical roller bearing with high density roller packing
US10787928B2 (en) 2015-12-01 2020-09-29 General Electric Company Casing for use in a turbofan engine and method of scavenging fluid therefrom
US10954818B2 (en) 2015-12-04 2021-03-23 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Turbocharger and engine system

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Publication number Priority date Publication date Assignee Title
FR3011277B1 (fr) * 2013-09-30 2018-04-06 Turbomeca Turbomachine adaptee a fonctionner en mode vireur
DE102020122588A1 (de) 2020-08-28 2022-03-03 Rolls-Royce Deutschland Ltd & Co Kg Ölsystem eines Gasturbinentriebwerkes und Gasturbinentriebwerk

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EP2665900A1 (fr) 2013-11-27
WO2012098324A1 (fr) 2012-07-26
US9708981B2 (en) 2017-07-18
RU2013138383A (ru) 2015-02-27
CA2823670C (fr) 2018-09-04
CN103328779A (zh) 2013-09-25
JP5897602B2 (ja) 2016-03-30
EP2665900B1 (fr) 2016-03-30
CN103328779B (zh) 2015-08-26
FR2970504B1 (fr) 2013-02-08
KR20140003489A (ko) 2014-01-09
RU2573077C2 (ru) 2016-01-20
FR2970504A1 (fr) 2012-07-20
KR101907228B1 (ko) 2018-12-07
JP2014503047A (ja) 2014-02-06
US20160348583A1 (en) 2016-12-01

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