EP3036439A1 - Fluid device output shaft with coating - Google Patents

Fluid device output shaft with coating

Info

Publication number
EP3036439A1
EP3036439A1 EP14837882.1A EP14837882A EP3036439A1 EP 3036439 A1 EP3036439 A1 EP 3036439A1 EP 14837882 A EP14837882 A EP 14837882A EP 3036439 A1 EP3036439 A1 EP 3036439A1
Authority
EP
European Patent Office
Prior art keywords
land
output shaft
coating
valving
fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP14837882.1A
Other languages
German (de)
French (fr)
Other versions
EP3036439A4 (en
Inventor
Takashi Konishi
Eiji Fukuchi
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.)
Eaton Corp
Original Assignee
Eaton Corp
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 Eaton Corp filed Critical Eaton Corp
Publication of EP3036439A1 publication Critical patent/EP3036439A1/en
Publication of EP3036439A4 publication Critical patent/EP3036439A4/en
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/008—Driving elements, brakes, couplings, transmissions specially adapted for rotary or oscillating-piston machines or engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/103—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F04C2/104—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement having an articulated driving shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F01C1/104—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/02—Arrangements of bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0088—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2230/00—Manufacture
    • F04C2230/90—Improving properties of machine parts
    • F04C2230/91—Coating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/04—PTFE [PolyTetraFluorEthylene]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/06—Polyamides, e.g. NYLON

Definitions

  • Hydraulic motors have many different shaft configurations and are used in many different applications. Some shaft configurations include tapered roller bearings, ball bearings, needle bearings and journal bearings. These bearings are used to support the output shaft in the hydraulic motor.
  • Hydraulic motors having journal bearings typically have lower side load capability than hydraulic motors having other types of bearings. While hydraulic motors using journal bearings are typically less expensive than other hydraulic motors using other types of bearings, the use of the other hydraulic motors may be necessitated solely as a result of side load capability. Therefore, it is desired to provide a hydraulic motor having journal bearings with improved side load capability.
  • An aspect of the present disclosure relates to a fluid device.
  • the fluid device includes a housing defining a central bore, a plurality of commutator holes that extend radially outward from the central bore and a plurality of axial passages in fluid communication with the commutator holes.
  • a fluid displacement assembly is in fluid communication with the housing.
  • the fluid displacement assembly includes a plurality of volume chambers in fluid communication with the axial passages of the housing.
  • An output shaft includes a valving portion disposed in the central bore of the housing.
  • the valving portion includes a first land, a second land and a valving land disposed between the first and second lands.
  • the first land cooperates with the central bore to define a first journal bearing and the second land cooperates with the central bore of the housing to define a second journal bearing.
  • a coating is applied to the first and second lands of the output shaft.
  • the coating includes a polyamide 11 material.
  • the fluid device includes a housing defining a central bore, a plurality of commutator holes that extend radially outward from the central bore and a plurality of axial passages in fluid communication with the commutator holes.
  • a fluid displacement assembly is in fluid communication with the housing.
  • the fluid displacement assembly includes a plurality of volume chambers in fluid communication with the axial passages of the housing.
  • An output shaft includes a valving portion disposed in the central bore of the housing.
  • the valving portion includes a first land and an oppositely disposed second land.
  • the first land cooperates with the central bore to define a first journal bearing and the second land cooperates with the central bore of the housing to define a second journal bearing.
  • a coating is applied to the first and second lands of the output shaft.
  • the coating includes a material selected from the group consisting of polyamide, polytetrafluoroethylene and combinations thereof.
  • the fluid device includes a housing defining a central bore, a plurality of commutator holes that extend radially outward from the central bore and a plurality of axial passages in fluid communication with the commutator holes.
  • a fluid displacement assembly is in fluid communication with the housing.
  • the fluid displacement assembly includes a plurality of volume chambers in fluid communication with the axial passages of the housing.
  • An output shaft includes a valving portion disposed in the central bore of the housing.
  • the valving portion includes a first land, a second land and a valving land disposed between the first and second lands.
  • the first land cooperates with the central bore to define a first journal bearing and the second land cooperates with the central bore of the housing to define a second journal bearing.
  • the valving portion of the output shaft defines a first groove disposed between the first land and the valving land and a second groove disposed between the second land and the valving land.
  • the first and second journal bearings are lubricated by fluid from the first and second grooves, respectively, during operation of the fluid device.
  • a coating is applied to the first and second lands and the valving land of the output shaft.
  • the coating includes a material selected from the group consisting of polyamide, polytetrafluoroethylene and combinations thereof.
  • Another aspect of the present disclosure relates to a method for manufacturing an output shaft for a fluid device.
  • the method includes machining a first land and a second land of a valving portion of an output shaft of a fluid device.
  • the output shaft is heat treated.
  • a first grinding operation is performed on the output shaft.
  • a coating is applied the first land and second land of the output shaft.
  • the coating includes a material selected from the group consisting of polyamide, polytetrafluoroethylene and combinations thereof.
  • a second grinding operation is performed on the first land and the second land of the output shaft.
  • Another aspect of the present disclosure relates to a method for manufacturing an output shaft for a fluid device.
  • the method includes machining an interface portion, a sealing portion and a valving portion of an output shaft, the sealing portion being disposed between the interface portion and the valving portion, wherein the valving portion includes a first land, a second land and a valving land disposed between the first and second lands.
  • the output shaft is heat treated.
  • a first grinding operation is performed on the output shaft.
  • a coating is applied the first land and second land of the output shaft.
  • the coating includes a polyamide material.
  • a second grinding operation is performed on the first land and the second land of the output shaft following the application of the coating.
  • FIG. 1 is a cross-sectional view of a fluid device having exemplary features of aspects in accordance with the principles of the present disclosure.
  • FIG. 2 is side view of an output shaft of the fluid device of FIG. 1.
  • FIG. 3 is a side view of the output shaft of FIG. 2 with an applied coating.
  • FIG. 4 is a graph of side load capacity versus rotational speed of the output shaft.
  • FIG. 5 is a representation of a method of manufacturing an output shaft.
  • the fluid device 10 is a fluid motor. In another embodiment, the fluid device 10 is a fluid pump.
  • the fluid device 10 includes a body 12.
  • the body 12 includes a plurality of sections.
  • the body 12 includes a flange 14, a housing 16, a spacer plate 18, a fluid displacement assembly 20, and an end cap 22.
  • the sections of the body 12 are held together in tight sealing engagement by a plurality of bolts 24.
  • the housing 16 is made of a metallic material.
  • the housing 16 is made of a ferrous metal (e.g., grey iron, ductile iron, etc.).
  • the housing 16 includes a first axial end 26 and an oppositely disposed second axial end 28.
  • the flange 14 abuts the first axial end 26 of the housing 16 while a first face 30 of the spacer plate 18 abuts the second axial end 28.
  • the fluid displacement assembly 20 abuts a second face 32 of the spacer plate 18.
  • the fluid displacement assembly 20 is a geroler® assembly.
  • the fluid displacement assembly 20 includes a ring 34, a star 36 and a plurality of rollers 38.
  • the star 36 is disposed in a central opening of the ring 34 and is adapted to obit and rotate about a central axis of the ring 34.
  • the ring 34, star 36 and rollers 38 cooperatively define a plurality of fluid volume chambers 40 that expand and contract as the star 36 orbits and rotates about the central axis of the ring 34.
  • the housing 16 defines a fluid inlet port (not shown) and a fluid outlet port 42.
  • the housing 16 defines a central bore 44 that extends through the first and second axial ends 26, 28.
  • the fluid inlet port is in fluid communication with the central bore 44 through a first fluid passage (not shown).
  • the fluid outlet port 42 is in fluid communication with the central bore 44 through a second fluid passage 46.
  • the housing 16 defines a plurality of commutator holes 48.
  • the commutator holes 48 extend radially outward from the central bore 44.
  • the housing 16 further defines a plurality of axial passages 50 in fluid communication with the plurality of commutator holes 48.
  • the axial passages 50 are in fluid communication with the fluid volume chambers 40 of the fluid displacement assembly 20.
  • the fluid device 10 further includes an output shaft assembly 52.
  • the output shaft assembly 52 includes a bearing assembly 54 and an output shaft 56.
  • the bearing assembly 54 includes a bearing race 58 and a thrust bearing 60.
  • the output shaft 56 is shown.
  • the output shaft 56 is adapted to rotate about a central axis 62.
  • the output shaft 56 is made from a metallic material.
  • the output shaft 56 is made from a ferrous metal (e.g., steel, etc.).
  • the output shaft 56 includes an interface portion 64, a sealing portion 66 and a valving portion 68.
  • the sealing portion 66 is disposed between the interface portion 64 and the valving portion 68.
  • the interface portion 64 of the output shaft 56 is adapted for coupling to a customer application (e.g., a coupler, a wheel hub, a winch, etc.).
  • the interface portion 64 extends outwardly from the flange 14 of the fluid device 10.
  • the interface portion 64 defines a keyway 70 that is adapted to receive a shaft key 72.
  • the sealing portion 66 of the output shaft 56 is operably associated with a shaft seal 74 (shown in FIG. 1).
  • the shaft seal 74 is disposed in the flange 14 of the motor 14 and is adapted to prevent fluid in the interior of the fluid device 10 from leaking to the exterior of the fluid device 10 at the shaft-flange interface.
  • An outer diameter of the sealing portion 66 of the output shaft 56 is greater than an outer diameter of the interface portion 64.
  • the valving portion 68 of the output shaft 56 is disposed in the central bore 44 of the housing 16.
  • the valving portion 68 includes a first end 76 and an oppositely disposed second end 78.
  • the first end 76 of the valving portion 68 is disposed immediately adjacent to the sealing portion 66.
  • the valving portion 68 further includes a first land 80, a second land 82 and a valving land 84.
  • the first land 80 is disposed adjacent to the first end 76 while the second land 82 is disposed adjacent to the second end 78.
  • the valving land 84 is disposed between the first and second lands 80, 82.
  • the valving portion 68 defines a first groove 86 that is disposed between the first land 80 and the valving land 84.
  • the first groove 86 extends circumferentially about the central axis 62 of the output shaft 56.
  • the first groove 86 is in fluid communication with the first fluid port of the housing 16 when the valving portion 68 of the output shaft 56 is disposed in the central bore 44 of the housing 16.
  • the valving portion 68 defines a second groove 88 that is disposed between the second land 82 and the valving land 84.
  • the second groove 88 extends circumferentially about the central axis 62 of the output shaft 56.
  • the second groove 88 is in fluid communication with the second fluid port 52 of the housing 16 when the valving portion 68 of the output shaft 56 is disposed in the central bore 44 of the housing 16.
  • the valving land 84 of the valving portion 68 defines a first plurality of slots 90 that is in fluid communication with the first groove 86 and a second plurality of slots 92 that is in fluid communication with the second groove 88.
  • the first and second pluralities of slots 90, 92 extend in an axial direction. In the depicted embodiment, the first and second pluralities of slots 90, 92 are alternately disposed about the valving land 84 of the valving portion 68 of the output shaft 56.
  • the first and second pluralities of slots 90, 92 are in commutating fluid communication with commutator holes 48 in the housing 16.
  • This commutating fluid communication provides selective fluid communication between the first and second fluid ports of the housing 16 and the volume chambers 40 of the fluid displacement assembly 20.
  • the first land 80 of the output shaft 56 and the central bore 44 of the housing 16 cooperatively define a first journal bearing 94 (shown in FIG. 1).
  • the second land 82 of the output shaft 56 and the central bore 44 of the housing 16 cooperatively define a second journal bearing 96 (shown in FIG. 1).
  • the first and second journal bearings 94, 96 allow the fluid device 10 to function when a radial force F (shown in FIG. 1) is applied to the output shaft 56.
  • the first and second journal bearings 94, 96 are lubricated by fluid in the first and second grooves 86, 88, respectively, of the output shaft 56. Fluid in the first and second grooves 86, 88 passes over the first and second lands 80, 82 of the output shaft 56, respectively. This fluid creates a hydrodynamic film across the first and second journal bearings 94, 96. This film allows the output shaft 56 to rotate when the radial force F is applied to the output shaft 56.
  • a coating 100 is applied to a surface of the rotating component of the first and second journal bearings 94, 96 (shown in FIG. 1).
  • the coating 100 is applied to the first land 80 and the second land 82 of the output shaft 56.
  • the coating 100 is also applied to the valving land 84 of the output shaft 56.
  • the coating 100 includes a polyamide (PA) material. In one embodiment, the coating 100 includes a polyamide 11 (PA11) material. In one embodiment, the polyamide material is at least about 50% by weight of the coating 100.
  • the coating 100 includes a polytetrafluoroethylene (PTFE) material.
  • PTFE polytetrafluoroethylene
  • the polytetrafluoroethylene material is at least about 50% by weight of the coating 100.
  • a thickness of the coating 100 at the first and second lands 80, 82 of the output shaft 56 is greater than or equal to about 0.1 mm. In another embodiment, the thickness of the coating 100 at the first and second lands 80, 82 of the output shaft 56 is less than or equal to about 0.2 mm. In another embodiment, the thickness of the coating 100 at the first and second lands 80, 82 of the output shaft 56 is in a range of about 0.1 mm to about 0.2 mm.
  • FIG. 4 a graph of side load capability of a fluid device having a standard output shaft without the coating 100 and the fluid device 10 having the output shaft 56 with the coating 100 is shown.
  • the dashed line in FIG. 4 represents the side load capability of a standard output shaft that has a phosphate coating that is adapted to reduce galling between the lands of the output shaft and the central bore of the housing.
  • the solid line in FIG. 4 represents the side load capacity of the output shaft 56 with the coating 100 that includes poly amide 11.
  • the side load capacity of the output shaft of the fluid device 10 with the coating 100 is about 150% of the side load capacity of the output shaft without the coating 100.
  • the radial clearance between the lands of the output shaft and the central bore of the housing would need to be increased significantly to allow for more fluid from the first and second grooves to pass across the lands.
  • such an increase in radial clearance would have a negative effect on the volumetric efficiency of the fluid device.
  • the coating 100 applied to the output shaft 56 of the fluid device 10 allows for the radial clearance between the first and second lands 80, 82 to be minimized while providing significantly improved side load capability. This minimization of radial clearance allows the fluid device 10 to perform at volumetric efficiencies greater than or equal to the standard fluid device at rated side load capabilities. Thus, the coating 100 provides increased side load capability without sacrificing volumetric efficiency.
  • step 202 the output shaft 56 is machined from an output shaft blank.
  • the interface portion 64, the sealing portion 66 and the valving portion 68 are machined (e.g., turned, milled, etc.).
  • the first land 80, the second land 82 and the valving land 84 of the valving portion 68 are machined in step 202.
  • step 204 the output shaft 56 is heat treated to a desired hardness.
  • step 206 a first grinding operation is performed on the heat treated output shaft 56. In one embodiment, the grinding operation 206 is performed on the outer diameter of the interface portion 64, the sealing portion 66 and the valving portion 68 of the output shaft 56.
  • the interface portion 64 and the sealing portion 66 of the output shaft 56 are masked (e.g., concealed or covered) by a covering in step 208.
  • the output shaft 56 is coated with the coating 100.
  • the coating 100 is applied to the output shaft 56.
  • a portion of the output shaft 56 is masked. Therefore, the coating 100 is only applied to the unmasked portion of the output shaft 56.
  • the coating 100 is applied to the valving portion 68 of the output shaft 100.
  • the coating 100 is applied to the first land 80, the second land 82, and the valving land 84 of the output shaft 56.
  • the coating 100 is sprayed onto the output shaft 56.
  • the output shaft 56 is dipped into the coating 100.
  • a second grinding operation is performed on the portion of the output shaft 56 having the coating 100.
  • the second grinding operation is performed on the first land 80, the second land 82 and the valving land 84.
  • the second grinding operation is adapted to remove excess amounts of the coating 100 from the output shaft 56.
  • the second grinding operation is adapted to provide a thickness of the coating 100 that is greater than or equal to about 0.1 mm.
  • the second grinding operation is adapted to provide a thickness of the coating 100 that is less than or equal to about 0.2 mm.
  • the second grinding operation is adapted to provide a thickness of the coating 100 that is in a range of about 0.1 mm to about 0.2 mm.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Sliding-Contact Bearings (AREA)
  • Hydraulic Motors (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

A fluid device includes a housing defining a central bore, a plurality of commutator holes that extend radially outward from the central bore and a plurality of axial passages in fluid communication with the commutator holes. A fluid displacement assembly is in fluid communication with the housing. The fluid displacement assembly includes volume chambers in fluid communication with the axial passages of the housing. An output shaft includes a valving portion disposed in the central bore of the housing. The valving portion includes a first and second lands and a valving land disposed between the first and second lands. The first land cooperates with the central bore to define a first journal bearing and the second land cooperates with the central bore to define a second journal bearing. A coating is applied to the first and second lands of the output shaft. The coating includes a polyamide 11 material.

Description

FLUID DEVICE OUTPUT SHAFT WITH COATING
CROSS-REFERENCE TO RELATED APPLICATIONS
This application is being filed on August 22, 2014, as a PCT International Patent application and claims priority to U.S. Patent Application Serial No. 61/869,348 filed on August 23, 2014, the disclosure of which is incorporated herein by reference in its entirety.
BACKGROUND
Hydraulic motors have many different shaft configurations and are used in many different applications. Some shaft configurations include tapered roller bearings, ball bearings, needle bearings and journal bearings. These bearings are used to support the output shaft in the hydraulic motor.
Many applications apply radial loads on the output shaft of the hydraulic motor. As a result, the type of hydraulic motor chosen for an application may depend on the magnitude of the radial load being applied to the output shaft.
Hydraulic motors having journal bearings typically have lower side load capability than hydraulic motors having other types of bearings. While hydraulic motors using journal bearings are typically less expensive than other hydraulic motors using other types of bearings, the use of the other hydraulic motors may be necessitated solely as a result of side load capability. Therefore, it is desired to provide a hydraulic motor having journal bearings with improved side load capability.
SUMMARY
An aspect of the present disclosure relates to a fluid device. The fluid device includes a housing defining a central bore, a plurality of commutator holes that extend radially outward from the central bore and a plurality of axial passages in fluid communication with the commutator holes. A fluid displacement assembly is in fluid communication with the housing. The fluid displacement assembly includes a plurality of volume chambers in fluid communication with the axial passages of the housing. An output shaft includes a valving portion disposed in the central bore of the housing. The valving portion includes a first land, a second land and a valving land disposed between the first and second lands. The first land cooperates with the central bore to define a first journal bearing and the second land cooperates with the central bore of the housing to define a second journal bearing. A coating is applied to the first and second lands of the output shaft. The coating includes a polyamide 11 material.
Another aspect of the present disclosure relates to a fluid device. The fluid device includes a housing defining a central bore, a plurality of commutator holes that extend radially outward from the central bore and a plurality of axial passages in fluid communication with the commutator holes. A fluid displacement assembly is in fluid communication with the housing. The fluid displacement assembly includes a plurality of volume chambers in fluid communication with the axial passages of the housing. An output shaft includes a valving portion disposed in the central bore of the housing. The valving portion includes a first land and an oppositely disposed second land. The first land cooperates with the central bore to define a first journal bearing and the second land cooperates with the central bore of the housing to define a second journal bearing. A coating is applied to the first and second lands of the output shaft. The coating includes a material selected from the group consisting of polyamide, polytetrafluoroethylene and combinations thereof.
Another aspect of the present disclosure relates to a fluid device. The fluid device includes a housing defining a central bore, a plurality of commutator holes that extend radially outward from the central bore and a plurality of axial passages in fluid communication with the commutator holes. A fluid displacement assembly is in fluid communication with the housing. The fluid displacement assembly includes a plurality of volume chambers in fluid communication with the axial passages of the housing. An output shaft includes a valving portion disposed in the central bore of the housing. The valving portion includes a first land, a second land and a valving land disposed between the first and second lands. The first land cooperates with the central bore to define a first journal bearing and the second land cooperates with the central bore of the housing to define a second journal bearing. The valving portion of the output shaft defines a first groove disposed between the first land and the valving land and a second groove disposed between the second land and the valving land. The first and second journal bearings are lubricated by fluid from the first and second grooves, respectively, during operation of the fluid device. A coating is applied to the first and second lands and the valving land of the output shaft. The coating includes a material selected from the group consisting of polyamide, polytetrafluoroethylene and combinations thereof.
Another aspect of the present disclosure relates to a method for manufacturing an output shaft for a fluid device. The method includes machining a first land and a second land of a valving portion of an output shaft of a fluid device. The output shaft is heat treated. A first grinding operation is performed on the output shaft. A coating is applied the first land and second land of the output shaft. The coating includes a material selected from the group consisting of polyamide, polytetrafluoroethylene and combinations thereof. A second grinding operation is performed on the first land and the second land of the output shaft.
Another aspect of the present disclosure relates to a method for manufacturing an output shaft for a fluid device. The method includes machining an interface portion, a sealing portion and a valving portion of an output shaft, the sealing portion being disposed between the interface portion and the valving portion, wherein the valving portion includes a first land, a second land and a valving land disposed between the first and second lands. The output shaft is heat treated. A first grinding operation is performed on the output shaft. A coating is applied the first land and second land of the output shaft. The coating includes a polyamide material. A second grinding operation is performed on the first land and the second land of the output shaft following the application of the coating.
DRAWINGS
FIG. 1 is a cross-sectional view of a fluid device having exemplary features of aspects in accordance with the principles of the present disclosure.
FIG. 2 is side view of an output shaft of the fluid device of FIG. 1.
FIG. 3 is a side view of the output shaft of FIG. 2 with an applied coating.
FIG. 4 is a graph of side load capacity versus rotational speed of the output shaft.
FIG. 5 is a representation of a method of manufacturing an output shaft. DETAILED DESCRIPTION
Reference will now be made in detail to the exemplary aspects of the present disclosure that are illustrated in the accompanying drawings. Wherever possible, the same reference numbers will be used throughout the drawings to refer to the same or like structure.
Referring now to FIG. 1, a fluid device 10 is shown. In the subject embodiment, the fluid device 10 is a fluid motor. In another embodiment, the fluid device 10 is a fluid pump.
The fluid device 10 includes a body 12. In the depicted embodiment, the body 12 includes a plurality of sections. In the depicted embodiment, the body 12 includes a flange 14, a housing 16, a spacer plate 18, a fluid displacement assembly 20, and an end cap 22. The sections of the body 12 are held together in tight sealing engagement by a plurality of bolts 24.
The housing 16 is made of a metallic material. In the depicted embodiment, the housing 16 is made of a ferrous metal (e.g., grey iron, ductile iron, etc.). The housing 16 includes a first axial end 26 and an oppositely disposed second axial end 28. In the depicted embodiment, the flange 14 abuts the first axial end 26 of the housing 16 while a first face 30 of the spacer plate 18 abuts the second axial end 28. The fluid displacement assembly 20 abuts a second face 32 of the spacer plate 18. In the depicted embodiment, the fluid displacement assembly 20 is a geroler® assembly. The fluid displacement assembly 20 includes a ring 34, a star 36 and a plurality of rollers 38. The star 36 is disposed in a central opening of the ring 34 and is adapted to obit and rotate about a central axis of the ring 34. The ring 34, star 36 and rollers 38 cooperatively define a plurality of fluid volume chambers 40 that expand and contract as the star 36 orbits and rotates about the central axis of the ring 34.
In the depicted embodiment, the housing 16 defines a fluid inlet port (not shown) and a fluid outlet port 42. The housing 16 defines a central bore 44 that extends through the first and second axial ends 26, 28. The fluid inlet port is in fluid communication with the central bore 44 through a first fluid passage (not shown). The fluid outlet port 42 is in fluid communication with the central bore 44 through a second fluid passage 46. The housing 16 defines a plurality of commutator holes 48. The commutator holes 48 extend radially outward from the central bore 44. The housing 16 further defines a plurality of axial passages 50 in fluid communication with the plurality of commutator holes 48. The axial passages 50 are in fluid communication with the fluid volume chambers 40 of the fluid displacement assembly 20.
The fluid device 10 further includes an output shaft assembly 52. In the depicted embodiment, the output shaft assembly 52 includes a bearing assembly 54 and an output shaft 56. In the depicted embodiment, the bearing assembly 54 includes a bearing race 58 and a thrust bearing 60.
Referring now to FIGS 1 and 2, the output shaft 56 is shown. The output shaft 56 is adapted to rotate about a central axis 62. The output shaft 56 is made from a metallic material. In the depicted embodiment, the output shaft 56 is made from a ferrous metal (e.g., steel, etc.).
The output shaft 56 includes an interface portion 64, a sealing portion 66 and a valving portion 68. In the depicted embodiment, the sealing portion 66 is disposed between the interface portion 64 and the valving portion 68.
The interface portion 64 of the output shaft 56 is adapted for coupling to a customer application (e.g., a coupler, a wheel hub, a winch, etc.). The interface portion 64 extends outwardly from the flange 14 of the fluid device 10. In the depicted embodiment, the interface portion 64 defines a keyway 70 that is adapted to receive a shaft key 72.
The sealing portion 66 of the output shaft 56 is operably associated with a shaft seal 74 (shown in FIG. 1). The shaft seal 74 is disposed in the flange 14 of the motor 14 and is adapted to prevent fluid in the interior of the fluid device 10 from leaking to the exterior of the fluid device 10 at the shaft-flange interface. An outer diameter of the sealing portion 66 of the output shaft 56 is greater than an outer diameter of the interface portion 64.
The valving portion 68 of the output shaft 56 is disposed in the central bore 44 of the housing 16. The valving portion 68 includes a first end 76 and an oppositely disposed second end 78. The first end 76 of the valving portion 68 is disposed immediately adjacent to the sealing portion 66. The valving portion 68 further includes a first land 80, a second land 82 and a valving land 84. The first land 80 is disposed adjacent to the first end 76 while the second land 82 is disposed adjacent to the second end 78. The valving land 84 is disposed between the first and second lands 80, 82.
The valving portion 68 defines a first groove 86 that is disposed between the first land 80 and the valving land 84. The first groove 86 extends circumferentially about the central axis 62 of the output shaft 56. In the depicted embodiment, the first groove 86 is in fluid communication with the first fluid port of the housing 16 when the valving portion 68 of the output shaft 56 is disposed in the central bore 44 of the housing 16.
The valving portion 68 defines a second groove 88 that is disposed between the second land 82 and the valving land 84. The second groove 88 extends circumferentially about the central axis 62 of the output shaft 56. In the depicted embodiment, the second groove 88 is in fluid communication with the second fluid port 52 of the housing 16 when the valving portion 68 of the output shaft 56 is disposed in the central bore 44 of the housing 16.
The valving land 84 of the valving portion 68 defines a first plurality of slots 90 that is in fluid communication with the first groove 86 and a second plurality of slots 92 that is in fluid communication with the second groove 88. The first and second pluralities of slots 90, 92 extend in an axial direction. In the depicted embodiment, the first and second pluralities of slots 90, 92 are alternately disposed about the valving land 84 of the valving portion 68 of the output shaft 56.
As the output shaft 56 rotates in the central bore 44 of the housing 16, the first and second pluralities of slots 90, 92 are in commutating fluid communication with commutator holes 48 in the housing 16. This commutating fluid communication provides selective fluid communication between the first and second fluid ports of the housing 16 and the volume chambers 40 of the fluid displacement assembly 20.
The first land 80 of the output shaft 56 and the central bore 44 of the housing 16 cooperatively define a first journal bearing 94 (shown in FIG. 1). The second land 82 of the output shaft 56 and the central bore 44 of the housing 16 cooperatively define a second journal bearing 96 (shown in FIG. 1). The first and second journal bearings 94, 96 allow the fluid device 10 to function when a radial force F (shown in FIG. 1) is applied to the output shaft 56. The first and second journal bearings 94, 96 are lubricated by fluid in the first and second grooves 86, 88, respectively, of the output shaft 56. Fluid in the first and second grooves 86, 88 passes over the first and second lands 80, 82 of the output shaft 56, respectively. This fluid creates a hydrodynamic film across the first and second journal bearings 94, 96. This film allows the output shaft 56 to rotate when the radial force F is applied to the output shaft 56.
Referring now to FIG. 3, a coating 100 is applied to a surface of the rotating component of the first and second journal bearings 94, 96 (shown in FIG. 1). In the subject embodiment, the coating 100 is applied to the first land 80 and the second land 82 of the output shaft 56. In the depicted embodiment, the coating 100 is also applied to the valving land 84 of the output shaft 56.
In the depicted embodiment, the coating 100 includes a polyamide (PA) material. In one embodiment, the coating 100 includes a polyamide 11 (PA11) material. In one embodiment, the polyamide material is at least about 50% by weight of the coating 100.
In another embodiment, the coating 100 includes a polytetrafluoroethylene (PTFE) material. In one embodiment, the polytetrafluoroethylene material is at least about 50% by weight of the coating 100.
In the subject embodiment, a thickness of the coating 100 at the first and second lands 80, 82 of the output shaft 56 is greater than or equal to about 0.1 mm. In another embodiment, the thickness of the coating 100 at the first and second lands 80, 82 of the output shaft 56 is less than or equal to about 0.2 mm. In another embodiment, the thickness of the coating 100 at the first and second lands 80, 82 of the output shaft 56 is in a range of about 0.1 mm to about 0.2 mm.
Referring now to FIG. 4, a graph of side load capability of a fluid device having a standard output shaft without the coating 100 and the fluid device 10 having the output shaft 56 with the coating 100 is shown. The dashed line in FIG. 4 represents the side load capability of a standard output shaft that has a phosphate coating that is adapted to reduce galling between the lands of the output shaft and the central bore of the housing. The solid line in FIG. 4 represents the side load capacity of the output shaft 56 with the coating 100 that includes poly amide 11.
As shown in FIG. 4, applying the coating 100 to the output shaft 56 provides a significant increase in shaft side load capacity. In the depicted embodiment, the side load capacity of the output shaft of the fluid device 10 with the coating 100 is about 150% of the side load capacity of the output shaft without the coating 100. In order to achieve these side load capacities in the standard output shaft (shown in dashed lines in FIG. 4), the radial clearance between the lands of the output shaft and the central bore of the housing would need to be increased significantly to allow for more fluid from the first and second grooves to pass across the lands. However, such an increase in radial clearance would have a negative effect on the volumetric efficiency of the fluid device.
The coating 100 applied to the output shaft 56 of the fluid device 10 allows for the radial clearance between the first and second lands 80, 82 to be minimized while providing significantly improved side load capability. This minimization of radial clearance allows the fluid device 10 to perform at volumetric efficiencies greater than or equal to the standard fluid device at rated side load capabilities. Thus, the coating 100 provides increased side load capability without sacrificing volumetric efficiency.
Referring now to FIGS. 2, 3 and 5, a method 200 for manufacturing the output shaft 56 of the fluid device 10 is shown. In step 202, the output shaft 56 is machined from an output shaft blank. In one embodiment of step 202, the interface portion 64, the sealing portion 66 and the valving portion 68 are machined (e.g., turned, milled, etc.). In one embodiment, the first land 80, the second land 82 and the valving land 84 of the valving portion 68 are machined in step 202.
In step 204, the output shaft 56 is heat treated to a desired hardness. In step 206, a first grinding operation is performed on the heat treated output shaft 56. In one embodiment, the grinding operation 206 is performed on the outer diameter of the interface portion 64, the sealing portion 66 and the valving portion 68 of the output shaft 56.
After the grinding operation 206, the interface portion 64 and the sealing portion 66 of the output shaft 56 are masked (e.g., concealed or covered) by a covering in step 208. In step 210, the output shaft 56 is coated with the coating 100. In step 210, the coating 100 is applied to the output shaft 56. In the subject embodiment, a portion of the output shaft 56 is masked. Therefore, the coating 100 is only applied to the unmasked portion of the output shaft 56. In the depicted embodiment, the coating 100 is applied to the valving portion 68 of the output shaft 100. In the depicted embodiment, the coating 100 is applied to the first land 80, the second land 82, and the valving land 84 of the output shaft 56. In one embodiment, the coating 100 is sprayed onto the output shaft 56. In another embodiment, the output shaft 56 is dipped into the coating 100.
After the coating 100 has been applied to the output shaft 56, the masking is removed from the output shaft 56 in step 212. In step 214, a second grinding operation is performed on the portion of the output shaft 56 having the coating 100. In the depicted embodiment, the second grinding operation is performed on the first land 80, the second land 82 and the valving land 84. The second grinding operation is adapted to remove excess amounts of the coating 100 from the output shaft 56. In the depicted embodiment, the second grinding operation is adapted to provide a thickness of the coating 100 that is greater than or equal to about 0.1 mm. In another embodiment, the second grinding operation is adapted to provide a thickness of the coating 100 that is less than or equal to about 0.2 mm. In another embodiment, the second grinding operation is adapted to provide a thickness of the coating 100 that is in a range of about 0.1 mm to about 0.2 mm.
Various modifications and alterations of this disclosure will become apparent to those skilled in the art without departing from the scope and spirit of this disclosure, and it should be understood that the scope of this disclosure is not to be unduly limited to the illustrative embodiments set forth herein.

Claims

What is claimed is:
1. A fluid device comprising:
a housing defining a central bore, a plurality of commutator holes that extend radially outward from the central bore and a plurality of axial passages in fluid communication with the commutator holes;
a fluid displacement assembly in fluid communication with the housing, the fluid displacement assembly including a plurality of volume chambers in fluid communication with the axial passages of the housing;
an output shaft having a valving portion disposed in the central bore of the housing, the valving portion having a first land, a second land and a valving land disposed between the first and second lands, wherein the first land cooperates with the central bore of the housing to define a first journal bearing and the second land cooperates with the central bore of the housing to define a second journal bearing; and
a coating applied to the first and second lands and the valving land of the output shaft, the coating including a polyamide 11 material.
2. The fluid device of claim 1, wherein the polyamide 11 material is at least 50% by weight of the coating.
3. The fluid device of claim 1, wherein a thickness of the coating is greater than or equal to about 0.1 mm.
4. The fluid device of claim 3, wherein the thickness of the coating is less than or equal to about 0.2 mm.
5. The fluid device of claim 1, wherein the coating is applied to the valving portion of the output shaft.
6. The fluid device of claim 1 , wherein the valving portion of the output shaft includes a first groove disposed between the first land and the valving land and a second groove disposed between the second land and the valving land.
7. The fluid device of claim 6, wherein the first and second journal bearings are lubricated by fluid from the first and second grooves, respectively, during operation of the fluid device.
8. The fluid device of claim 1, wherein the housing defines a fluid inlet port and a fluid outlet port.
9. A fluid device comprising:
a housing defining a central bore, a plurality of commutator holes that extend radially outward from the central bore and a plurality of axial passages in fluid communication with the commutator holes;
a fluid displacement assembly in fluid communication with the housing, the fluid displacement assembly including a plurality of volume chambers in fluid communication with the axial passages of the housing;
an output shaft having a valving portion disposed in the central bore of the housing, the valving portion having a first land and an oppositely disposed second land, wherein the first land cooperates with the central bore of the housing to define a first journal bearing and the second land cooperates with the central bore of the housing to define a second journal bearing; and
a coating applied to the first and second lands of the output shaft, the coating including a material selected from the group consisting of polyamide,
polytetrafluoroethylene and combinations thereof.
10. The fluid device of claim 9, wherein the material is at least 50% by weight of the coating.
11. The fluid device of claim 9, wherein a thickness of the coating is greater than or equal to about 0.1 mm.
12. The fluid device of claim 11, wherein the thickness of the coating is less than or equal to about 0.2 mm.
13. The fluid device of claim 9, wherein the output shaft includes a valving land disposed between the first and second lands, the valving land defining a first plurality of slots that extend axially outward from a first groove disposed between the first land and the valving land and a second plurality of slots extends outwardly from a second groove disposed between the valving land and the second groove.
14. The fluid device of claim 13, wherein the first and second journal bearings are lubricated by fluid from the first and second grooves, respectively, during operation of the fluid device.
15. The fluid device of claim 14, wherein the coating is applied to the valving land.
16. The fluid device of claim 9, wherein the coating is applied to the valving portion of the output shaft.
17. A fluid device comprising:
a housing defining a central bore, a plurality of commutator holes that extend radially outward from the central bore and a plurality of axial passages in fluid communication with the commutator holes;
a fluid displacement assembly in fluid communication with the housing, the fluid displacement assembly including a plurality of volume chambers in fluid communication with the axial passages of the housing;
an output shaft having a valving portion disposed in the central bore of the housing, the valving portion having a first land, a second land and a valving land disposed between the first and second lands, the first land cooperating with the central bore of the housing to define a first journal bearing and the second land cooperating with the central bore of the housing to define a second journal bearing, the valving portion of the output shaft defining a first groove disposed between the first land and the valving land and a second groove disposed between the second land and the valving land, wherein the first and second journal bearings are lubricated by fluid from the first and second grooves, respectively, during operation of the fluid device; and a coating applied to the first and second lands and the valving land of the output shaft, the coating including a material selected from the group consisting of polyamide, polytetrafluoroethylene and combinations thereof.
18. The fluid device of claim 17, wherein the material is at least 50% by weight of the coating.
19. The fluid device of claim 17, wherein a thickness of the coating is greater than or equal to about 0.1 mm.
20. The fluid device of claim 17, wherein a thickness of the coating is less than or equal to about 0.2 mm.
21. A method for manufacturing an output shaft for a fluid device comprising:
machining a first land and second land of a valving portion of an output shaft of a fluid device;
heat treating the output shaft;
performing a first grinding operation on the output shaft;
applying a coating to the first land and second land of the output shaft, the coating including a material selected from the group consisting of polyamide,
polytetrafluoroethylene and combinations thereof; and
performing a second grinding operation on the first land and second land of the output shaft.
22. The method of claim 21, wherein the thickness of the coating on the first land and second land of the output shaft after the second grinding operation is in a range of about 0.1 mm to about 0.2 mm.
23. The method of claim 21, wherein the material includes polyamide 11.
24. The method of claim 23, wherein the material is at least 50% by weight of the coating.
25. The method of claim 21, wherein a valving land that is disposed between the first land and the second land of the valving portion of the output shaft is coated with the coating.
26. A method for manufacturing an output shaft for a fluid device comprising:
machining an interface portion, a sealing portion and a valving portion of an output shaft, the sealing portion being disposed between the interface portion and the valving portion, wherein the valving portion includes a first land, a second land and a valving land, the valving land being disposed between the first and second lands;
heat treating the output shaft;
performing a first grinding operation on the output shaft;
applying a coating to the first land and the second land of the output shaft, the coating including a polyamide material; and
performing a second grinding operation on the first land and second land of the output shaft following the application of the coating.
27. The method of claim 26, wherein the polyamide material includes polyamide 11.
28. The method of claim 26, wherein the valving land of the valving portion of the output shaft is coated with the coating.
29. The method of claim 26, wherein the thickness of the coating on the output shaft after the second grinding operation is in a range of about 0.1 mm to about 0.2 mm.
EP14837882.1A 2013-08-23 2014-08-22 Fluid device output shaft with coating Withdrawn EP3036439A4 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201361869348P 2013-08-23 2013-08-23
PCT/US2014/052263 WO2015027143A1 (en) 2013-08-23 2014-08-22 Fluid device output shaft with coating

Publications (2)

Publication Number Publication Date
EP3036439A1 true EP3036439A1 (en) 2016-06-29
EP3036439A4 EP3036439A4 (en) 2017-07-26

Family

ID=52484188

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14837882.1A Withdrawn EP3036439A4 (en) 2013-08-23 2014-08-22 Fluid device output shaft with coating

Country Status (5)

Country Link
US (1) US20160201463A1 (en)
EP (1) EP3036439A4 (en)
JP (1) JP2016529438A (en)
CN (1) CN105593528A (en)
WO (1) WO2015027143A1 (en)

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2747222A (en) * 1951-06-11 1956-05-29 Polymer Corp Production of nylon rod
DE2107493B2 (en) * 1971-02-17 1973-02-08 Danfoss A/S, Nordborg (Danemark) PARALLEL AND IN-AXIS ROTARY LISTON MACHINE
US3881791A (en) * 1973-03-02 1975-05-06 Skf Ind Trading & Dev Dry journal bearing
JPS53150503U (en) * 1977-05-04 1978-11-27
US4362479A (en) * 1981-03-25 1982-12-07 Eaton Corporation Rotary fluid pressure device and lubrication circuit therefor
JPS63263278A (en) * 1987-04-17 1988-10-31 Sanyo Electric Co Ltd Sliding member for compressor
CN2229563Y (en) * 1994-11-18 1996-06-19 武汉水泵厂 Vertical macro-axis pump
JP3795984B2 (en) * 1996-12-20 2006-07-12 富士通株式会社 Wireless receiver
KR20000046648A (en) * 1998-12-31 2000-07-25 윤종용 Compressor
US7595095B2 (en) * 2000-09-12 2009-09-29 Koyo Seiko Co. Coated article, manufacturing method therefor and coating apparatus
EP1664561A4 (en) * 2003-09-12 2007-01-10 Minebea Co Ltd Fluid dynamic bearing unit
US7695258B2 (en) * 2006-05-08 2010-04-13 White Drive Products, Inc. Gerotor motor and brake assembly
JP2008111390A (en) * 2006-10-31 2008-05-15 Sanden Corp Compressor
US8029965B2 (en) * 2007-03-08 2011-10-04 Konica Minolta Business Technologies, Inc. Developing roller and image forming method employing the same
US7845919B2 (en) * 2007-03-30 2010-12-07 Eaton Corporation Brake releasing mechanism and brake system
WO2009095740A1 (en) * 2008-01-30 2009-08-06 Danfoss Commercial Compressors Temporary self-lubricating coating for scroll compressor
DE102008055194A1 (en) * 2008-12-30 2010-07-08 Federal-Mogul Wiesbaden Gmbh Slide
JP5776228B2 (en) * 2011-03-07 2015-09-09 株式会社ジェイテクト Shaft member for rolling bearing device for wheel and manufacturing method thereof
EP2530317B1 (en) * 2011-06-03 2014-11-12 Perkins Engines Company Limited Bearing coating for fuel lubricated fuel pumps

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2015027143A1 *

Also Published As

Publication number Publication date
EP3036439A4 (en) 2017-07-26
US20160201463A1 (en) 2016-07-14
CN105593528A (en) 2016-05-18
JP2016529438A (en) 2016-09-23
WO2015027143A1 (en) 2015-02-26

Similar Documents

Publication Publication Date Title
WO2003078870A1 (en) Gear unit lubrication
US6629829B1 (en) Vane type rotary machine
CN102834630A (en) Drives for wind power plants
CN113847238B (en) Axial pressure relief for pump slide bearing
US8979471B2 (en) Bearing carrier with multiple lubrication slots
WO2020064398A1 (en) Compact sliding-contact bearing with a sealing arrangement, and water pump with same
US6935849B2 (en) Grooved shaft member and associated turbocharger and method
CN103534485A (en) Fluid device with pressurized roll pockets
US20160201463A1 (en) Fluid device output shaft with coating
US12066109B2 (en) Seal assembly and method of using the same
CN105134787B (en) A kind of bearing ring and bearing
CN111075832A (en) Sliding bearing
CN104100481B (en) The radial piston machine of piston unit and hydrostatic
JP2004522109A (en) Package bearing with lubricant inlet and outlet
US7290987B1 (en) Impeller hub for torque converter
US20030025273A1 (en) Seal and bearing assembly
EP2884122A1 (en) Thrust bearing, drive train, gear and wind generator
US12152586B2 (en) Hydraulic machine with lubricated rotating spool
CA2993290A1 (en) Modular thrust-compensating rotor assembly
US9010100B2 (en) Seal assembly for torque converter
GB2537857A (en) Thrust washer comprising a polymer running layer having a textured surface
US3804474A (en) Journal bearings
US9273730B2 (en) Non-contact split seal
US7086845B2 (en) Vane pump having an abradable coating on the rotor
RU2238425C1 (en) Hydraulic motor repair method

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20160314

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAX Request for extension of the european patent (deleted)
A4 Supplementary search report drawn up and despatched

Effective date: 20170627

RIC1 Information provided on ipc code assigned before grant

Ipc: F04D 29/10 20060101ALI20170621BHEP

Ipc: F04C 2/10 20060101ALI20170621BHEP

Ipc: F04D 29/04 20060101AFI20170621BHEP

Ipc: F04D 29/40 20060101ALI20170621BHEP

Ipc: F04D 29/046 20060101ALI20170621BHEP

Ipc: F04C 15/00 20060101ALI20170621BHEP

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20190430