EP3411588A1 - Bearing arrangement - Google Patents

Bearing arrangement

Info

Publication number
EP3411588A1
EP3411588A1 EP16705557.3A EP16705557A EP3411588A1 EP 3411588 A1 EP3411588 A1 EP 3411588A1 EP 16705557 A EP16705557 A EP 16705557A EP 3411588 A1 EP3411588 A1 EP 3411588A1
Authority
EP
European Patent Office
Prior art keywords
oil
bearing
bearing arrangement
bearing element
arrangement according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP16705557.3A
Other languages
German (de)
French (fr)
Other versions
EP3411588B1 (en
Inventor
Franco CAVRESSI
Hannu Nurmi
Jaakko ISTOLAHTI
Janne LEPPÄKANGAS
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.)
Wartsila Finland Oy
Original Assignee
Wartsila Finland Oy
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 Wartsila Finland Oy filed Critical Wartsila Finland Oy
Publication of EP3411588A1 publication Critical patent/EP3411588A1/en
Application granted granted Critical
Publication of EP3411588B1 publication Critical patent/EP3411588B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/0265—Pumps feeding common rails
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/006—Crankshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/18—Lubricating

Definitions

  • the present invention relates to a bearing arrangement for a common rail fuel injection pump of a piston engine in accordance with the preamble of claim 1 .
  • a typical high-pressure pump of a common rail fuel injection system of a large piston engine, such as a ship or a power plant engine comprises one or more reciprocating plungers, which are configured to pressurize fuel in a fluid cham- ber.
  • the plungers are moved by cams of a camshaft.
  • the camshaft is supported by lubricated plain bearings.
  • a bearing of the high-pressure pump comprises a housing and a bearing element that is arranged within the housing and comprises a sliding surface against which a journal of the camshaft rotates.
  • lubricating oil is supplied onto the sliding surface through an oil port, which is arranged in an upper part of the bearing element.
  • the oil port can be connected to another oil port via a groove, which is arranged on the sliding surface of the bearing element. Highest bearing load is experienced in a lower part of the bearing. Due to the location of the oil ports, renewing of the lubricating oil film in the most loaded area of the bearing is not effective, which increases the risk of seizure of the bearing.
  • An object of the present invention is to provide an improved bearing arrangement for a common rail fuel injection pump of a piston engine.
  • the characteriz- ing features of the bearing arrangement according to the invention are given in the characterizing part of claim 1 .
  • the bearing arrangement is configured to carry radial forces and comprises a housing, a bearing element that is arranged within the housing and provided with a sliding surface for supporting a rotating journal or shaft, at least one oil feeding port opening onto the sliding surface of the bearing element, and an oil supply bore that is arranged in the housing.
  • the bearing arrangement further comprises an oil groove that is arranged between the housing and the bearing element for establishing fluid communication between the oil supply bore and the oil feeding port.
  • the width of the oil pocket is 30- 95 % of the width of the bearing element.
  • a wide oil pocket distributes the oil film uniformly across the whole width of the sliding surface. Therefore, the width is preferably at least 60 % of the width of the sliding surface.
  • the oil groove can be arranged either in the housing or in the bearing element.
  • the arrangement comprises at least two oil feeding ports.
  • the oil can be supplied to several locations on the sliding surface, which makes the oil film more uniform.
  • the oil groove extends from the oil supply bore to both directions along the perimeter of the bearing element for connecting each of the oil feeding ports to the oil supply bore.
  • the sliding surface of the bearing element is flat outside the oil pocket(s). A maximal area of the sliding surface can thus be utilized for forming an oil film.
  • the oil groove is configured to end to an oil feeding port.
  • At least one oil feeding port is ar- ranged in a sector that extends 60 degrees to each direction from the lowermost point of the bearing element. This improves lubrication in the lower part of the bearing arrangement.
  • a high-pressure pump for a common rail fuel injection system in accordance with the invention comprises a bearing arrangement defined above.
  • At least one oil feeding port is arranged in the proximity of the area where the highest bearing load appears. Oil is thus supplied to the most loaded area of the bearing.
  • Fig. 1 shows schematically a high-pressure pump for a common rail fuel injection system
  • Fig. 2 shows a cross-sectional side view of a bearing arrangement according to an embodiment of the invention
  • Fig. 3 shows another view of the bearing arrangement of figure 2.
  • FIG 1 is shown a simplified view of a high-pressure pump of a common rail fuel injection system of a piston engine.
  • the engine where the high-pressure pump can be used is a large internal combustion engine, such as a main or an auxiliary engine of a ship or an engine that is used at a power plant for producing electricity.
  • the engine comprises a plurality of cylinders and the high- pressure pump supplies pressurized fuel to several cylinders of the engine.
  • the expression "high-pressure pump” refers here to a pump that is capable of raising the pressure of a liquid fuel, such as light fuel oil or marine diesel oil to a level that is suitable for direct fuel injection into the cylinders of the engine.
  • the pressure after the high-pressure pump can be, for instance, in the range of 500 to 3000 bar.
  • the high-pressure pump comprises two plungers 10 for pressurizing the fuel.
  • the pump could also be provided with only one plunger 10 or it could comprise more than two plungers 10.
  • Each of the plungers 10 is arranged to move in a reciprocating manner and to protrude into a fluid chamber 1 1 , where the plunger 10 pressurizes the fuel.
  • the fuel injection system where the high-pressure pump is used comprises one or more low- pressure pumps for supplying fuel to the high-pressure pump.
  • the high-pressure pump comprises a camshaft 7.
  • the camshaft 7 comprises one cam 12 for each plunger 10.
  • the plungers 10 are moved by the cams 12 in a reciprocating manner. There is a phase difference between the two plungers 10 such that when one of the plungers 10 is at top dead center, the other plunger 10 is at bottom dead center. This ensures that the output of the high-pressure pump is as constant as possible.
  • Cam followers 13 transform the rotational move- ment of the cams 12 into the reciprocating movement of the plungers 10.
  • the camshaft 7 can be driven by the crankshaft of the engine where the high- pressure pump is used. Alternatively, the camshaft 7 could be driven for example by an electric motor or a hydraulic motor.
  • the camshaft 7 of the high-pressure pump is supported by bearings that are configured to carry radial loads.
  • the camshaft 7 is supported by three bearings.
  • the minimum number of radial bearings is two, but depending on the number of the plungers 10, the high-pressure pump could also comprise more than three radial bearings.
  • the bearings of the high- pressure pump are lubricated plain bearings.
  • Each bearing comprises a hous- ing 1 and a bearing element 2 that is arranged within the housing 1 .
  • the camshaft 7 is provided with journals 6, which are arranged to rotate within the bearing elements 2. Lubricating oil is supplied between each bearing element 2 and journal 6 for forming a fluid film and minimizing friction in the rotating contact.
  • FIGs 2 and 3 show a bearing arrangement according to an embodiment of the invention.
  • the bearing arrangement can be used in the bearings of a high- pressure pump of a common rail fuel injection system.
  • the bearing arrangement comprises a housing 1 and a bearing element 2, which is arranged within the housing 1 .
  • the bearing element 2 comprises a sliding surface 3, against which a journal 6 or a shaft 7 can rotate.
  • the sliding surface 3 is thus the inner surface of an annular bearing element 2.
  • the sliding surface 3 extends over the whole inner perimeter of the bearing element 2.
  • the bearing arrangement For supplying lubricating oil between the bearing element 2 and a journal 6, the bearing arrangement comprises at least one oil feeding port 4, which opens onto the sliding surface 3 of the bearing element 2.
  • the bearing arrangement comprises three oil feeding ports 4, but the number of oil feeding ports 4 can be, for instance, between 1 and 4.
  • Each oil feeding port 4 of the bearing arrangement is surrounded by an oil pocket 9, which is arranged on the sliding surface 3 of the bearing element 2.
  • An oil pocket 9 is a recess, which is configured to hold a certain amount of oil.
  • the oil pockets 9 help to distribute the oil evenly onto the sliding surface 3.
  • the width of an oil pocket 9 is 30-95 % of the width of the bearing element 2 in the axial direction of the bearing element 2.
  • the width of the oil pocket 9 is preferably at least 60 percent of the width of the bearing element 2.
  • the length of the oil pocket 9 in the direction of the perimeter of the bearing element 2 is at most the same as the width of the oil pocket 9.
  • the oil pockets 9 are rectangular. However, the oil pockets 9 could also be for example circular or elliptical.
  • the sliding surface 3 of the bearing element 2 is flat. No recesses or grooves are thus formed outside the oil pockets 9.
  • a flat sliding surface 3 improves the thickness of the oil film and maximizes the use of the sliding surface 3.
  • the bearing arrange- ment For supplying the lubricating oil to the oil feeding ports 4, the bearing arrange- ment comprises an oil supply bore 5, which is arranged in the housing 1 of the bearing arrangement.
  • the oil supply bore 5 is arranged to supply the oil to the oil feeding ports 4 from an upper part of the bearing arrangement.
  • the oil from the oil supply bore 5 is received by an oil groove 8, which is arranged between the housing 1 and the bearing element 2.
  • the oil groove 8 is formed in the housing 1 .
  • the outer perimeter of the bearing element 2 is thus flat.
  • the oil groove 8 could also be formed in the bearing element 2, or the oil groove 8 could be partly in the housing 1 and partly in the bearing element 2.
  • the oil groove 8 is configured to establish fluid communication between the oil supply bore 5 and each of the oil feeding ports 4.
  • the oil groove 8 extends to both direc- tions along the perimeter of the bearing element 2. This ensures that even if the bearing element 2 rotates in relation to the housing 1 , oil supply to the oil feeding ports 4 is not completely cut, but lubricating oil is supplied to at least one of the oil feeding ports 4.
  • the oil groove 8 is configured such that at both ends it ends to an oil feeding port 4.
  • the oil groove 8 does thus not extend beyond those oil feeding ports 4 that are farthest from the oil supply bore 5 and it does not contain dead ends. This prevents cavitation.
  • two of the oil feeding ports 4 are located in a lower part of the bearing element 2. In a high-pressure pump of a common rail fuel injection system, this is the most loaded area of the bearings. By arranging at least one of the oil feeding ports 4 in the proximity of the area with the highest bearing load, it is ensured that this area is properly lubricated. Preferably at least one oil feeding port 4 is arranged in a sector that extends 60 degrees to each direction from the lowermost point of the bearing element 2. In the embodiment of figures 2 and 3, the oil supply bore 5 extends below the bearing element 2. This end of the oil supply bore 5 is closed by a plug 14. The plug 14 is arranged close to the bearing element 2 to minimize the volume between the oil groove 8 and the plug 14. By this way creating of an oil damper is avoided. It will be appreciated by a person skilled in the art that the invention is not limited to the embodiments described above, but may vary within the scope of the appended claims.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The bearing arrangement for a common rail fuel injec- tion pump of a piston engine is configured to carry ra- dial forces and comprises a housing (1), a bearing el- ement (2) that is arranged within the housing (1) and provided with a sliding surface (3) for supporting a ro- tating journal (6) or shaft (7), at least one oil feeding port (4) opening onto the sliding surface (3) of the bearing element (2), and an oil supply bore (5) that is arranged in the housing (1). The arrangement further comprises an oil groove (8) that is arranged between the housing (1) and the bearing element (2) for estab- lishing fluid communication between the oil supply bore (5) and the oil feeding port (4).

Description

Bearing arrangement
Technical field of the invention
The present invention relates to a bearing arrangement for a common rail fuel injection pump of a piston engine in accordance with the preamble of claim 1 .
Background of the invention
A typical high-pressure pump of a common rail fuel injection system of a large piston engine, such as a ship or a power plant engine comprises one or more reciprocating plungers, which are configured to pressurize fuel in a fluid cham- ber. The plungers are moved by cams of a camshaft. The camshaft is supported by lubricated plain bearings. A bearing of the high-pressure pump comprises a housing and a bearing element that is arranged within the housing and comprises a sliding surface against which a journal of the camshaft rotates. In a prior art solution, lubricating oil is supplied onto the sliding surface through an oil port, which is arranged in an upper part of the bearing element. The oil port can be connected to another oil port via a groove, which is arranged on the sliding surface of the bearing element. Highest bearing load is experienced in a lower part of the bearing. Due to the location of the oil ports, renewing of the lubricating oil film in the most loaded area of the bearing is not effective, which increases the risk of seizure of the bearing.
Summary of the invention
An object of the present invention is to provide an improved bearing arrangement for a common rail fuel injection pump of a piston engine. The characteriz- ing features of the bearing arrangement according to the invention are given in the characterizing part of claim 1 .
The bearing arrangement according to the invention is configured to carry radial forces and comprises a housing, a bearing element that is arranged within the housing and provided with a sliding surface for supporting a rotating journal or shaft, at least one oil feeding port opening onto the sliding surface of the bearing element, and an oil supply bore that is arranged in the housing. The bearing arrangement further comprises an oil groove that is arranged between the housing and the bearing element for establishing fluid communication between the oil supply bore and the oil feeding port. By arranging the oil groove between the housing and the bearing element, lubricating oil can be supplied to the oil feeding ports of the bearing arrangement on the rear side of the bearing element without disturbing oil film formation on the sliding surface. The sliding surface can thus be made flat, which improves the thickness of the oil film. According to an embodiment of the invention, the sliding surface of the bearing element comprises an oil pocket that is arranged around the oil feeding port. The oil pocket is a recess that is configured to hold a certain amount of oil. The oil pocket helps to distribute the oil onto the sliding surface.
According to an embodiment of the invention, the width of the oil pocket is 30- 95 % of the width of the bearing element. A wide oil pocket distributes the oil film uniformly across the whole width of the sliding surface. Therefore, the width is preferably at least 60 % of the width of the sliding surface.
The oil groove can be arranged either in the housing or in the bearing element.
According to an embodiment of the invention, the arrangement comprises at least two oil feeding ports. By providing the bearing arrangement with two or more oil feeding ports, the oil can be supplied to several locations on the sliding surface, which makes the oil film more uniform.
According to an embodiment of the invention, the oil groove extends from the oil supply bore to both directions along the perimeter of the bearing element for connecting each of the oil feeding ports to the oil supply bore. By having oil feeding ports on both sides of the oil supply bore and arranging the oil groove to extend to opposite directions from the oil supply bore, possible rotation of the bearing element in relation to the housing does not completely cut oil supply to the oil feeding ports. According to an embodiment of the invention, the sliding surface of the bearing element is flat outside the oil pocket(s). A maximal area of the sliding surface can thus be utilized for forming an oil film. According to an embodiment of the invention, the oil groove is configured to end to an oil feeding port. By ensuring that the oil groove does not contain dead ends, the risk of cavitation can be reduced.
According to an embodiment of the invention, at least one oil feeding port is ar- ranged in a sector that extends 60 degrees to each direction from the lowermost point of the bearing element. This improves lubrication in the lower part of the bearing arrangement.
A high-pressure pump for a common rail fuel injection system in accordance with the invention comprises a bearing arrangement defined above.
According to an embodiment of the invention, at least one oil feeding port is arranged in the proximity of the area where the highest bearing load appears. Oil is thus supplied to the most loaded area of the bearing.
Brief description of the drawings Embodiments of the invention are described below in more detail with reference to the accompanying drawings, in which
Fig. 1 shows schematically a high-pressure pump for a common rail fuel injection system,
Fig. 2 shows a cross-sectional side view of a bearing arrangement according to an embodiment of the invention, and
Fig. 3 shows another view of the bearing arrangement of figure 2.
Description of embodiments of the invention
In figure 1 is shown a simplified view of a high-pressure pump of a common rail fuel injection system of a piston engine. The engine where the high-pressure pump can be used is a large internal combustion engine, such as a main or an auxiliary engine of a ship or an engine that is used at a power plant for producing electricity. The engine comprises a plurality of cylinders and the high- pressure pump supplies pressurized fuel to several cylinders of the engine. The expression "high-pressure pump" refers here to a pump that is capable of raising the pressure of a liquid fuel, such as light fuel oil or marine diesel oil to a level that is suitable for direct fuel injection into the cylinders of the engine. The pressure after the high-pressure pump can be, for instance, in the range of 500 to 3000 bar.
In the example of figure 1 , the high-pressure pump comprises two plungers 10 for pressurizing the fuel. However, the pump could also be provided with only one plunger 10 or it could comprise more than two plungers 10. Each of the plungers 10 is arranged to move in a reciprocating manner and to protrude into a fluid chamber 1 1 , where the plunger 10 pressurizes the fuel. The fuel injection system where the high-pressure pump is used comprises one or more low- pressure pumps for supplying fuel to the high-pressure pump. For moving the plungers 10, the high-pressure pump comprises a camshaft 7. In the example of figure 1 , the camshaft 7 comprises one cam 12 for each plunger 10. As the camshaft 7 rotates, the plungers 10 are moved by the cams 12 in a reciprocating manner. There is a phase difference between the two plungers 10 such that when one of the plungers 10 is at top dead center, the other plunger 10 is at bottom dead center. This ensures that the output of the high-pressure pump is as constant as possible. Cam followers 13 transform the rotational move- ment of the cams 12 into the reciprocating movement of the plungers 10. The camshaft 7 can be driven by the crankshaft of the engine where the high- pressure pump is used. Alternatively, the camshaft 7 could be driven for example by an electric motor or a hydraulic motor.
The camshaft 7 of the high-pressure pump is supported by bearings that are configured to carry radial loads. In the example of figure 1 , the camshaft 7 is supported by three bearings. The minimum number of radial bearings is two, but depending on the number of the plungers 10, the high-pressure pump could also comprise more than three radial bearings. The bearings of the high- pressure pump are lubricated plain bearings. Each bearing comprises a hous- ing 1 and a bearing element 2 that is arranged within the housing 1 . The camshaft 7 is provided with journals 6, which are arranged to rotate within the bearing elements 2. Lubricating oil is supplied between each bearing element 2 and journal 6 for forming a fluid film and minimizing friction in the rotating contact. Due to the high-pressure the pump needs to produce, the load of the bearings is relatively high. The highest load occurs at the bottom of the bearings. Figures 2 and 3 show a bearing arrangement according to an embodiment of the invention. The bearing arrangement can be used in the bearings of a high- pressure pump of a common rail fuel injection system. The bearing arrangement comprises a housing 1 and a bearing element 2, which is arranged within the housing 1 . The bearing element 2 comprises a sliding surface 3, against which a journal 6 or a shaft 7 can rotate. The sliding surface 3 is thus the inner surface of an annular bearing element 2. The sliding surface 3 extends over the whole inner perimeter of the bearing element 2. For supplying lubricating oil between the bearing element 2 and a journal 6, the bearing arrangement comprises at least one oil feeding port 4, which opens onto the sliding surface 3 of the bearing element 2. In the embodiment of figures 2 and 3, the bearing arrangement comprises three oil feeding ports 4, but the number of oil feeding ports 4 can be, for instance, between 1 and 4. Each oil feeding port 4 of the bearing arrangement is surrounded by an oil pocket 9, which is arranged on the sliding surface 3 of the bearing element 2. An oil pocket 9 is a recess, which is configured to hold a certain amount of oil. The oil pockets 9 help to distribute the oil evenly onto the sliding surface 3. The width of an oil pocket 9 is 30-95 % of the width of the bearing element 2 in the axial direction of the bearing element 2. A wider oil pocket 9 distributes the oil more effectively over the whole width of the sliding surface 3. Therefore, the width of the oil pocket 9 is preferably at least 60 percent of the width of the bearing element 2. The length of the oil pocket 9 in the direction of the perimeter of the bearing element 2 is at most the same as the width of the oil pocket 9. In the embodiment of figures 2 and 3, the oil pockets 9 are rectangular. However, the oil pockets 9 could also be for example circular or elliptical. Outside the oil pockets 9, the sliding surface 3 of the bearing element 2 is flat. No recesses or grooves are thus formed outside the oil pockets 9. A flat sliding surface 3 improves the thickness of the oil film and maximizes the use of the sliding surface 3.
For supplying the lubricating oil to the oil feeding ports 4, the bearing arrange- ment comprises an oil supply bore 5, which is arranged in the housing 1 of the bearing arrangement. The oil supply bore 5 is arranged to supply the oil to the oil feeding ports 4 from an upper part of the bearing arrangement. The oil from the oil supply bore 5 is received by an oil groove 8, which is arranged between the housing 1 and the bearing element 2. In the embodiment of figures 1 and 2, the oil groove 8 is formed in the housing 1 . The outer perimeter of the bearing element 2 is thus flat. However, the oil groove 8 could also be formed in the bearing element 2, or the oil groove 8 could be partly in the housing 1 and partly in the bearing element 2. The oil groove 8 is configured to establish fluid communication between the oil supply bore 5 and each of the oil feeding ports 4. From the end of the oil supply bore 5, the oil groove 8 extends to both direc- tions along the perimeter of the bearing element 2. This ensures that even if the bearing element 2 rotates in relation to the housing 1 , oil supply to the oil feeding ports 4 is not completely cut, but lubricating oil is supplied to at least one of the oil feeding ports 4.
The oil groove 8 is configured such that at both ends it ends to an oil feeding port 4. The oil groove 8 does thus not extend beyond those oil feeding ports 4 that are farthest from the oil supply bore 5 and it does not contain dead ends. This prevents cavitation.
In the embodiment of figures 2 and 3, two of the oil feeding ports 4 are located in a lower part of the bearing element 2. In a high-pressure pump of a common rail fuel injection system, this is the most loaded area of the bearings. By arranging at least one of the oil feeding ports 4 in the proximity of the area with the highest bearing load, it is ensured that this area is properly lubricated. Preferably at least one oil feeding port 4 is arranged in a sector that extends 60 degrees to each direction from the lowermost point of the bearing element 2. In the embodiment of figures 2 and 3, the oil supply bore 5 extends below the bearing element 2. This end of the oil supply bore 5 is closed by a plug 14. The plug 14 is arranged close to the bearing element 2 to minimize the volume between the oil groove 8 and the plug 14. By this way creating of an oil damper is avoided. It will be appreciated by a person skilled in the art that the invention is not limited to the embodiments described above, but may vary within the scope of the appended claims.

Claims

Claims
1 . A bearing arrangement for a common rail fuel injection pump of a piston engine, the bearing arrangement being configured to carry radial forces and comprising
- a housing (1 ),
- a bearing element (2) that is arranged within the housing (1 ) and provided with a sliding surface (3) for supporting a rotating journal (6) or shaft (7),
- at least one oil feeding port (4) opening onto the sliding surface (3) of the bearing element (2), and
- an oil supply bore (5) that is arranged in the housing (1 ),
characterized in that the bearing arrangement comprises an oil groove (8) that is arranged between the housing (1 ) and the bearing element (2) for establishing fluid communication between the oil supply bore (5) and the oil feeding port (4).
2. A bearing arrangement according to claim 1 , wherein the sliding surface (3) of the bearing element (2) comprises an oil pocket (9) that is arranged around the oil feeding port (4).
3. A bearing arrangement according to claim 2, wherein the width of the oil pocket (9) is 30-95 % of the width of the bearing element (2).
4. A bearing arrangement according to claim 3, wherein the width of the oil pocket (9) is 60-95 % of the width of the bearing element (2).
5. A bearing arrangement according to any of the preceding claims, wherein the oil groove (8) is arranged in the housing (1 ).
6. A bearing arrangement according to any of the preceding claims, wherein the oil groove (8) is arranged in the bearing element (1 ).
7. A bearing arrangement according to any of the preceding claims, wherein the arrangement comprises at least two oil feeding ports (4).
8. A bearing arrangement according to claim 7, wherein the oil groove (8) extends from the oil supply bore (5) to both directions along the perimeter of the bearing element (2) for connecting each of the oil feeding ports (4) to the oil supply bore (5).
9. A bearing arrangement according to any of the preceding claims, wherein the sliding surface (3) of the bearing element (2) is flat outside the oil pocket(s) (9).
10. A bearing arrangement according to any of the preceding claims, wherein the oil groove (8) is configured to end to an oil feeding port (4).
1 1 . A bearing arrangement according to any of the preceding claims, wherein at least one oil feeding port (4) is arranged in a sector that extends 60 degrees to each direction from the lowermost point of the bearing element (2).
12. A high-pressure pump for a common rail fuel injection system, character- ized in that the pump comprises a bearing arrangement according to any of the preceding claims.
13. A high-pressure pump according to claim 12, wherein at least one oil feeding port (4) is arranged in the proximity of the area where the highest bearing load appears.
EP16705557.3A 2016-02-02 2016-02-02 Bearing arrangement Active EP3411588B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/FI2016/050068 WO2017134332A1 (en) 2016-02-02 2016-02-02 Bearing arrangement

Publications (2)

Publication Number Publication Date
EP3411588A1 true EP3411588A1 (en) 2018-12-12
EP3411588B1 EP3411588B1 (en) 2019-11-27

Family

ID=55404742

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Application Number Title Priority Date Filing Date
EP16705557.3A Active EP3411588B1 (en) 2016-02-02 2016-02-02 Bearing arrangement

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EP (1) EP3411588B1 (en)
KR (1) KR102097882B1 (en)
CN (1) CN108779751B (en)
WO (1) WO2017134332A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7836296B2 (en) 2020-09-10 2026-03-26 カミンズ インコーポレーテッド Fuel pump device, system, and method

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR19980052375A (en) * 1996-12-24 1998-09-25 김영귀 Lubricator of the engine camshaft
DE19953576C2 (en) * 1999-11-08 2003-06-26 Bosch Gmbh Robert bearing bush
JP4134896B2 (en) * 2003-12-15 2008-08-20 株式会社デンソー Fuel supply pump
JP2008019842A (en) * 2006-07-14 2008-01-31 Toyota Motor Corp Fuel pump support structure for internal combustion engine and pump support bracket used for the support structure
DE102007055782B4 (en) * 2007-02-06 2019-02-07 Denso Corporation Fuel supply pump with lubricant circulation device
JP4556973B2 (en) * 2007-02-06 2010-10-06 株式会社デンソー Supply pump
DE102009028795A1 (en) * 2009-08-21 2011-02-24 Robert Bosch Gmbh High-pressure fuel pump
DE102012212153A1 (en) * 2012-07-11 2014-01-16 Robert Bosch Gmbh high pressure pump
DE102014207186A1 (en) * 2014-04-15 2015-10-15 Robert Bosch Gmbh Injector
CN105351359A (en) * 2015-10-29 2016-02-24 西安交通大学 Fluid supporting tilting-pad bearing

Also Published As

Publication number Publication date
WO2017134332A1 (en) 2017-08-10
CN108779751B (en) 2020-09-08
KR20180104151A (en) 2018-09-19
KR102097882B1 (en) 2020-04-06
CN108779751A (en) 2018-11-09
EP3411588B1 (en) 2019-11-27

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