EP1403531A1 - Hydraulischer Pumpenkreislauf - Google Patents

Hydraulischer Pumpenkreislauf Download PDF

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Publication number
EP1403531A1
EP1403531A1 EP20030018897 EP03018897A EP1403531A1 EP 1403531 A1 EP1403531 A1 EP 1403531A1 EP 20030018897 EP20030018897 EP 20030018897 EP 03018897 A EP03018897 A EP 03018897A EP 1403531 A1 EP1403531 A1 EP 1403531A1
Authority
EP
European Patent Office
Prior art keywords
fluid
valve
flow
hydraulic pump
passageway
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Withdrawn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
EP20030018897
Other languages
English (en)
French (fr)
Inventor
Ashraf B. Abdelrahman
Dennis H. Gibson
Joseph S. Burkitt
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.)
Caterpillar Inc
Original Assignee
Caterpillar Inc
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 Caterpillar Inc filed Critical Caterpillar Inc
Publication of EP1403531A1 publication Critical patent/EP1403531A1/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/146—Swash plates; Actuating elements
    • F04B1/148—Bearings therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • 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
    • F04B53/06—Venting
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/044—Removal or measurement of undissolved gas, e.g. de-aeration, venting or bleeding

Definitions

  • the present disclosure is directed to a circuit for a hydraulic pump and, more particularly, to a circuit for bleeding air from the inlet to a hydraulic pump.
  • Hydraulic pumps are commonly used for many purposes in many different applications.
  • Vehicles such as, for example, highway trucks and off-highway work machines, commonly include hydraulic pumps that are driven by an engine in the vehicle to generate a flow of pressurized fluid.
  • the pressurized fluid may be used for any of a number of purposes during the operation of the vehicle.
  • a highway truck for example, uses pressurized fluid to operate a fuel injection system or a braking system.
  • a work machine for example, uses pressurized fluid to propel the machine around a work site or to move a work implement.
  • a hydraulic pump typically draws operating fluid, such as, for example, oil, from a reservoir and applies work to the fluid to increase the pressure of the fluid.
  • the hydraulic pump directs the pressurized fluid into a fluid rail or another similar supply system for use during the operation of the vehicle.
  • the hydraulic pump may be configured to vary the rate at which the pressurized fluid is directed into the fluid rail. This may be accomplished with a variable displacement pump or with a fixed displacement pump that has a variable flow.
  • a hydraulic pump usually includes a pumping element that applies the work to the fluid to increase the pressure of the fluid.
  • the pumping element includes a sliding, rotating, or spinning part, such as, for example, a gear , gearotor, piston, vane, or swash plate. These moving parts are typically lubricated to prevent excessive wear due to friction.
  • the engine lubrication system in the vehicle may provide the operating fluid that is pressurized by the hydraulic pump and the lubricating fluid that is used to lubricate the moving parts of the hydraulic pump.
  • the supply of fluid may, however, also include air that is drawn into the system. This is particularly a problem when the engine is starting after having been idle for a period of time.
  • the oil in the lubrication system may drain from the system and return to the reservoir. The draining oil is replaced by air pockets, which are purged from the lubrication system when the engine is started.
  • an air bleed valve may be disposed in the outlet path of the pump. This type of valve can remove any air that is included in the flow of pressurized fluid.
  • the hydraulic pump must pressurize both the fluid and the air before the air is purged from the system through the air bleed valve. The additional work that is required to pressurized the air, which is subsequently released from the system, decreases the efficiency of the hydraulic pump.
  • the hydraulic pump circuit of the present disclosure solves one or more of the problems set forth above.
  • the present disclosure is directed to a circuit for a hydraulic pump.
  • the circuit includes a supply of fluid.
  • a pumping element is operable to increase the pressure of fluid received from the supply of fluid and to generate a flow of pressurized fluid.
  • An inlet passageway connects the pumping element with the supply of fluid.
  • a drain passageway is connected to the inlet passageway.
  • a valve is disposed in the drain passageway. The valve is moveable between a first position where the valve prevents a flow of fluid relative to the drain passageway and a second position where the valve allows a flow of fluid relative to the drain passageway.
  • the present disclosure is directed to a method of removing air from a hydraulic pump.
  • a flow of an operating fluid is supplied to an inlet passageway of the hydraulic pump.
  • a pumping element is operated to increase the pressure of the flow of fluid supplied to the pump and to generate a flow of pressurized fluid.
  • a valve is moved from a first position to a second position to allow fluid to flow from the inlet passageway to a drain passageway when the pressure of the fluid in inlet passageway is above a predetermined limit.
  • hydraulic circuit 10 includes a tank 12 that contains a supply of fluid.
  • Tank 12 may be part of a lubrication system for the vehicle, such as an oil sump.
  • the fluid within tank 12 may be a hydraulic fluid, such as, for example, a lubricating oil, although tank 12 may store other types of fluids.
  • hydraulic circuit 10 may include a supply pump 14.
  • Supply pump 14 may be a relatively low pressure pump, such as, for example, a sump pump that may be commonly included in a lubrication system to distribute oil to various systems in an engine.
  • Supply pump 14 may increase the pressure of the fluid to a relatively low pressure, such as about 70 Kpa. This relatively low pressurized fluid may then be directed into an inlet line 16.
  • Hydraulic circuit 10 may also include a high pressure pump, such as hydraulic pump 20, to further increase the pressure of the operating fluid.
  • a high pressure fluid may be required to operate certain systems.
  • the high pressure fluid may be used to operate a fuel injection system and/or a braking system.
  • the high pressure fluid may be used to operate other types of systems as well.
  • hydraulic pump 20 is depicted as a fixed displacement variable flow pump. It is contemplated, however, that hydraulic pump 20 may another type of pump.
  • hydraulic pump 20 may be a constant displacement constant flow pump or a variable displacement pump.
  • Hydraulic pump 20 includes a housing 21 and an inlet 22.
  • Inlet 22 may be connected to inlet line 16 to receive fluid from supply pump 14.
  • Inlet 22 directs the low pressure operating fluid to a pumping element 26.
  • Pumping element 26 is operable to increase the pressure of the operating fluid provided through inlet 22.
  • pumping element 26 includes a series of pistons 32 that are driven by a swashplate 28.
  • pumping element 26 may include a gear, gearotor, or vane pump.
  • an input shaft 52 is provided to drive pumping element 26.
  • Input shaft 52 is mounted for rotating movement on a bearing 50.
  • Input shaft 52 may be driven, for example, by an engine on the vehicle.
  • Input shaft 52 may include a spline or keyed end that may be operatively engaged with the crankshaft or gear train of the engine.
  • Input shaft 52 may be connected to the engine in any manner readily apparent to one skilled in the art.
  • swashplate 28 has an angled driving surface that is engaged with pistons 32.
  • the angle surface of swashplate 28 causes each piston 32 to reciprocate within a bore as swashplate 28 rotates.
  • the reciprocating movement of each piston 32 pressurizes fluid contained within the bore and supplied through inlet 22. It should be noted that the angle of swashplate 28 may be varied to vary the displacement of each piston 32 within hydraulic pump 20.
  • a pivoting shoe 30 may be disposed between each piston 32 and the angled surface of swashplate 28. Each shoe 30 rides along the surface of swashplate 28 as swashplate 28 rotates. Each shoe 30 provides a pivoting motion to accommodate for the angled surface of swashplate 28.
  • a check valve 36 may be disposed at the outlet of each bore.
  • Each check valve 36 may be configured to open when the fluid within the bore reaches a predetermined level. When pumping element pressurizes the operating fluid to the predetermined pressure, check valve 36 will open to allow the pressurized fluid to flow from the bore.
  • Hydraulic pump 20 may include a collector 38. Pressurized fluid released from each bore may be directed to collector 38. Collector 38 stores a supply of pressurized fluid that is released by pistons 32.
  • Fluid rail 19 may be configured to distribute pressurized fluid to a system, such as, for example, a fuel injection system associated with the vehicle and/or engine.
  • hydraulic pump 20 may include a control device 44 that is connected to outlet 24 through a control line 40.
  • control device 44 governs the flow rate of pressurized fluid produced by hydraulic pump 20 by controlling the position of a metering device 34.
  • control device 44 may perform any controlling function that is common in a hydraulic pump, such as, for example, displacement control, flow rate control, output pressure control, torque or horsepower control, or load control.
  • the position of metering device 34 may control the flow rate of pressurized fluid produced by each piston 32.
  • Metering device 34 may be, for example, a metering sleeve that is moveable between a first position and a second position. Movement of metering device 34 from the first position to the second position may act to decrease the flow rate of pressurized fluid generated by each piston 32.
  • drain passageway 46 may be connected to inlet 22. Drain passageway 46 may lead to bearing 50 of input shaft 52. It should be noted, however, that drain passageway 46 may lead to another bearing within hydraulic pump 20, another surface within hydraulic pump 20 that requires lubrication, directly to tank 12, or to some other desired location.
  • a valve 48 may be disposed in drain passageway 46.
  • Valve 48 has a first, or closed, position, where valve 48 prevents fluid from flowing through drain passageway 46.
  • Valve 48 also has a second, or open, position, where valve 48 allows fluid to flow through drain passageway 46. By controlling the position of valve 48, a fluid flow through drain passageway 46 may be selectively controlled.
  • Valve 48 may be, for example, a check valve, a spool, valve, or any other type of valve operable to selectively allow a flow of fluid through a fluid passageway.
  • valve 48 may be a check valve.
  • valve 48 includes a body 60.
  • Body 60 defines a valve inlet 62 and a valve outlet 64.
  • a poppet 66 is slidably disposed within body 60.
  • Poppet 66 is configured to engage a seat 70 that surrounds inlet 62.
  • a spring 68 may be disposed in housing 60 to bias poppet 66 into engagement with seat 70. The engagement of poppet 66 with seat 70 prevents fluid from flowing from valve inlet 62 to valve outlet 64.
  • Valve 48 may be disposed in drain passageway 46 so that valve inlet 62 is exposed to fluid from inlet 22. Valve inlet 62 directs this fluid against poppet 66. When the force exerted by the fluid on poppet 66 exceeds the countering force exerted by spring 68, poppet 66 will disengage from seat 70 and allow fluid to flow from valve inlet 62 through valve outlet 64.
  • Spring 68 may be selected to allow poppet 66 to disengage seat 70 when poppet 66 is subject to a fluid having a predetermined pressure.
  • spring 68 may be configured to allow poppet 66 to disengage seat 70 when the fluid has a pressure of about 70 Kpa.
  • valve 68 may be configured to open at other pressures.
  • the described hydraulic circuit 10 may be included as part of a vehicle to provide pressurized fluid to a system in the vehicle.
  • the vehicle may be, for example, a highway truck or an off-highway work machine.
  • valve 48 When the vehicle, or engine, that includes hydraulic circuit 10 is not in operation, both supply pump 14 and hydraulic pump 20 will be idle. Accordingly, the oil in inlet line 16 and inlet 22 will be at a low pressure, so that valve 48 remains closed. In the closed position, valve 48 prevents oil from draining from inlet line 16 and inlet 22 through drain passageway 46. Valve 48 will thereby preventing the formation of air pockets in hydraulic circuit 10.
  • supply pump 14 and hydraulic pump 20 When the engine of the vehicle is started, both supply pump 14 and hydraulic pump 20 will also start operating.
  • Supply pump 14 will provide a supply of relatively low pressure oil through inlet line 16 and inlet 22.
  • Pumping element 26 of hydraulic pump 20 further increases the pressure of the oil.
  • the high pressure oil is directed through outlet 24 to fluid rail 19 for use by another system in the vehicle.
  • Valve 48 may be configured to open when exposed to fluid having a pressure slightly lower than the standard output pressure of supply pump 14. Valve 48 will, therefore, open when supply pump 14 is operating normally and providing a stream of fluid at a typical output pressure. The opening of valve 48 will allow oil to flow from inlet 22 through drain passageway 46.
  • Drain passageway 46 may be connected with inlet 22 at the highest elevation in inlet 22. With this placement, the force of gravity will act on the oil to cause the oil to continue to flow through inlet 22 and to pumping element 26. Any air that is mixed with the oil supplied to hydraulic pump 20 will tend to collect adjacent to or in drain passageway 46. When valve 48 opens in response to an increase in the pressure of the supply oil, the collected air, along with some of the oil will flow through drain passageway 46.
  • Drain passageway 46 may lead to bearing 50 that supports input shaft 52.
  • the oil flowing through drain passageway 46 will lubricate bearing 50.
  • the lubrication will prevent excessive wear on input shaft 52.
  • the amount of maintenance necessary to keep hydraulic pump 20 operational may be reduced.
  • the foregoing disclosure provides a hydraulic circuit 10 for a hydraulic pump 20 that allows for the removal of air at the inlet to the hydraulic pump 20 and may be used to lubricate the moving parts of the hydraulic pump 20. By removing the air before the air is pressurized by the pumping element 26, the efficiency of the hydraulic pump 20 may be increased.
  • the described hydraulic circuit 10 may prevent the formation of air pockets in the flow of pressurized fluid that is used to operate an auxiliary system on the vehicle, such as, for example, a fuel injection system.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP20030018897 2002-09-25 2003-08-20 Hydraulischer Pumpenkreislauf Withdrawn EP1403531A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US253973 1994-06-03
US10/253,973 US20040057836A1 (en) 2002-09-25 2002-09-25 Hydraulic pump circuit

Publications (1)

Publication Number Publication Date
EP1403531A1 true EP1403531A1 (de) 2004-03-31

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ID=31977813

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20030018897 Withdrawn EP1403531A1 (de) 2002-09-25 2003-08-20 Hydraulischer Pumpenkreislauf

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US (1) US20040057836A1 (de)
EP (1) EP1403531A1 (de)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102705191B (zh) * 2012-06-01 2015-09-23 沈如华 调色机的色浆定量供应装置
FR2992034B1 (fr) * 2012-06-14 2014-07-18 Hydro Leduc Pompe hydraulique a pistons axiaux pouvant fonctionner dans les deux sens

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US1972560A (en) * 1931-11-26 1934-09-04 Heller Ernst Machine tool feeding means
GB957528A (en) * 1959-12-04 1964-05-06 Eckerle Otto Pumping system
US3973398A (en) * 1975-09-12 1976-08-10 Deere & Company Hydraulic system and automatically shiftable direction control valve therefor
US5253988A (en) * 1991-02-27 1993-10-19 Maag Pump Systems Ag Gear pump
GB2297128A (en) * 1994-12-01 1996-07-24 Sauer Sundstrand Ltd Closed centre hydraulic system
JPH09236082A (ja) * 1996-02-29 1997-09-09 Unisia Jecs Corp 液体ポンプ
US20020034448A1 (en) * 1999-11-30 2002-03-21 De Matthaeis Sisto Luigi Valve system for controlling the fuel intake pressure in a high-pressure pump
US20020078928A1 (en) * 2000-12-27 2002-06-27 Mitsubishi Denki Kabushiki Kaisha Variable delivery type fuel supply apparatus

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Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1972560A (en) * 1931-11-26 1934-09-04 Heller Ernst Machine tool feeding means
GB957528A (en) * 1959-12-04 1964-05-06 Eckerle Otto Pumping system
US3973398A (en) * 1975-09-12 1976-08-10 Deere & Company Hydraulic system and automatically shiftable direction control valve therefor
US5253988A (en) * 1991-02-27 1993-10-19 Maag Pump Systems Ag Gear pump
GB2297128A (en) * 1994-12-01 1996-07-24 Sauer Sundstrand Ltd Closed centre hydraulic system
JPH09236082A (ja) * 1996-02-29 1997-09-09 Unisia Jecs Corp 液体ポンプ
US20020034448A1 (en) * 1999-11-30 2002-03-21 De Matthaeis Sisto Luigi Valve system for controlling the fuel intake pressure in a high-pressure pump
US20020078928A1 (en) * 2000-12-27 2002-06-27 Mitsubishi Denki Kabushiki Kaisha Variable delivery type fuel supply apparatus

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 1998, no. 01 30 January 1998 (1998-01-30) *

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