Classifications

• • 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
  • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
  • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
  • F04C15/0073—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
• • 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
  • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
  • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
• • 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
  • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
  • F04C14/02—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for several machines or pumps connected in series or in parallel
• • 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
  • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
  • F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
  • F01M1/00—Pressure lubrication
  • F01M1/02—Pressure lubrication using lubricating pumps
  • F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
  • F01M1/00—Pressure lubrication
  • F01M1/02—Pressure lubrication using lubricating pumps
  • F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
  • F01M2001/0238—Rotary pumps
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
  • F01M1/00—Pressure lubrication
  • F01M1/02—Pressure lubrication using lubricating pumps
  • F01M2001/0253—Pressure lubrication using lubricating pumps characterised by the pump driving means
• • 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
  • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
  • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
  • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
• • 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
  • F04C2270/00—Control; Monitoring or safety arrangements
  • F04C2270/19—Temperature
• • 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
  • F04C2270/00—Control; Monitoring or safety arrangements
  • F04C2270/56—Number of pump/machine units in operation

Definitions

• the invention relates to a pump arrangement, in particular for lubricating oil pumps for internal combustion engines, with at least two pump devices, wherein the pump devices can promote each other independently.
• two-stage pressure-controlled pumps are known, with two internal gear pumps operate in parallel, the second stage from a certain oil pressure (of about 3 bar) back into the intake of the pump.
• a certain oil pressure of about 3 bar
• a pump arrangement in particular for lubricating oil pumps for internal combustion engines, with at least two pump devices, which are arranged on a common drive shaft, but can independently convey, and wherein the first pump is always rotationally connected to the drive shaft, wherein the at least second pump via a temperature-dependent actuated rotary drive connection to the shaft or the rotor of the first pump is connectable.
• the inventive idea is to present an at least two-stage pump in which one stage delivers continuously and the other depending on the temperature is switched on or off to save power.
• Two fixed displacement pumps eg gerotor or external gear pumps
• the two pumps are separated.
• the idea is to connect one pump firmly to the drive shaft and the other with the help of a temperature-dependent shaft-hub connection to switch. Once the required switching temperature has been reached, the second pump stage becomes active and both volumetric flows are available to the consumer.
• An inventive pump arrangement is characterized in that the at least second pump is connected by a temperature-dependent variable actuator, in particular by a volume expansion of an actuator body at a temperature rise.
• a pump arrangement in which the actuator produces a shaft-hub connection in a force-locking manner. Furthermore, a pump arrangement is preferred in which the actuator produces a positive shaft-hub connection.
• the shaft-hub connection can thus be executed positively or non-positively. When a certain temperature is exceeded, the connection is established and released when falling below.
• Another inventive pump arrangement is characterized in that within the second pump, a first cone is arranged on the shaft and a second cone in the pump rotor hub is arranged, wherein the actuator expands axially when the temperature increases and the second cone in the axial direction against presses the first cone.
• a pump is preferred in which between the shaft and the rotor hub within the rotor hub, a cylindrical recess is arranged with two conical clamping sleeves, which move with axial expansion of the actuator against each other and cause a radial contact between the shaft and rotor hub.
• a pump arrangement is preferred in which in the second pump, the shaft has a radial recess for receiving a radially expandable actuator, which is surrounded by a slotted sleeve, so that when radially expanding the actuator, the slotted sleeve expands in its circumference and a Press connection between actuator and rotor hub manufactures.
• a pump arrangement is preferred in which on the shaft, a cylindrical annular body is arranged as an expansion element within a slotted sleeve, so that upon radial expansion of the annular body, the slotted sleeve expands in its circumference and produces a press connection between the actuator and rotor hub.
• a further pump arrangement according to the invention is characterized in that an actuator is arranged in the rotor hub, which presses a ball against a return spring in a tapered seat in the rotor hub with temperature increase, so that the ball is pressed over the conical seat against the shaft and thus a Clamping force generated between rotor hub and shaft.
• a pump arrangement is preferred in which within the second pump in a recess of the shaft radially extendable pins or elements with conical / conical ends are arranged, which are radially retractable by spring forces in the shaft, wherein by an axially within the recess of the shaft extendable actuator, which also has a tapered end which presses against the tapered ends of the pins, the elements can extend radially when deflecting the actuator by deflecting the forces at the tapered ends and engage in radial openings of the hub of the pump rotor.
• a pump arrangement in which in the second pump in an axial recess of the shaft, a cup-shaped expansion body is arranged with a conical shape with radially deflectable Spreizarmen in a conical shape, wherein the radially deflectable spreader arms through slots in the shaft in recesses of the Rotomabe can engage when an axially disposed within the recess of the shaft extendable actuator having a tapered or a spherical end, so that the radially deflectable spreader presses through the slots in the shaft in the rotor hub.
• the spreading arms move back into the shaft by their springback force.
• FIG. 1 shows a second pump with an axially acting cone connection.
• FIG. 2 shows a second pump with a radially acting conical connection.
• FIG. 3 shows a second pump with a radially acting expansion element.
• FIG. 4 shows a second pump with an annular expansion element.
• FIG. 5 shows a second pump with an expansion element in the hub.
• FIG. 6 shows a second pump with an expansion element in the shaft and radially acting pins.
• FIG. 7 shows a second pump with an expansion element in the shaft and a pot-shaped expansion body.
• FIG. 8 shows two pumps with a displaceable intermediate plate.
• the so-called second pump which is temperature-dependent connectable to the shaft, shown as a gear pump with a gear 1.
• the gear 1 is mounted on a shaft 2, which has a cone 4 at its end.
• the hub of the gear 1 has a conical end portion 6, which rests on the conical end portion 4 of the shaft 2.
• a support cap 8 is further arranged.
• a sleeve 10 is arranged, which partially surrounds an annular expansion element 12. When the temperature increases, this element 12 expands and thus frictionally jammed the gear 1 with the shaft 2.
• FIG. 2 shows a further clamping cone connection by means of an expansion element.
• a cup-shaped recess 16 is arranged within a gear 14.
• the pot-shaped recess 16 includes two conically shaped, mutually displaceable rings 18.
• a stretchable element 22 is arranged, which expands upon temperature increase and the two conical rings 18 moves against each other.
• a radial clamping force By the conical clamping rings 18 so there is a force deflection between the axially expanding expansion element 22 and the radially to be clamped parts of the gear 14 and the shaft 24 instead.
• a radially extendable expansion element 30 is arranged in a radial bore 26 of a shaft 28.
• the shaft 28 is further surrounded by a slotted sleeve 32 in the region of the expansion element 30.
• the slotted sleeve 32 is pressed against the hub of the gear 34 and thus produces a frictional connection between the expansion element 30 and thus the shaft 28 and the gear 34.
• an annular expansion element 36 is arranged in an annular recess 38 of the shaft 40.
• the expansion element 36 is in turn surrounded by a slotted clamping sleeve 42.
• the expansion element 36 arranged on the shaft 40 expands substantially radially when the temperature increases. During this expansion, it spreads the slotted sleeve 42. Again, the torque is transmitted to the gear 44 in turn by the resulting frictional force.
• a temperature-dependent actuator 46 is arranged in a recess in the hub 48 of a toothed wheel 50.
• the actuator 46 when expanded by increasing the temperature, presses a ball 52 into a conical seat 54 such that the ball 52 is pressed more firmly against the surface of the shaft 56, thus producing an increasing frictional force.
• the ball within the conical seat 54 is pushed back by a spring 58 and repealed the frictional force. Again, the actuator force is deflected by the ball and the conical seat 54.
• FIG. 6 shows a form-fitting connection with a temperature-dependent adjustable actuator.
• a temperature-controlled actuator 62 is arranged, which acts on a conical element 64 in axial expansion.
• a return spring 66 presses on cooling the conical member 64 and thus the actuator 62 back to its original position.
• the conical element 64 in turn presses on tapered ends 70 of cylindrical pins 68, which thus extend radially from the shaft 60 and retract into radial openings 74 of a gear 76 at temperature elevation.
• a positive connection between the shaft 60 and the gear 76 is produced.
• the cylindrical pins 68 are returned by return springs 72 back into the shaft.
• the springs 72 also prevent the extension of the cylindrical pins 68 by centrifugal force.
• the torque between the shaft 60 and the gear 76 is thus transmitted in this arrangement by positive engagement.
• a corresponding positive connection is produced by a so-called expansion element 78.
• a temperature-dependent expansion element 82 is arranged in a recess of a shaft 80.
• the expansion element 82 here has a spherical segment-shaped actuating body 84 which presses against spreading arms 86 of the expansion body 78 when the temperature-dependent element 82 extends under an increase in temperature.
• the spreader arms 86 are pressed through openings 88 in the shaft in recesses 90 of a gear 92 and thus take the gear 92 in the rotary motion positively.
• a return spring 94 ensures the retraction of the actuator 82 and the actuator body 84 in the cooled state, wherein the spreader arms 86 in turn spring back from the recesses 90 of the gear 92 in the shaft 80 and the frictional connection is released again due to their return spring force.
• a further possibility of coupling the second pump to the shaft could consist of a combination of a shaft-hub connection and a valve 95, as indicated in FIG.
• the separation of the two pumps 96 and 98 takes place via a loosely inserted intermediate plate 100.
• the advantage of a loosely inserted plate 100 is the improvement in volumetric efficiency due to the reduction of the gap. Due to the temperature-dependent switching of the valve 95, the disc 100 is axially displaced against the pump 98 due to the pressurization of the pressure plate 100, the suction and pressure surfaces on the side of the pump 96 are now completely under system pressure. This displacement minimizes the column of the fixed stage 98, while the overall stage 96 rotates under pressure with large gaps, without promoting and thus absorbs only minimal power.

Applications Claiming Priority (2)

Publications (2)

Family

ID=37654812

Family Applications (1)

Country Status (4)

Families Citing this family (3)

Family Cites Families (9)

• 2006
  • 2006-10-17 AT AT06805431T patent/ATE556223T1/de active
  • 2006-10-17 WO PCT/DE2006/001823 patent/WO2007048380A1/fr active Application Filing
  • 2006-10-17 EP EP06805431A patent/EP1943423B1/fr not_active Not-in-force
  • 2006-10-17 DE DE112006002561T patent/DE112006002561A5/de not_active Withdrawn

Non-Patent Citations (1)

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