WO2006066678A1 - Unite de lubrification haute pression autonome - Google Patents

Unite de lubrification haute pression autonome Download PDF

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Publication number
WO2006066678A1
WO2006066678A1 PCT/EP2005/012485 EP2005012485W WO2006066678A1 WO 2006066678 A1 WO2006066678 A1 WO 2006066678A1 EP 2005012485 W EP2005012485 W EP 2005012485W WO 2006066678 A1 WO2006066678 A1 WO 2006066678A1
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WO
WIPO (PCT)
Prior art keywords
pressure
lubrication unit
unit
battery module
pressure lubrication
Prior art date
Application number
PCT/EP2005/012485
Other languages
German (de)
English (en)
Inventor
Michael Przybylsky
Original Assignee
Willy Vogel Ag
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 Willy Vogel Ag filed Critical Willy Vogel Ag
Publication of WO2006066678A1 publication Critical patent/WO2006066678A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N13/00—Lubricating-pumps
    • F16N13/02—Lubricating-pumps with reciprocating piston

Definitions

  • the invention relates to a self-sufficient, electrically driven high-pressure lubrication unit for an autonomous central lubrication system for generating a lubricating pressure by which at least one lubrication point can be supplied with lubricant, with at least one pump piston which is arranged to be movable back and forth in a pump cylinder, with an electric motor drive , which is connected via a drive train with reduction gear to the pump piston, and with at least one battery module, which is connected as an electrical energy source with the electromotor drive see.
  • the invention further relates to a method for generating a lubricating pressure, wherein an electromotive drive is driven by the electrical energy of a battery module and generates the lubricating pressure.
  • DE 92 14 096 U1 an automatic lubricant dispenser with a battery-powered motor is known, which drives a rotary shaft with an external thread via a reduction gear. By the rotation of the rotary shaft, a piston with a piston rod, which has a threaded bore, pressed down, whereby lubricant is pressed from a lubricant container through an outlet opening.
  • the lubricant dispenser of DE 92 14 096 U1 is able to provide a lubrication point with lubricant, even if no electrical energy source, such as a central power grid or a car battery, is present in the vicinity of the lubrication point.
  • the device of DE 92 14 096 U1 respect lent manufacture and maintenance should be improved.
  • DE 102 34 881 A1 A device that discharges a metered amount of lubricant with greater pressure is described in DE 102 34 881 A1.
  • the lubricant is first pumped from a reservoir by means of an actuating piston through a passage in the threaded rod of the actuating piston in an axial bore of a plunger.
  • the plunger is arranged in extension to the threaded rod.
  • the drive of DE 102 34 881 A1 contains a motor-driven, coaxial with the plunger surrounding drive shaft with a control surface. The drive firstly moves the actuator piston and secondly generates a stroke movement of the plunger.
  • the control surface of the shaft and a plunger head are provided with complementary sliding surfaces at their contact surfaces. Since the plunger or the plunger head are mounted in a torsionally rigid manner, the rotation of the drive shaft produces a stroke movement of the plunger, whereby the lubricant is pressed out of the axial bore of the plunger with a delivery pressure through an outlet opening on the plunger end.
  • the delivery pressure of the lubricating device of DE 102 34 881 A1 due to the energy losses caused by the friction on the contact surfaces of the control surface and plunger head, not sufficient to operate passive pressure actuated distributor with the generated lubrication pressure.
  • a distributor device in which a hollow manifold body is rotatably disposed in a fixed distribution sleeve.
  • the hollow distributor body is sealingly received in the distributor sleeve, so that the lubricant is passed through staggered radial distribution bores in the body.
  • the distributor device of EP 1 418 379 A2 requires that the distributor device be connected to a voltage supply which provides the energy for the active induced rotation of the distributor body.
  • the distributor device of EP 1 418 379 A2 is not a passive distributor, which is only operated by the lubricating pressure of the lubricating unit.
  • the object of the present invention is therefore to provide a high-pressure lubrication unit which is easy to maintain and to monitor, which is able to operate a large number of lubrication points of a centralized lubrication system, which are usually far apart, with passive progressive dividers.
  • the object is achieved in that the lubricating unit is frictionally reduced by the drive train is provided with Wälzippoffenn, and that the lubricating pressure generated in operation by the high-pressure lubricating unit at least corresponds to the driving pressure of a passive Progressionneilers.
  • the object is achieved in that the friction on the drive train is reduced by Wälzromeffen and such a high lubricating pressure is generated that passive Progressionneiler can be operated.
  • roller contact means of the drive train reduce the frictional losses, which, for example, in the device of DE 102 34 881 A1 at the contact surface between drive shaft and shock absorber. are particularly high, so that the energy of the battery module, such as a primary battery, a rechargeable battery or a fuel cell, sufficient to produce very high lubrication pressures above 50 bar.
  • the battery module such as a primary battery, a rechargeable battery or a fuel cell
  • the solution according to the invention offers the advantage of a reliable lubrication system which can also be used where no voltage supply has hitherto been provided or where the costs and the outlay for the connection to existing power supplies are too high.
  • autarkic high-pressure lubrication unit can be further developed by means of different, mutually independent, respectively advantageous embodiments.
  • rolling bearings can be arranged as Wälzromekar on the drive train. This has the advantage that the friction losses compared to the common slide-mounted constructions are significantly reduced. In this way, the efficiency of the high-pressure lubricating unit increases, whereby it is possible to convert the limited, provided by the battery module electrical energy into very high lubrication pressures.
  • the rolling bearings can be arranged at any point of the drive train.
  • the rolling contact means can be arranged in the force flow of the piston forces.
  • the rolling contact means are arranged directly at the points where the highest frictional forces or friction moments and thus also the largest energy losses occur.
  • Lifting element is understood to mean a component that converts the rotation of a shaft into a lifting movement of a piston, such as a cam disc, a swash plate or an eccentric.
  • the lifting element can be shaped on a contact surface which is in communication with the pump piston such that during the pressure stroke, a rotational speed of the lifting element can be converted into a substantially constant stroke speed of the pump piston.
  • the contact surface in a radial pump design as a Nooke or in an axial pump design as a plane which is inclined with respect to the axis of rotation of the output spindle may be formed.
  • the friction radius i. the distance between the axis of rotation of the lifting element and the contact point of the lifting element and the pump piston should be small, so that the resulting friction torque is minimized.
  • the pump piston can be arranged substantially parallel to the axis of the spindle of the drive train.
  • This Axialbauweise shows over the more common radial design with eccentric as a lifting means improved efficiency.
  • the pump piston is arranged axially parallel to the spindle, so very high lubrication pressures can be generated.
  • the The high-pressure lubrication unit according to the invention can also be designed with a pump piston arranged substantially radially to the spindle of the drive train. It is possible that a roller bearing is arranged on the circumference of the lifting element, in this case, for example, an eccentric to reduce the friction reduction.
  • the eccentric may have a deviating from the usual circular cross-section, for example in cam shape, which allows during the compression stroke to the rotational speed of the cam constant stroke speed of the piston and thus a uniform torque.
  • An additional advantage of the Axialbauweise is that the pump piston, and thus also the lubrication unit, in the radial direction with respect to the spindle of the drive train requires less space. If the high-pressure lubricating unit is equipped with a lubricant reservoir with stirrer, so the diameter of the stirrer can be reduced. A reduced stirrer diameter means a reduction in the required drive torque for the stirrer, which also goes in favor of the efficiency and efficiency of the lubricating unit.
  • a further reduction of the stirrer diameter can be achieved by arranging a pressure spring acted upon piston at the interface between lubricant and air in a lubricant reservoir of the lubricating unit.
  • the reduction gear of the drive train may preferably be designed as a planetary, helical or bevel gear, because these gears show improved efficiency compared to the otherwise conventional worm gear.
  • the reduction gear can have a longer reduction than 300: 1.
  • the higher gear reduction leads to a reduced spindle speed, to a lower drive torque of the engine at a certain engine speed.
  • the high-pressure lubrication unit can be optimized for application with lower power or power requirement via the reduction ratio of the transmission.
  • At least one passive progressive distributor module can be connected to the pump cylinder and with the lubricating pressure a passive distributor module can be operated which supplies lubricant to at least two lubrication points, preferably at least seven lubrication points.
  • a plurality of passive distributor modules can be arranged one after the other or next to one another, which can be indirectly connected directly or via secondary lines of passive distributor modules to the pump cylinder and operated with the lubricant pressure of the high-pressure lubricant unit.
  • a lubricating pressure of at least 250 bar can be produced. Namely, at low temperatures, the viscosity of the lubricant increases and higher lubricating pressures are necessary so that a reliable lubrication is ensured even in the deteriorated flow behavior of the lubricant. In general, the higher the maximum producible pressure of a pump, the lower the lower operating limit temperature.
  • progressive dividers which consist of modular distributor subassemblies
  • the subunits with differently sized, variably adjustable distributor spaces can form the progressive distributor and operate with the high-pressure lubricating unit according to the invention.
  • metered distributors which transport different amounts of lubricant through the branch lines branching off from the distributor.
  • Cycle sensor can be arranged in the Progressivererteilermodul and connected to the battery module.
  • the cycle sensor may be an inductance switch which can be installed as a modular subunit in the progressiv divider and can be operated by it. In this way, the complete lubrication process can be monitored at a central point, namely the distributor module.
  • mechanical or magnetic (reed) switches can be used.
  • the discharged battery module may generate a discharge voltage required to operate the cycle sensor.
  • the cycle sensor can also work on a discharged battery module and specify at least one error message. This can be achieved simply by the fact that the discharge voltage of the battery module at least one operating voltage of the cycle sensor equivalent.
  • the discharge voltage ie the residual voltage in the case of empty batteries, is about 0.9 volts per cell for a commercial alkaline cell, for example.
  • the battery module may comprise series-connected or series-connected and parallel-connected battery cells.
  • the battery module may generate at least one standardized output voltage that is used to power all the electrically driven components of the high pressure lubrication assembly.
  • the output voltage is thus an integer multiple of the basic voltage of a single battery cell, and the discharge voltage of the battery module is the sum of the discharge voltages of all series-connected battery cells.
  • the energy source has at least 7 battery cells, preferably 12 battery cells.
  • the high pressure lubricating unit may have a receiving slot for the battery module.
  • the receiving shaft should be in one of be located outside easily accessible location, so that a simple replacement of the battery module is possible.
  • the battery module can also be mounted in or on the outside of the housing of the high pressure lubrication unit.
  • it makes sense to design or attach to the housing of the high-pressure lubricating unit fastening means, via which the battery module is repeatedly releasably secured to the housing.
  • solar moduls which are composed of a plurality of stacked solar cell layers and absorb light of different wavelengths. In this way, a broader wavelength range of sunlight can be absorbed by the solar module and used to drive the high-pressure lubricating unit.
  • solar modules with a textured surface which is for example occupied by micro-pyramids, can be used.
  • the solar cells can be coated for example with a coating of titanium oxide, which causes a self-cleaning effect in conjunction with Lichteinstrahfung.
  • the embodiments of the solar module thus make it possible, on the one hand, for solar cells with a smaller area to be used, which can be mounted more easily on the lubricating unit and have a reduced space requirement.
  • the lubricating pressure is generated intermittently.
  • the energy storage can be charged during the long rest phase of the high-pressure lubricating unit and deliver the required output voltage to the components of the high-pressure lubricating unit to be supplied electrically in the short lubrication pressure-generating lubrication phase.
  • an intermittent mode of operation of the high-pressure lubricant unit causes the capacity of the battery module in ampere hours to drive the high-pressure lubricant unit over a longer period of time.
  • a motor with an operating voltage of less than 12 volts, of 6 volts can be used and the number of windings of the motor can be applied to a particularly low rated current in order to reduce the power requirement of the motor.
  • a control module may be connected to the battery module, by which the high-pressure lubricating unit from the lubrication state, in which lubrication pressure is generated, is designed to switch to a rest state.
  • the drive motor is only selectively switched on in precisely defined, temporally spaced, short lubrication phases, since the engine requires a lot of energy. Only the control module has to be supplied with energy essentially without interruption by the operating module.
  • an energy-saving control module controls the lubrication phases and resting phases of the unit.
  • the display of the control module can only be operated periodically.
  • the display can have energy-saving LEDs, which also only flash or only light up at the touch of a button.
  • control module can be reduced by the control module having a processor with a low quiescent current consumption, for example less than 300 ⁇ A, preferably 200 ⁇ A.
  • control module can be configured according to a further advantageous embodiment with a regulated switching power supply for controlling the operating voltage of the high-pressure lubricating unit.
  • a regulated switching power supply for controlling the operating voltage of the high-pressure lubricating unit.
  • long lubrication phases can be divided into individual intervals, which are interrupted by pauses in which the battery module can regenerate. This procedure is particularly advantageous at low ambient temperatures.
  • the control module can be data-transmitting connected to an operating sensor which is arranged at a point to be lubricated and by which a request signal can be output to the control module.
  • the operating sensor senses the lubrication state of the friction point and signals the control module when to initiate a lubrication cycle.
  • the lubrication phases of the high-pressure lubricating unit can be controlled in dependence on a lubrication signal indicating the lubricant requirement.
  • the data transmission between the control module and the cycle or operating sensors can also be done wirelessly, eg with 2.4 GHz ISM, by radio or blue tooth.
  • special sensors should be used, which receive their supply voltage via a magnetic field, which is for example generated centrally from the power supply of the machine by a transformer with, for example 120 KHz, and in particular designed for a lower power consumption.
  • control module can be configured with an electrical switching element, for example a current regulator, for controlling the drive motor and for setting the drive rotational speed.
  • an electrical switching element for example a current regulator, for controlling the drive motor and for setting the drive rotational speed.
  • the current is limited to the drive motor, and it is possible to adjust the speed via a voltage adjustment to the required load. This allows a load-independent, constant flow rate.
  • electronic switches have a lower energy consumption than the usual electromechanical relays, which extends the operating life of the battery module.
  • the high-pressure lubrication unit can have an operating voltage that corresponds to the output voltage of the operating module at a lower operating limit temperature.
  • This lower operating temperature can be in particular at -10 0 C.
  • the capacity or power and in particular the generated current of battery cells varies depending on the operating temperature, so that at low temperatures only a small amount of power can be supplied by the battery module.
  • an energy amplifier which is connected from a charged state by being charged to the power source is, in a dispensing state in which it is designed to be reversible connected to the drive, this is supplied with energy.
  • the power amplifier such as an accumulator or a capacitor, from the power source in the idle state of the high-pressure lubricating unit will be slowly charged, and in the lubricating state to release the stored energy within the short lubrication cycle and to operate the high-pressure lubrication unit for a short time with very high power.
  • FIG. 1 shows a first embodiment of the high-pressure Schmieraggre- gates invention with a Progressionneiler.
  • FIG. 2 shows an enlarged detail of FIG. 1, which represents an embodiment of a drive train according to the invention with rolling contact means between the lifting element and the pump piston;
  • Fig. 3 shows another embodiment of the invention high-pressure lubricating unit with a reservoir and a solar battery.
  • the high-pressure lubricating unit 1 comprises a battery module 2, which is housed in a readily accessible from the outside of the battery compartment 3 within the housing 12 of the high-pressure lubricating unit 1.
  • the battery module 2 contains a plurality of, for example seven, series-connected battery cells 4 and is fixed in position by a cover 5 which closes the battery compartment 4.
  • the battery module 2 or the battery cells 4 may also be attached to the lid, so that the battery is removed with removal of the lid 5 from the compartment.
  • the battery module 2 supplies both a modular control unit 6 with a control element 7 and a display 8 and an electric motor 9 with electrical energy.
  • 9 electrical lines 10a and 10b are mounted between battery module 2 and control unit 6 and electric motor.
  • the motor-carrying line 10b is interrupted at one point by a switch 11, with the switch 11 under the control of the control module 6, so that the control module 6 determines when the motor 9 is powered and powered by the battery module 2.
  • control unit 6 is positioned so that the display 8 outside the housing 12 of the high pressure lubricating unit 1 clearly visible and the buttons and switches of the control element 7 are easily accessible.
  • the drive train of the high-pressure lubricating unit which converts the mechanical energy of the battery module 2 into a hydraulic lubrication pressure P s , contains the electric motor 9, a reduction gear 13 with a drive pinion 14, an output spindle 15, a torsionally rigid mounted on the output spindle 15 output gear 16 and a Cam 20 and finally a pump element 21.
  • the pump element 21 is disposed in a pump chamber 19 which is located within the unit housing 12, and generates the hydraulic lubrication pressure P s -
  • the electric motor 9 with the transmission gear 13 connected thereto is shown only schematically.
  • the reduction gear 12 is indicated in Fig. 1 as a spur gear, but may also be a planetary or bevel gear.
  • the output spindle 15 extends from one end of the housing 12 to the opposite end, which ends within the pump chamber 19, which lies in Fig. 1 next to the battery compartment 4.
  • the output spindle 15 is rotatably disposed within the lubricating unit 1 by means of three radial ball bearings. Two of the bearings 18 are mounted within the pump chamber 19, another ball bearing 17 is located at the other end of the output shaft 15th
  • the ball bearings 17 and 18 are shown only schematically in FIG. 1 and are intended to make clear that the output spindle 15 is provided with antifriction bearings in a friction-reducing manner. Exact structural details, for example, how the attachment of the ball bearings 17 and 18 is realized on the walls of the housing 12 and 19, is not shown in detail.
  • the cam 20 is configured with a circumferential guide groove 26, which extends as a screw once completely around the circumference of the cam 20.
  • a pump element 21 is likewise accommodated, which comprises a pump piston 22, a pump cylinder 23 and a check valve 24.
  • the pump piston 22 is accommodated precisely and sealingly within the pump cylinder 23, whereby a pump space 25 is formed between the check valve 24 and the one end of the pump piston 23 whose volume changes in dependence on the position of the pump piston 22.
  • the other end of the pump piston 22 projects out of the pump cylinder 23 and is provided with a piston head 27 which has a larger diameter than the otherwise cylindrical pump piston body.
  • the pump element 21 is arranged axially parallel to the output spindle 16, so that a rotation of the cam 20 generates a stroke movement of the pump piston 22.
  • the lifting movement moves the piston 22 back and forth between a delivery position in which the volume of the pump chamber 25 is minimal and a starting position in which the pump chamber 25 has maximum volume.
  • the lubricant in the pump chamber 22 is pressed out of the pump element 21 and the lubricating unit 1 with a lubricating pressure P s through the check valve 24, which is opened due to the lubricating pressure Ps.
  • a lubricant line 29 is disposed within the high pressure lubricating unit 1, which connects the pump chamber 25 and the borehole 28 with a reservoir (not shown in Fig. 1).
  • the return valve 24 is disposed at the end of the pump cylinder 23, which defines the pump chamber 25 and which forms a lubricating opening in the housing wall 12 of the high pressure lubricating unit 1, which is occupied by the return valve 24. In this way, lubricant can be discharged from the pump chamber 25 through the check valve 24 in a main line 30 when the pump element 23 generates the lubrication pressure Ps.
  • the main line 30 is screwed with a fastening nut 31 to the lubricating unit 1 and the lubricant-dispensing end of the pump cylinder 23.
  • Lubricant with the lubricant pressure P s is conveyed through the main line 30 to a pressure distributor 32, into which the lubricant is introduced at a drive pressure P A which essentially corresponds to the lubricant pressure P s .
  • the passive progressive distributor module is thus actuated only by the lubrication pressure Ps as the drive pressure P A.
  • the manifold module 32 has four manifold subassemblies 33 each dividing the lubricant into two sublines 34. Furthermore, the distribution module 32 has a cycle switch 35 as a further subunit, which is mounted farthest from the mouth of the main line 30 and also from the Lubrication pressure P s is actuated. However, the cycle switch 35 is not required for the operability of the high-pressure lubricating unit 1, but represents an optional additional component.
  • the cycle switch 35 is connected via an electrical line 36 to 36 'to the battery module 2 and is thus supplied by the battery module 2 with a required operating voltage Uz.
  • the cycle switch 35 is data transmitting connected via a data line 37 to 37 'to the control module 6 and can report a faulty lubrication to the control unit 6, which is made visible to the user in the display 8 or displayed by an audible signal in good audible frequency. In order to minimize the energy requirement of the error message, it makes sense to output an intermittent signal.
  • a control unit can also specify an error signal directly to a central computer.
  • the battery module 2 of Fig. 1 is designed so that even when discharged state, a discharge voltage U E is available, which is at least as large as the operating voltage U 2 and guaranteed at any time.
  • the cycle switch 35 is capable of outputting at least one error message to the control unit 6 in order to be able to carry out countermeasures as quickly as possible, for example refilling lubricant into the reservoir or replacing the battery cells K of the battery module 2.
  • FIG. 2 shows an enlarged detail of the pump chamber 25 with the contact point of the drive train between the pump element 21 and the cam disc 20, which is mounted in a torsionally rigid manner on the output spindle 15.
  • FIG. 2 shows an enlarged detail of the pump chamber 25 with the contact point of the drive train between the pump element 21 and the cam disc 20, which is mounted in a torsionally rigid manner on the output spindle 15.
  • FIG. 2 shows an enlarged detail of the pump chamber 25 with the contact point of the drive train between the pump element 21 and the cam disc 20, which is mounted in a torsionally rigid manner on the output spindle 15.
  • FIG. 2 In contrast to the embodiment of Fig. 1, a high-pressure lubricating unit 1 is shown in FIG. 2, in which with a cam 20, two pump elements 21 and 21 'are actuated.
  • Fig. 2 shows that the output spindle 15 is mounted with roller bearings 18 on the housing wall 38 of the pump chamber 19.
  • the inner, lying on the operating spindle 15 ring of the roller bearing 18 is fixed from one side with a mounting ring 39 and from the other side via a mounting shoulder 40 of the cam 20.
  • the cam 20 operates two pump elements 21 and 21 * on. This has the advantage that per revolution of the cam 20, two pump strokes occur. In this way, either twice the amount of lubricant can be promoted or a second lubrication circuit can be supplied with other requirements, such as a different lubricant quantity or type.
  • the return movement of the pump piston 22 from the discharge to the starting position is effected by the second support shoulder 44 of the cam 20, which is arranged closer to the pump cylinder 23, on the inner head surface 45 of the pump piston 22, which faces in the direction of the pump cylinder 23, a force exerts axially to the drive spindle axis.
  • these elements are geometrically shaped and kinematically arranged in a particularly favorable manner.
  • the two top surfaces 43 and 45 of the pump piston 22 are rounded at the outside at their contact edges.
  • the support tabs 42 and 44 of the cam 20 are not arranged in a plane perpendicular to the axis of the spindle 15, but they are slightly inclined at their outer edges, against their respective axial power transmission direction H. In Fig. 2, this means concretely that the first support shoulder 42 is slightly tilted toward the edge in the direction of the return movement, whereas the second support shoulder 44 is always slightly inclined at the edge in the lubrication direction.
  • the support tabs 42 and 44 for the piston head 27 always form a kind of rotatable, slated plane on which the curved piston head 27 moves in a rotating manner. Due to the thus formed contact surfaces between cam 20 and pump body 22, the cam 20 transmits not only the axial force for generating the stroke H to the pump piston 22nd
  • the special embodiment transmits, in addition to the stroke H, a rotation R from the cam 20 to the complete pump piston 22, since the piston head 27 rolls on the skewed flat support shoulders 42 and 44 with its rounded head surfaces 43 and 45.
  • the pump pistons 22 rotate in a rotational direction R ', which is opposite to the rotation of the output shaft.
  • the friction or the friction torque between the piston 22 and cam 20 is greatly reduced, whereby the high pressures of the self-propelled high-pressure pump 1 according to the invention are even possible.
  • the reduction in friction of the embodiment according to the invention is particularly noticeable on the support shoulder 42, which is in contact with the outer head surface 43 during the pressure-transmitting stroke movement.
  • the return of the pump piston or 22 can also be solved by means of Federschreib- position. Then the support shoulder 44 eliminates the cam, which reduces the manufacturing cost.
  • the frictional torque on the support of the spring can be reduced by transmitting the spring force to the piston through a sliding disk, wherein a shoulder on the sliding disk or the pump piston 22 minimizes the friction radius.
  • FIG. 3 shows a further embodiment of the high pressure lubricating unit 1 according to the invention.
  • the same reference numerals are used as in the preceding embodiments. For the sake of clarity, only the differences from the embodiment of FIG. 1 will be discussed below.
  • the battery compartment 3 is not arranged inside the housing 12 of the lubricating unit 1, but is attached to the housing 12 from outside via fastening means 49.
  • the control module 6 as well as portions of the lubricant line 29 and the output spindle 15 of all components of the high pressure lubricating unit 1 have been omitted.
  • a modular reservoir 46 with an agitator 57 which represents an optional component of the lubricating unit and can be embodied, for example, as a replaceable cartridge, is shown.
  • the battery compartment 3 has a fastening shoulder 47, which projects beyond the lateral edge of the battery compartment 3, and in which fastening holes 48 are formed. Through the mounting holes 48 fasteners, in Fig. 3, for example, screws 49, pushed, with which the battery compartment 3 is attached to the housing 11.
  • the housing 12 has screw holes 50 with an internal thread for the fastening screw 49 for this purpose.
  • the fastening form shown in Fig. 3 is only an example, and can be arbitrarily replaced by an alternative, releasable fastening means, such as clips or hooks.
  • the battery module 2 of FIG. 3 is designed as a rechargeable accumulator, which is connected via an electrical line 52, for example a cable, to a solar cell 51 and can be charged by it.
  • the solar cell 51 converts sunlight S into electrical energy, which is then stored in the battery module 3.
  • it is necessary that the solar cell 51 is attached to an outwardly exposed point of the high pressure lubricating unit 1 or in its immediate vicinity.
  • the solar cell 51 is mounted on the reservoir 46.
  • the solar module 51 can be attached via a holder or attachment at any other point on the lubricating unit 1, or in the vicinity thereof. It is also possible to integrate the solar cell 51 into the outer contour of the pump 1 by, for example, producing the solar module 51 by direct deposition of silicon on a part of the housing surface 12.
  • the embodiment of FIG. 3 furthermore has a charge controller 53, which controls the charging phase and the discharge phase of the rechargeable battery 2 in time.
  • the charge controller 53 is attached to the solar module 51, for example.
  • the charge controller 53 may also be located at any other point of the housing 12 of the high pressure lubrication unit 1 or be designed integrated into the control device 6.
  • the battery battery module 2 briefly deliver very high power to the drive motor 9 during the short lubrication phases, whereby the high pressure lubrication unit 1 generates very high pressures Ps in the lubrication phase.
  • the recharging of the rechargeable battery 2 takes place, so that it can again provide a sufficient amount of electrical energy in the next lubrication phase.
  • this principle can only be usefully operated if the energy fed into the battery module 2 during the charging phase is greater than or at least equal to the energy removed during the lubricating phase.
  • lubricant 55 reservoir 46 is shown, which is provided with a stirrer 57 and is placed on the high-pressure lubricating unit 1.
  • a stirring spindle 58 is further arranged, which is arranged in extension of the output spindle 15 of the high-pressure lubricating unit 1 and is rotationally rigidly connected to the output spindle 15.
  • a nose 59 engages the Rlickwerkesspindel 58 at the junction in a complementary to the nose 59 shaped recess 60 of the output spindle 15. Through this engagement of nose 59 and groove 60, the spindle 15 transmits its rotation R on the agitator spindle.
  • a stirring means 61 is fixed in a rotationally fixed manner near the bottom of the storage container 2, which serves to mix the lubricant well and to reduce the viscosity of the lubricant 55.
  • the stirring means 61 is shown schematically in FIG. 1 as a propeller stirrer. However, it is also possible to use any other type of stirrer, such as, for example, inclined blade, disc or helical stirrers.
  • a Ab- Streifkolben 62 which is located at the interface between filled with lubricant 55 and already emptied and filled with air area.
  • the stripping piston 62 serves to strip the lubricant 55 remaining on the wall of the reservoir 46 downward.
  • the stripping is done by lateral consumers, which are connected to the agitator 57, whereby, however, the diameter and the torque of the agitator 57 and thus the energy consumption for a self-sufficient, battery-operated high-pressure lubricating unit 1 would be too high.
  • the stripping piston 62 is pressed by a compression spring 63 in the direction of the bottom of the reservoir 46.
  • the stripping piston 62 is moved upward against the spring force of the pressure spring 63, so that the energy stored in the deformation of the compression spring 63 is released slowly over a long period of time for actuating the stripping piston 63, without access the limited capacity of the battery module 2.
  • the illustrated embodiments of the high-pressure lubricating unit 1 represent only individual, concrete designs whose exemplary description does not limit the scope of the high-pressure lubricating unit 1 according to the invention or of the method according to the invention.
  • the arrangements of the individual components or supplementary modules of the unit 1 are merely exemplary and can be replaced as desired.
  • the illustrated embodiment of the high-pressure lubricating unit in axial arrangement tion to the output spindle 15 only a preferred embodiment and can also be replaced by a radially arranged to the output spindle 15 pump elements 21, which are driven by a rotating rigidly mounted on the output spindle 15 eccentric.

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Abstract

L'invention concerne une unité de lubrification haute pression autonome à entraînement électrique (1) conçue pour une installation de lubrification centrale autonome, destinée à générer une pression de lubrification permettant d'alimenter au moins un point de lubrification en substance lubrifiante. L'unité de lubrification haute pression comprend au moins un piston plongeur (22) qui est disposé dans un cylindre de pompe (23) de manière à pouvoir effectuer un mouvement de va-et-vient, un entraînement électromoteur (9) qui est relié avec le piston plongeur (22) par l'intermédiaire d'une chaîne cinématique comportant un mécanisme démultiplicateur (13), et au moins un module de batterie (2) qui est relié à l'entraînement électromoteur en tant que source d'énergie électrique. L'objectif de cette invention est de créer une unité de lubrification haute pression (1) facile à entretenir et à inspecter, qui peut faire fonctionner, de manière autonome et efficace, une installation de lubrification centrale avec des distributeurs progressifs passifs (32). A cet effet, l'unité de lubrification est configurée de manière à présenter un frottement réduit, dans la mesure où la chaîne cinématique (13, 14, 15, 16, 20, 21) comporte des moyens de contact roulant (17, 18, 42, 43), et la pression de lubrification (Ps) qui peut être produite lors du fonctionnement de l'unité de lubrification haute pression correspond au moins à la pression d'entraînement (PA) d'un distributeur progressif passif.
PCT/EP2005/012485 2004-12-17 2005-11-22 Unite de lubrification haute pression autonome WO2006066678A1 (fr)

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DE102004061447.4 2004-12-17
DE102004061447.4A DE102004061447B4 (de) 2004-12-17 2004-12-17 Autarkes Hochdruck-Schmieraggregat

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DE202007016788U1 (de) 2007-11-29 2008-02-21 Lincoln Gmbh Schmierstoffgeber
DE102008046153A1 (de) * 2008-09-06 2010-03-11 Bhs Corrugated Maschinen- Und Anlagenbau Gmbh Automatische Schmierung
US8844679B2 (en) 2010-11-29 2014-09-30 Lincoln Industrial Corporation Pump having venting and non-venting piston return
DE102013007629B4 (de) * 2013-05-06 2016-12-15 Benz GmbH Werkzeugsysteme Einwechselaggregat mit einem Kleinmengenschmiermittelspender II
DE102014001755A1 (de) * 2014-02-10 2015-08-13 Wacker Neuson Produktion GmbH & Co. KG Öl-Schmiervorrichtung für Arbeitsgeräte
DE102015207468B4 (de) 2015-04-23 2019-03-07 Skf Lubrication Systems Germany Gmbh Schmiermittelpumpe
DE102017125307A1 (de) * 2017-10-27 2019-05-02 Baier & Köppel GmbH & Co. KG Verfahren zum Steuern einer Zentralschmieranlage, Computerlesbares Speichermedium, Zentralschmieranlage und System

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EP0845631A1 (fr) * 1996-11-27 1998-06-03 Satzinger GmbH & Co. Distributeur de graisse
EP1074734A2 (fr) * 1999-08-04 2001-02-07 Pierburg Aktiengesellschaft Pompe à pistons axiaux
DE10234881A1 (de) * 2002-06-19 2004-01-15 Perma-Tec Gmbh & Co Kg Dosiervorrichtung für Schmierstoff
US6695590B1 (en) * 1999-11-01 2004-02-24 Skf Engineering & Research Centre B.V. Lubricant pump having piston with radial through opening

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DE9214093U1 (de) * 1992-10-19 1992-12-03 Tsai, I-Shou, Taipeh/T'ai-pei Montageanordnung für Festplattenlaufwerk
EP0845631A1 (fr) * 1996-11-27 1998-06-03 Satzinger GmbH & Co. Distributeur de graisse
EP1074734A2 (fr) * 1999-08-04 2001-02-07 Pierburg Aktiengesellschaft Pompe à pistons axiaux
US6695590B1 (en) * 1999-11-01 2004-02-24 Skf Engineering & Research Centre B.V. Lubricant pump having piston with radial through opening
DE10234881A1 (de) * 2002-06-19 2004-01-15 Perma-Tec Gmbh & Co Kg Dosiervorrichtung für Schmierstoff

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