EP0543423A1 - Schmierölzufuhrsystem für eine Brennkraftmaschine - Google Patents

Schmierölzufuhrsystem für eine Brennkraftmaschine Download PDF

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Publication number
EP0543423A1
EP0543423A1 EP92119901A EP92119901A EP0543423A1 EP 0543423 A1 EP0543423 A1 EP 0543423A1 EP 92119901 A EP92119901 A EP 92119901A EP 92119901 A EP92119901 A EP 92119901A EP 0543423 A1 EP0543423 A1 EP 0543423A1
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EP
European Patent Office
Prior art keywords
lubricant
engine
supply
amount
pump
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
EP92119901A
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English (en)
French (fr)
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EP0543423B1 (de
Inventor
Kidera c/o Yamaha Hatsudoki K.K. Hiroyuki
Izumi c/o Yamaha Hatsudoki K.K. Toru
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Yamaha Motor Co Ltd
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Yamaha Motor Co Ltd
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Publication of EP0543423A1 publication Critical patent/EP0543423A1/de
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    • 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
    • F01M3/00—Lubrication specially adapted for engines with crankcase compression of fuel-air mixture or for other engines in which lubricant is contained in fuel, combustion air, or fuel-air mixture
    • F01M3/02—Lubrication specially adapted for engines with crankcase compression of fuel-air mixture or for other engines in which lubricant is contained in fuel, combustion air, or fuel-air mixture with variable proportion of lubricant to fuel, lubricant to air, or lubricant to fuel-air-mixture

Definitions

  • This invention relates to a lubricating oil supplying system for an engine and more particularly to an improved arrangement for supplying an accurate and appropriate amount of lubricant to the engine during all of its running phases.
  • Figure 1 is a graphical view which also appears in the aforenoted co-pending application and which illustrates one of the problems with the prior art type of device wherein the plunger stroke of the lubricant pump is varied corresponding to engine speed and accelerator position.
  • the curve “a” shows the manner in which the stroke of the pump is changed in response to engine speed changes while the curve “b” shows the actual delivery output from the pump.
  • the curve "c” results which provides a substantial increase in the amount of lubricant before the engine speed has actually increased. This results in excess lubricant which, at the minimum, will cause excessive hydrocarbons in the exhaust and at the maximum can additionally cause smoke to develop in the exhaust.
  • the aforenoted application provides an arrangement wherein the pump output is controlled by varying the duty cycle of the flow controlling valve to obtain more accurate control over the amount of lubricant supplied.
  • the flow of lubricant during the time when the valve is being switched between its positions is not as great as when the valve is in its fully opened position. That is, the flow does not follow a square line shape, but rather has curved shape delivery during the opening and closing phases. As a result, the supply of lubricant does not vary completely linearly with the duty cycle of the solenoid valve. This can give rise to variations in the amount of lubricant supplied for a given condition.
  • the variations in lubricant supplied can be minimized if the amount of lubricant supplied to the engine is controlled primarily by extending the length of time when the valve is in its fuel delivery position rather than increasing the frequency of opening of the valve. However, if the time of lubricant delivery is the only variable that is employed in controlling the amount of lubricant, then the system may not be responsive enough under transient conditions.
  • a first feature of the invention is adapted to be embodied in a lubricating system for an internal combustion engine comprising a lubricant pump and lubricant control means for controlling the amount of lubricant delivered by the lubricant pump to the engine.
  • Sensing means sense a running condition of the engine.
  • Means are provided for initiating the supply of an amount of lubricant by the lubricant control means determined in response to the sensed running condition of the engine sensed by the sensing means.
  • Means are provided for changing the condition of the supply of lubricant from the lubricant control means in response to the engine condition requirements as sensed by the sensing means after the lubricant supply has begun.
  • Another feature of the invention is adapted to be embodied in a lubricating system for an internal combustion engine that comprises a lubricant pump and lubricant control means for controlling the amount of lubricant supplied by the lubricant pump to the engine.
  • the lubricant control means is operative to control the amount of lubricant supplied to the engine by selectively delivering lubricant to the engine or bypassing lubricant back to a return.
  • the amount of lubricant supplied to the engine is varied by varying the duty cycle of the control and also the duration of time when the control is supplying lubricant.
  • Another feature of the invention is adapted to be embodied in a lubricating system for an internal combustion engine comprising a lubricant pump.
  • Lubricant control means are provided for controlling the amount of lubricant delivered by the lubricant pump to the engine by varying a duty cycle of delivery of the lubricant.
  • Means are provided for sensing an engine running condition. The time of supply of lubricant by the control means is set to be longer under one series of engine running conditions than another series of engine running conditions.
  • Another feature of the invention is also adapted to be embodied in a lubricating system for an internal combustion engine comprising a lubricant pump.
  • the lubricant pump is a positive displacement pump that is driven in timed relationship with the engine.
  • Lubricant control means are provided for controlling the amount of lubricant delivered by the lubricant pump to the engine.
  • Means are provided for sensing a running condition of the engine.
  • the lubricant control means is provided with an internal map indicating the amount of lubricant to be supplied by the control means during a given time period in response to the sensed engine condition. This map has a portion that is flat so that the amount of lubricant supplied by the control means during this flat portion is the same even though the condition varies.
  • Another feature of the invention is adapted to be embodied in a method for controlling the amount of lubricant supplied to an internal combustion engine by a lubricating system that includes a lubricant pump.
  • a running condition of the engine is sensed and the initiation of the supply of an amount of lubricant by the lubricant control means in response to the sensed condition of the engine prior to the initiation of lubricant supply is initiated.
  • the supply of lubricant by the control means is discontinued once the amount of lubricant supplied for a running condition sensed after the period of supply is initiated is terminated.
  • Yet another feature of the invention is adapted to be embodied in a method of controlling the amount of lubricant supplied to an internal combustion engine by a lubricating system that includes a lubricant pump and a lubricant control which selectively permits the flow of lubricant from the lubricant pump to the engine or bypasses the lubricant back to a return.
  • a lubricating system that includes a lubricant pump and a lubricant control which selectively permits the flow of lubricant from the lubricant pump to the engine or bypasses the lubricant back to a return.
  • the running condition of the engine is sensed and the amount of lubricant supplied is controlled by changing both the duty cycle of the control and the time period during each duty cycle when the control is in its lubricant delivery position.
  • Another feature of the invention is also adapted to be embodied in a method for controlling the amount of lubricant supplied to an engine by a lubricating system including a lubricant pump.
  • Lubricant control means are provided for controlling the amount of lubricant delivered by the lubricant pump to the engine by varying the duty cycle of lubricant delivery.
  • a running condition of the engine is sensed and during a range of the running condition, the lubricant supply period is longer than during another running condition of the engine.
  • a still further feature of the invention is adapted also to be embodied in a method for controlling the amount of lubricant supplied to an engine by a lubricating system including a lubricant pump.
  • a running condition of the engine is sensed and an amount of lubricant is supplied to the engine in response to the running condition in response to a preprogrammed map. That map is preprogrammed to include a flat area wherein the amount of lubricant supplied to the engine is constant even though the running condition varies.
  • Figure 1 is a graphical view showing the prior art type of construction and relationship of lubricant supply and demand amount in relation to engine speed.
  • Figure 2 is a partially schematic cross-sectional view showing the lubricant supply system in accordance with an embodiment of the invention.
  • FIG. 3 is a block diagram of the lubricant supply and control system in accordance with this embodiment.
  • Figure 4 is a map showing the duty cycle in relation to engine speed and throttle opening or load in accordance with this embodiment.
  • Figure 5 is a graphical view of a map showing the actual amount of lubricant supplied in response to engine speed and throttle opening and/or load.
  • Figure 6 is a graphical view showing the actuation of the solenoid control valve and the amount of flow through the valve during a running condition of the engine.
  • Figure 7 is a graphical view, in part similar to Figure 6, showing the characteristics during another running condition of the engine.
  • Figure 8 is a block diagram showing the control routine.
  • Figure 9 is a block diagram showing a portion of the control routine by which the supply time period is selected.
  • Figure 10 is a graphical view showing the lubricant requirements of the engine in relation to time during a condition when the engine is maintained at idle, is accelerated gradually to full throttle, is held at full throttle for a time period and then is decelerated somewhat more rapidly than the acceleration back to idle.
  • Figure 11 is a graphical view, on the same time scale, showing the lubricant pump output.
  • Figure 12 is a graphical view, on the same time scale, showing the duty cycle of the solenoid valve of the lubricant control system.
  • Figure 13 is a graphical view, on the same time scale, showing the actual amount of lubricant supplied to the engine.
  • Figure 14 is a graphical view showing the amount of lubricant supplied to the engine and the amount of lubricant actually consumed during the same time period.
  • Figure 15 is a graphical view showing the amount of residual lubricant in the engine.
  • Figure 16 is a map, in part similar to Figure 4, and shows another map used in conjunction with another type of control strategy.
  • Figure 17 is a graphical view showing the amount of fuel supplied in accordance with the map of Figure 16.
  • Figure 18 is a block diagram showing how the duty cycle is set in accordance with this embodiment of the invention, and is in part similar to Figure 7.
  • an internal combustion engine is identified in block form by the reference numeral 21 and may be of any known type.
  • the invention has particular utility in conjunction with two cycle crankcase compression internal combustion engines and the engine 21 is preferably of this type.
  • a lubricating system is provided for supplying lubricant from a lubricant tank 23 to the engine 21 for its lubrication.
  • the lubricant system 22 includes an engine driven pump 24 which may be of any known type but which, in accordance with a feature of the invention, is a reciprocating plunger type positive displacement pump that is driven in timed relationship with the engine 21.
  • This pump 24 will, therefore, output a fixed amount of lubricant each time the plunger operates through a cycle. Since the pump 24 is driven by the engine 21 in timed relationship, a single rotation of the output shaft of the engine 21 will provide a fixed number of cycles or portions of cycles of the pump 24 and the total output of the pump 24 in a given unit of time will depend upon the rotational speed of the engine 21 as well as the per cycle displacement of the pump. This is important, as will become hereinafter apparent, in conjunction with a feature of the control strategy.
  • Lubricant flows from the lubricant tank 23 to the pump 24 through a supply line 25 and is delivered from the pump 24 through a conduit 26 to a solenoid operated control valve, indicated generally by the reference numeral 27.
  • the solenoid operated control valve 27 is operative to either supply lubricant through a conduit 28 to the engine 21 for its lubrication or to return lubricant to the lubricant tank 23 through a return line 29.
  • the manner in which the lubricant is delivered to the engine 21 may be of any of the known types. That is, the lubricant can be delivered to the engine 21 through its induction system and/or by direct lubrication to various components of the engine to be lubricated.
  • the solenoid operated lubricant control valve 27 includes a housing assembly 31 having an inlet fitting 32 that receives lubricant from the conduit 26 and delivers it to an interior chamber 33 in which a control valve element 34 is supported for reciprocation.
  • the control valve element 34 is biased by a coil compression spring 35 into a normally open supply condition wherein lubricant can flow from the chamber 33 through openings 36 in the valve 34 to a supply conduit 37 which communicates with the conduit 28 for delivery of lubricant to the engine 21.
  • control valve element 34 closes a return passageway 38 also formed in the housing 31, and which communicates with the return line 29.
  • a solenoid winding 39 is provided in the housing assembly 31 and cooperates with the valve element 34, which acts like an armature, and when energized will draw the valve element 34 down from the position shown in Figure 2 to a position wherein the supply passage 37 is closed and the return passage 38 is open. Under this condition, lubricant will be passed back to the lubricant tank 23 through the return conduit 29.
  • the ratio of time when the valve element 34 is in the supply position as shown in Figure 2 to the total time of a given cycle (opened and closed) is defined as the duty ratio.
  • a one hundred percent duty ratio would be a condition wherein the control valve element 34 was always open during one cycle of operation.
  • control unit 41 receives input signals indicative of certain engine running conditions. In the illustrated embodiment, these conditions are engine speed as sensed by an output signal, indicated by the character "r" from an ignition circuit 42 of the engine 21, the engine 21 being spark ignited.
  • a load or throttle valve position signal "T” is supplied to the control unit 41 from a throttle valve position sensor 43 which senses the position of the throttle valve of the engine 21.
  • the control unit 41 completes a circuit to the winding 39 from a battery 44 and through a main switch 45.
  • the circuit is such that when the main switch 45 is closed, a switching device such as an SCR will be maintained in its "off" condition so as to de-energize the winding 39 and leave the solenoid control valve 27 in its lubricant supply position as shown in Figure 1.
  • the SCR will switch and the winding 39 will be energized to cause recirculation of the lubricant back to the tank 23 through the return passage 38 and return conduit 39.
  • control unit 41 includes a number of components including an internal map 46 which may be stored on a device such as an ROM and which, in one embodiment, has a configuration as shown in Figure 4.
  • This map is generated to set the duty cycle of the solenoid control valve 27 so as to provide the desired amount of lubricant for the engine as shown in Figure 5.
  • the maps of Figures 4 and 5 are determined by actual measurements on the engine 21 as to its lubricant requirements under all speed and throttle settings.
  • Information is supplied, as aforenoted, to the control unit 41 from the throttle valve position sensor 43 and from the ignition circuit 42.
  • the ignition circuit 42 outputs its signal to a speed calculator unit 47 of the control unit 41 which converts the pulses from the ignition circuit into a speed information signal.
  • This information is, in turn, transmitted to a supply lubricant amount calculator 48 and a consumption amount calculator 49, both of which also receive information from the map 46.
  • the signals are processed and then are transmitted to an interrupt driver 51 which controls the aforenoted SCR so as to switch the solenoid winding 39 of the control valve 27 between its energized non-flow position and its non-energized flow position through a holding circuit 50.
  • the control unit 41 also includes a timer 52 that runs and resets during fixed time intervals and which outputs its signal to the calculators 48 and 49 so as to provide the necessary time signals.
  • the lubricant is supplied to the engine during the time when the interrupt means 51 has the control valve in its flow position and then shuts off the supply after the time has run.
  • the difference between the amount of lubricant supplied and the lubricant consumed is processed in a residue amount calculator 53 so as to provide control for the lubricant.
  • the strategy operates in accordance with a procedure wherein the running condition of the engine is sensed immediately prior to the switching off of the solenoid 39 and the initiation of supply of lubricant by the control valve 27. Lubricant supply is then begun and a fixed time interval is set for the interrupt driver 51 so as to again switch the solenoid 39 on after the time period when the calculated amount of lubricant will have been delivered.
  • the system continually monitors engine running condition and if the running condition changes, the interrupt means 51 is switched so as to turn the solenoid 39 back on when the actual necessary amount of lubricant has been supplied.
  • the residue amount calculation device 53 is employed, in a manner which will become apparent, so as to continually monitor the system and ensure that the minimum amount of lubricant necessary for the actual running condition is supplied so as to avoid hydrocarbon emissions and smoke in the exhaust of the engine.
  • the timer 52 sets out a timing signal with a time such as 80 milliseconds to the interrupt driver circuit 51.
  • the interrupt driver counts the number of such time signals so as to supply the necessary lubricant. For example, if the engine is operating at idle and it is determined that the necessary lubricating oil supply period is 960 milliseconds, then a set value of 12 is inserted into the interrupt means so that the time when the control valve 27 is supplying lubricant will be the period of 960 milliseconds.
  • the amount of lubricant supplied to the engine will be dependent upon not only the duty ratio of the control valve 27, but also the total time when the control valve 27 is placed in its flow supplying position.
  • the control strategy is such so as to provide accurate control by varying not only the duty ratio but also the time T when the control valve is in its opened position.
  • the first curve of Figure 6 shows a condition when there is a long time of valve maximum opening, indicated as T1 or T2, which times are illustrated as being substantially the same, but it is understood that the times T1 and T2 may be different from each other.
  • T1 or T2 a long time of valve maximum opening
  • T1 and T2 may be different from each other.
  • t1 time delay between when the solenoid is switched off and until the valve element 34 is in its fully opened position. This delay is caused first by a time delay before any movement occurs after switching and also the time required for the valve element 34 to move from its fully closed bypass position to its fully opened supply position.
  • the amount of lubricant supplied will vary from that if the valve element was in its fully opened position for the time T1 or T2. If long supply periods are maintained, as is the time periods T1 and T2, then the amount of hysteresis effect in the opening and closing of the valve will be minimized and more accurate control of the lubricant can be supplied.
  • a long supply period is chosen, it is difficult to provide rapid changes in the amount of lubricant supplied when the engine is in a transient condition. Therefore, there is another control strategy period as shown in Figure 7 when the time T3 of valve opening is less than the time T1 and T2. Again, there are the time delays t1 upon opening and t2 upon closing. However, it is possible to change the amount of lubricant being supplied more quickly in response to changes in engine condition under this control mode.
  • the mid-range control phase indicated by the designation T2 is in intermediate speed and load (throttle) positions wherein transient conditions are more likely to occur and wherein it is more desirable to maintain a shorter duration of valve opening while, at the same time, assuring that transient conditions can be quickly responded to.
  • T1 intermediate speed and load
  • T2 load
  • T3 the amount of lubricant supplied is determined by the duty cycle as well as the fixed times T1, T2 and T3 of actual valve opening. This construction and the effect of it will be described later by reference to Figures 10-15.
  • the duty cycle at the high speed high load range is set to be one hundred percent over a fairly flat area as shown in the map in Figure 4.
  • the low speed low throttle opening domain also has a fairly flat area where the duty cycle is fixed at its lowest amount.
  • the amount of lubricant supplied will vary to provide a lubricant supply as shown in Figure 5.
  • the reason for this is that the number of pumping cycles also will change with engine speed so that even though the duty ratio and time of valve opening is held constant, more lubricant will be supplied when the engine is running faster than when slower. Because of this choice of flat areas of the map, it is possible to obtain greater control accuracy with a minimum number of variables to be programmed into the system.
  • the supply amount calculator unit 48 has a means for calculating the amount of lubricating oil supplied to the engine. This is done by calculating the number of pumping strokes of the pump 24 that occur during the time when the solenoid 39 is in its off condition and the control valve 34 is in its open supply condition. Hence, this calculator 48 only requires indication of the speed signal and an indication of the duration of time when the interrupt means 51 is interrupting the supply of electrical current to the coil winding 39.
  • the consumption calculator 49 calculates the actual amount of lubricant consumed by the engine. This makes a consumption calculation based upon the consumption of lubricant during the time when the solenoid coil 39 is in its energized position and the control valve 34 is in its bypassing position so that lubricant is not being supplied to the engine. This is done by calculating the amount of lubricating oil consumed per unit of time based upon information from the map 46 dependent upon engine speed and throttle opening and also the lapse of time occurring after the starting operation of the interrupting means 51.
  • the residue amount calculating means 53 operates to compare the amount of fuel supplied by the supply amount calculator 48 and the consumption amount by the consumption calculator 49 and determines the residue lubricant. When the residue lubricant reaches 0, then the solenoid winding 39 is again de-energized to open the control valve 34 and permit the supply of lubricant to the engine 21.
  • the residue amount calculating means 53 also includes an integrating circuit for integrating the difference between the supply amount and the consumption amount and determining whether the lubricating oil bypass period is longer or shorter than a predetermined time and when it is longer than this predetermined time, the solenoid 39 is de-energized regardless of the integration results to prevent the lubricating oil bypass period to become longer than a predetermined amount for any reason.
  • the program moves to the step P3 to read the engine conditions so as to determine the lubricant supply period.
  • the engine speed r is supplied to the supply amount calculator 48 from the speed calculator 47 which, as noted, receives a signal from the ignition circuit 42.
  • the throttle valve position T is received from the throttle valve 43.
  • the program then moves to the map of Figure 4 at the step P4 so as to determine the duty cycle and also the lubricant supply period based upon these conditions.
  • step S1 the program moves to the step S1 to read engine speed r and throttle valve position T.
  • step S2 the program then moves to the step S2 to consult the map 46 and select a duty ratio D based on the engine speed and throttle opening for the current engine operating condition.
  • the program then moves to the step S3 to determine if the set duty ratio D is less than or equal to the duty ratio of the line A in the map of Figure 4 to determine whether the control domain should be set to the domain T1 or one of the domains T2 or T3 which will determine the time at which the solenoid coil 39 is maintained in its off condition so as to control the time of lubricant supply.
  • the program moves to the step S4 so as to set the supply period T1.
  • the program then moves to the step S5 so as to output this supply period T1 to the program appearing in Figure 8 at the step P4.
  • the program moves to the step S6 to determine whether the supply period T3 or the supply period T2 should be chosen. This is accomplished at the step S6 to determine if the engine speed r is less than or equal to the speed set by the line B on the map 4. If the speed r is less than that defined by the line B on the map of Figure 4, the program moves to the step S7 so as to set the supply period time T2. If the supply period T2 is set at the step S7, the program outputs this signal at the step S8 and proceeds to the step P4 of Figure 8.
  • the program moves to the step S9 so as to set the supply period T3.
  • the program then moves to the step S10 to output this set time period T3 and moves on to the step P4.
  • control unit 41 functions to determine which of the supply time periods T1, T2 or T3 from Figure 4 are outputted in the control unit 41 so as to set the lubricant amount strategy.
  • control strategy is such that the initial amount of lubricant to be supplied to the engine is determined by the running condition immediately prior to when the calculation is being made.
  • the program moves to the step P5 ( Figure 8) to output a trigger signal in the timer 52 to begin counting.
  • the signal holding circuit 50 will be positioned in a condition so as to hold the solenoid 39 in its off position so that the control valve 27 will be supplying lubricant.
  • the program moves to the step P6 to immediately begin the calculation of the actual lubricant consumption and this is done by reading at first at the step P6 the engine condition comprised of the engine speed r and the throttle valve position T.
  • the program then moves to the step P7 so as to calculate the actual amount of lubricant supplied. This is done by referring to the map of Figure 4 to determine the actual engine speed and throttle opening at this time period and then to determine the amount of lubricant which will have been consumed by the engine during the time period for the timer to have one of its timed pulses.
  • the program makes this calculation at the step P7.
  • the program then moves to the step P8 so as to add the amount of lubricant calculated at the step P7 to the amounts of lubricant previously calculated as being consumed.
  • the program then moves the step P9 so as to determine if the control valve 27 is in its supplying, off condition or in its non-supplying, on condition.
  • the program then moves to the step P10 to calculate the amount of lubricant being supplied. This is done by determining the initial supply condition as set at P4 and then calculating the amount of lubricant supplied in the time period for one trigger pulse. The amount of lubricant thus supplied is then added to the previously supplied amount of lubricant calculated at the step P11.
  • the program then moves to the step P12 to add one trigger count to the counter of the timer 52.
  • the program then moves to the step P13 to determine if the amount of lubricant called for at the supply period determination of step P4 has been made by calculating the number of trigger pulses which have been set. If the timed number of pulses have been determined and set, the program then moves to the step P14 so as to shut off the control valve 27 by energizing the solenoid 39 and stopping the supply of lubricant.
  • the program then returns to the step P5 and repeats the continuation of the calculation of amount of lubricant consumed at the steps P5 through P8.
  • the program then moves to the step P15 so as to determine the amount of lubricant which has been supplied in excess of that being consumed. This is called the residual amount of lubricant and this calculation is made by the calculator 53.
  • the program then moves to the step P16 to determine if the return time when the control valve is in its non-supply return condition is longer than the set time and if it is not, the program moves to the step P17 to determine if there still is residual lubricant. That is, at the step P17 the amount of lubricant supplied during the total supply period is compared with the amount of lubricant consumed and if lubricant residual is not less than or equal to zero, the program returns to the step P5 to again calculate the amount of lubricant being consumed until the total amount of lubricant consumed is equal to that which has been supplied.
  • the program then moves to the step P18 so as to reset the timer and to the step P19 to again begin lubricant supply by turning the solenoid winding 39 off and initiating the supply period of the control valve 27.
  • control routine is very effective in maintaining the strict control over the amount of lubricant supplied to the engine by setting an initial supply period dependent upon the running condition at the time when lubricant supply is started, but by not reinstituting a new supply of lubricant to the engine until the actual running conditions of the engine indicate that the lubricant amount previously supplied has all been consumed.
  • this system is extremely responsive to transient conditions and Figures 10-15 show specifically how the system responds to changed conditions of the engine.
  • Figures 10-15 are a graphical representation of how this control is achieved and depict a situation wherein the engine is operating at idle speed, is gradually accelerated to maximum speed and load, maintained there for a period and then decelerated, somewhat more rapidly than the acceleration, to idle speed.
  • Figure 10 shows the lubricant requirements under the various time conditions.
  • the pump output versus time is such that the number of pulses of the pump or pumping cycles are relatively low when the engine is operating at low speed, and increase in frequency as the speed increases and then again decrease in frequency as the speed decreases.
  • Figure 12 shows the on/off conditions of the solenoid valve during the running and the various "off" times T1, T2 and T3 under the various running conditions.
  • the time period T2 from the map of Figure 4 is selected so as to provide minimum effect in variations in lubricant supply due to the opening and closing operation of the valve element 34.
  • the shorter time period T3 is chosen so as to improve response to the transient condition.
  • the longer time periods T1 and T2, respectively are chosen.
  • control routine of the embodiment there have been three main control phases during which the times T of supply of lubricant have been varied depending upon the engine running conditions.
  • control phases are determined by engine running conditions and set the actual time when the control valve 27 is maintained in its supply position.
  • this map is similar to map of Figure 4, but the control phases are divided into four control domains T1, T2, T3 and T4.
  • the phase T1 has a relatively long duration of the supply period of the control valve 27. This is similar to the corresponding period T1 of Figure 4 and lies in a domain between the planes L1 and L2 which are defined by the duty ratio line A and revolution speed line B.
  • the control phase T3 lies also between the lines A and B and the intersection between the planes L1 and L2 and also has a relatively short time period as with the previously described embodiment so as to accommodate transient conditions.
  • a longer time period T2, which may be similar to the time period T1 lies in the domain at high throttle openings and low engine speeds where the planes L1 and L2 intersect.
  • There is an added control period T4 wherein the lubricant supply period is set even longer than the times T1 or T2 or T3 and which is in the range of low throttle openings and low speed. This provides an even greater accuracy of lubricant supply under these conditions.
  • control routine of this embodiment is basically the same as the control routine shown in Figure 8 of the previously described embodiment.
  • control routine of Figure 9 of that previous embodiment is replaced by the control routine of Figure 18 wherein the respective domains T1, T2, T3 or T4 are selected. Therefore, in order to understand the control routine of this embodiment it is only necessary to describe that of Figure 18 wherein the values T1, T2, T3 or T4 are determined. Certain steps of this routine are the same as the steps in Figure 9 and where that is the case, these steps have been identified by the same step numbers.
  • the engine speed r and throttle valve position T are read.
  • the program then moves to the step S2 so as to select the duty ratio D from the map of the Figure 16.
  • the program then, like the previous program, moves to the step S3 to determine if the duty ratio D is less than or equal to the valve A. If the duty ratio is less than or equal to A, the program then moves to the step S6, as with the previously described embodiment, to determine if the speed r lies on one side or the other of the speed line B. If it is equal to or less than the speed line B, the program moves to the step S7 so as to select the supply time T2 and to output this time T2 at the step S8 back to the program for the control.
  • the program moves to the step S9 so as to set the supply time T3 and at the step S10 to output this supply time to the control unit.
  • the program must determine whether to apply the time T1 or the time T4 according to the map of Figure 16. The program then moves to the step S11 so as to determine if the engine speed is less than or equal to the speed of the curve B. If it is less than or equal to the speed B, the program moves to the step S12 so as to set the supply time T4 and at the step S13 to output this time T4. If, however, the engine speed r is not less than or equal to the speed B, the program moves to the step S4, as previously noted, so as to set the supply time T1 and output this time T1 to the control.
  • the map of Figure 16 also has a flat area at high engine speeds and high throttle openings and a flat area at low engine speeds and low throttle openings.
  • the lubricant pump 24 is driven in timed relationship to the engine and hence varies the number of pumping cycles in response to engine speed, the lubricant supply curve of Figure 17 will be generated and adequate and proper lubricant will be supplied under all conditions.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
EP92119901A 1991-11-22 1992-11-23 Schmierölzufuhrsystem für eine Brennkraftmaschine Expired - Lifetime EP0543423B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP332781/91 1991-11-22
JP33278191 1991-11-22
JP89297/92 1992-03-16
JP8929792 1992-03-16

Publications (2)

Publication Number Publication Date
EP0543423A1 true EP0543423A1 (de) 1993-05-26
EP0543423B1 EP0543423B1 (de) 1996-10-23

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Application Number Title Priority Date Filing Date
EP92119901A Expired - Lifetime EP0543423B1 (de) 1991-11-22 1992-11-23 Schmierölzufuhrsystem für eine Brennkraftmaschine

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Country Link
EP (1) EP0543423B1 (de)
JP (1) JP3172954B2 (de)
DE (1) DE69214774T2 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0756070A2 (de) 1995-07-25 1997-01-29 Outboard Marine Corporation Schmierungsanlage für eine Zweitaktbrennkraftmaschine

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10124564A1 (de) * 2001-05-14 2002-11-28 Joma Hydromechanic Gmbh Verfahren zum Verstellen einer volumenstromvariablen Verdrängerpumpe in einem Brennkraftmotor
DE102012013709B3 (de) * 2012-07-11 2014-01-02 Sms Meer Gmbh Schmiervorrichtung zur Versorgung einesWerkzeugs mit Schmiermittel

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2411513A1 (de) * 1974-03-11 1975-09-25 Audi Nsu Auto Union Ag Schmiervorrichtung fuer brennkraftmaschinen
US4904163A (en) * 1987-10-30 1990-02-27 Nippondenso Co., Ltd. Oil regulating pump for lubricating engines and method of controlling thereof

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0508486B1 (de) * 1991-04-12 1996-10-02 Yamaha Hatsudoki Kabushiki Kaisha Verfahren zur Schmierung einer Zweitakt-Brennkraftmaschine und Schmierölzufuhrsystem

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2411513A1 (de) * 1974-03-11 1975-09-25 Audi Nsu Auto Union Ag Schmiervorrichtung fuer brennkraftmaschinen
US4904163A (en) * 1987-10-30 1990-02-27 Nippondenso Co., Ltd. Oil regulating pump for lubricating engines and method of controlling thereof

Non-Patent Citations (2)

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Title
PATENT ABSTRACTS OF JAPAN vol. 10, no. 204 (M-499)(2260) 17 July 1986 & JP-A-61 46 409 ( MAZDA MOTOR CORP ) 6 March 1986 *
PATENT ABSTRACTS OF JAPAN vol. 12, no. 121 (M-686)(2968) 15 April 1988 & JP-A-62 248 812 ( NIPPON SOKEN INC ) 29 October 1987 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0756070A2 (de) 1995-07-25 1997-01-29 Outboard Marine Corporation Schmierungsanlage für eine Zweitaktbrennkraftmaschine
US5632241A (en) * 1995-07-25 1997-05-27 Outboard Marine Corporation Oil lubricating system for a two-stroke internal combustion engine

Also Published As

Publication number Publication date
JP3172954B2 (ja) 2001-06-04
EP0543423B1 (de) 1996-10-23
JPH05321628A (ja) 1993-12-07
DE69214774D1 (de) 1996-11-28
DE69214774T2 (de) 1997-02-20

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