CN1218870A - Lubricating device for vehicle engine - Google Patents
Lubricating device for vehicle engine Download PDFInfo
- Publication number
- CN1218870A CN1218870A CN 98122805 CN98122805A CN1218870A CN 1218870 A CN1218870 A CN 1218870A CN 98122805 CN98122805 CN 98122805 CN 98122805 A CN98122805 A CN 98122805A CN 1218870 A CN1218870 A CN 1218870A
- Authority
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- China
- Prior art keywords
- valve
- solenoid valve
- oil
- oil pump
- cycle
- 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
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N1/00—Silencing apparatus characterised by method of silencing
- F01N1/08—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling
- F01N1/083—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling using transversal baffles defining a tortuous path for the gases or successively throttling gas flow
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2240/00—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being
- F01N2240/20—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being a flow director or deflector
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
Abstract
The present invention provides a lubricating device of a vehicular engine. Wherein a valve opening period t1 of a solenoid valve is made longer than a nondelivery period t3 of an oil pump, and shorter than a delivery cycle T2 regardless of an engine speed which is the delivery cycle T2 of the oil pump. The valve opening period t1 of the solenoid valve is made not longer than the delivery cycle T2 of the oil pump, and the valve opening cycle T1 of the solenoid valve is made not shorter than the oil delivery period t2 of the oil pump by this controlling, so that the valve opening period t1 of the solenoid valve can always overlap the oil delivery period t2 .Thus, the amount of lubricating oil is controlled precisely according to an engine speed.
Description
The present invention relates to the mobile engine lubricating fitting of the lubricant oil supply engine of oil pump being discharged off and on, particularly relate to the lubricating fitting that to control the mobile engine of lubricant oil delivery volume corresponding to the rotating speed of motor accurately by solenoid valve.
Additional on mobile engine have lubricating fitting, and this lubricating fitting supplies in the suction tude from solenoid valve by with oil pump the lubricant oil in the fuel tank being directed to solenoid valve, thus the slide part of piston in the lubricating engine and bent axle etc.
Figure 16 illustrates the schematic representation that the major component of the lubricating fitting of prior art constitutes, and oil pump 33 is connected with fuel tank 8 by suction pipe 32, and passes through discharge tube 34 and be connected with the oil-in 35a of solenoid valve 35.The return opening 35c of solenoid valve 35 is connected with above-mentioned fuel tank 8 by return tube 36, and oil export 35b is connected in the suction tude (not shown) of motor 10.
Above-mentioned oil pump 33 is connected in the bent axle (not shown) of motor 10, with the revolution of the bent axle lubricant oil in solenoid valve 35 is discharged fuel tank 8 off and on synchronously.That is the oily tap-off cycle and the engine speed of oil pump 33 are synchronous.The lubricant oil supply engine 10 that solenoid valve 35 is discharged oil pump 33 corresponding to the actuating signal of control device 40 outputs makes it return fuel tank 8 corresponding to stop signal.
In the lubricating fitting of above-mentioned formation, when the timing by oil pump 33 removal of lubricants and solenoid valve 35 open valve timing when consistent, then with lubricant oil supply engine 10, so, as both discharge and open valve timing and stagger, then can not correctly control the delivery volume of the lubricant oil that supplies to motor 10.Therefore, for example open in flat 4-292512 number, proposed 2 kinds at the control of oil pump 33 and solenoid valve 35 and made flowing mode the Japanese patent gazette spy.
Fig. 9,10 is respectively the timing diagram that the 1st and the 2nd of above-mentioned prior art is made flowing mode is shown, (a) for the discharge of oil pump/do not discharge regularly, (b) be solenoid valve switching regularly, (c) be the supply timing of lubricant oil.
Do in the flowing mode at the 1st shown in Fig. 9, by the t during the valve that opens solenoid valve
1Be controlled at the tap-off cycle T of oil pump
2More than, make the t during the valve that opens of solenoid valve
1Must and oil expulsive stage between t
2Overlap.In addition, do in the flowing mode, by solenoid valve left the valve period T the shown in Figure 10 the 2nd
1Be set in the efflux time t of oil pump
2Below, make the t during the valve that opens of solenoid valve
1Must and oil expulsive stage between t
2Overlap.
Though the delivery volume of lubricant oil need increase along with the rising of engine speed, but in above-mentioned prior art, the the 1st and the 2nd to make flowing mode all be to open the valve ratio by what increase solenoid valve along with the rising of engine speed, that is, increase the delivery volume of lubricant oil along with the valve dutycycle is opened in the rising raising of engine speed.
Do in the flowing mode in the 1st of above-mentioned prior art, because need be the t during the valve that opens of solenoid valve
1Control to the oily tap-off cycle T of oil pump
2More than, so the valve cycle of opening of solenoid valve must be elongated.Therefore, though the aggregate supply in can being controlled between longer-term, but the opening valve time of solenoid valve is for the servo-actuated deterioration of engine speed change, particularly in the few occasion of discharge capacity, owing to discharge elongated at interval, each difference of discharging discharge capacity regularly becomes big, so there is the low problem of the control response of oily discharge capacity.
Do in the flowing mode the above-mentioned the 2nd and since need be with solenoid valve open the valve period T
1Be controlled at the oily efflux time t of above-mentioned oil pump
2Below, so need make the solenoid valve high speed motion.Yet, because there is the limit based on electric and mechanical restriction in the movement speed of solenoid valve, so, particularly when engine speed rises, t between the expulsive stage of oil pump
2When shortening, it is impossible that the electromagnetic pump high speed motion is come down to, even suppose its possibility, the discharging operation of oil is also very difficult, can not control.
When the opening that the valve dutycycle rises along with engine speed of solenoid valve and when improving, the above-mentioned the 1st and the 2nd problem points of making flowing mode becomes more deep.
Purpose of the present invention just is to provide a kind of lubricating fitting that can control the mobile engine of lubricant oil delivery volume corresponding to engine speed accurately, to solve above-mentioned prior art problems.
In order to achieve the above object, the invention provides a kind of lubricating fitting of mobile engine, the lubricant oil supply engine that this lubricating fitting is discharged oil pump off and on by solenoid valve; It is characterized in that: opening of solenoid valve is controlled at the not above and do not finish in the scope of tap-off cycle between expulsive stage of oil pump during the valve.
According to above-mentioned formation, not with the t during the valve that opens of solenoid valve
1Extend to the oily tap-off cycle T of oil pump
2More than, nor solenoid valve left the valve period T
1Shorten to the oily efflux time t of oil pump
2Below, opening during the valve of solenoid valve overlapped between certain and oily expulsive stage.Therefore, can improve supply precision and responsiveness simultaneously.
Accompanying drawing is simply described as follows:
Fig. 1 is for adopting the left surface figure of automatic two-wheeled cycle of the present invention.
Fig. 2 is the gas handling system of employing motor of the present invention and the system diagram of lubrication system.
Fig. 3 is the sectional view of solenoid valve.
Fig. 4 is for adopting the left side view of motor of the present invention.
Suction port and suction tude on every side the left side view of Fig. 5 for adopting motor of the present invention.
Fig. 6 is for adopting the right side view of motor of the present invention.
Fig. 7 is for adopting motor of the present invention plan view on every side.
Fig. 8 is the timing diagram that elemental motion of the present invention is shown.
Fig. 9 illustrates the timing diagram that the 1st of prior art is made flowing mode.
Figure 10 illustrates the timing diagram that the 2nd of prior art is made flowing mode.
Figure 11 is for illustrating the timing diagram of action of the present invention (during the low engine speed revolution).
Figure 12 is for illustrating the timing diagram of action of the present invention (during the medium engine speed revolution).
Figure 13 is the timing diagram when action of the present invention (during the high engine speeds revolution) is shown.
Figure 14 is the figure that opens the relation between the valve dutycycle that engine speed and solenoid valve are shown.
Figure 15 is the figure that opens the relation between the valve dutycycle that engine speed and oil supply amount and solenoid valve are shown.
Figure 16 is the schematic representation of formation of major component that the lubricating fitting of prior art is shown.
Describe the present invention below with reference to the accompanying drawings in detail." preceding ", " back ", " left side ", " right side ", " on ", D score is that the direction of watching according to the driver is judged, Fr is the front side, Rr is a rear side, L is the left side, R is the right side.In addition, accompanying drawing is watched along the symbol direction.
Fig. 1 is a two-wheeled left side view involved in the present invention.Two-wheeled 1 is made of following part: cradle type vehicle body frame 2, be installed in the front fork 4 on the preceding pipe 3 of vehicle body frame 2, be installed in the front-wheel 5 on the front fork 4, be connected in the steering tiller 6 of front fork 4, stride across the fuel tank 7 that the front upper portion ground of vehicle body frame 2 is installed, be installed on the fuel tank 8 of vehicle body frame 2 in the left bottom of fuel tank 7, be installed in the vehicle seat 9 on the top, rear portion of vehicle body frame 2, be configured in water-cooled 2 two-stroke engines 10 in the cradle space of vehicle body frame 2, be connected in series in the air-strainer 11 of the suction port of motor 10, Carburetor 12 and suction tude 13, suction chamber 14 from suction tude 13 branches, be connected in the outlet pipe 15 and the baffler 16 of the relief opening of motor 10, be configured in the radiator 17 in motor 10 the place aheads, be installed on the rocking arm 18 at vehicle body frame 2 rear portions, the rearward end of rocking arm 18 is hung on the rear suspension 19 of vehicle body frame 2, be installed on the trailing wheel 20 of rocking arm 18.
Two-wheeled 1 disposes a pair of passenger with pedal 23 (1 in left side only is shown in the figure) in the left and right sides side of the crankcase 10a of motor 10, be used for oil feeding device 30 to motor 10 supplying lubricating oils in the nearby configuration of motor 10.Two-wheeled 1 has gear shift pedal 24, driving chain 25, front mudguard 26, side cover 27 and rear mudguard 28.
Fig. 2 is the system diagram that the lubricating oil system of engine aspirating system involved in the present invention and oil feeding device is shown.
The gas handling system of motor 10 constitutes by they being coupled together by the order of needle spring plate valve 29, suction tude 13, Carburetor 12 and air-strainer 11 at its suction port 10b.The chamber of suction chamber 14 for coming in and going out by the mixed gas of suction tude 13, its effect are that utilization is accompanied by the suction tude 13 interior pressure oscillations of needle spring plate valve 29 switchings and imports mixed gass from suction tude 13, or discharge mixed gas to suction tude 13.Because the effect of suction chamber 14 can be eliminated the fluctuation of the induction air flow ratio of suction port 10b, improve intake efficiency.
The oil pump 33 that oil feeding device 30 drives by means of the bent axle 10c by motor 10 by the flow of lubricant amount control device 35 (following note is simply made solenoid valve) that is made of solenoid valve, is supplied with suction tude 13 with the lubricant oil in the fuel tank 8.Specifically, oil feeding device 30 is by the lubricating oil system of lubricant oil by the path supply engine 10 of fuel tank 8 → oil purifier 31 → suction pipe 32 → oil pump 33 → discharge tube 34 → solenoid valve 35 → suction tude 13 constituted.This lubricating oil system also has as required makes lubricant oil turn back to the return tube 36 of fuel tank 8 from solenoid valve 35.
Bent axle 10c drives oil pump 33 directly or indirectly, for example is gear drive, belt drives, chain-drive structure.Suction pipe 32, discharge tube 34 and return tube 36 for example are made of the flexible pipe of rubber system.The opening valve time of above-mentioned solenoid valve 35 and open the valve cycle as described later by control device 100 control.
Fig. 3 is the sectional view of above-mentioned solenoid valve 35.Solenoid valve 35 is the solenoid type three-way valve, and it is by opening and closing the actuator state ground control flow rate of lubricating oil that is suitable for motor 10 repeatedly.This solenoid type three-way valve comprises: the valve chamber 41 that the end is arranged, cover on the valve gap 42 at valve chamber 41 upper opening places, in be loaded on the tubular coil rack 43 of valve chamber 41, be wound on the electromagnetic coil 44 on the coil rack 43, connect the core 45 at the end of valve chamber 41 from the center of coil rack 43, thereby move the valve body 46 that switches oil circuit vertically in 43 of coil racks, elastic force acts on the pressure spring 47 of valve body 46.
In solenoid valve 35, oil-in 35a extends to the side from valve gap 42, and oil export 35b extends downwards from core 45, and return opening 35c extends upward from valve gap 42.Oil-in 35a links to each other with discharge tube 34, and oil export 35b links to each other with suction tude 13, and return opening 35c links to each other with return tube 36.In such solenoid valve 35, if being non-excited state then valve body 46, electromagnetic coil 44 rises, oil-in 35a is communicated with by the oil circuit 46a of valve body with oil export 35b.If electromagnetic coil 44 is an excited state, then valve body 46 descends, and oil-in 35a is communicated with return opening 35c.
Fig. 4 is the left side view of motor of the present invention, in the suction tude 13 of the gas handling system of motor 10 solenoid valve 35 is installed, the cylinder portion of motor 10 by cylinder with cover 51 coverings.
Fig. 5 is the left side view around engine intake of the present invention and the suction tude.Suction tude 13 is flexible tubes such as rubber hose, and this flexible tube forms as one 2 sockets (the 1st socket 13a and the 2nd socket 13b).In the 1st socket 13a, insert suction chamber 14, in the 2nd socket 13b, insert the oil export 35b of solenoid valve 35.Solenoid valve 35 is owing to be directly installed on suction tude 13, so do not need installation component such as supporting member, it is simple that mounting construction becomes.
Fig. 6 is the right side view of motor involved in the present invention, and the posture of the motor of seeing from the inboard 10 above-mentioned illustrated in fig. 4 is shown, and has wherein saved cylinder with a upper right part of covering 51.
At the crankcase 10a of motor 10, in the front portion of right flank water pump 54 is installed, oil pump 33 is installed above water pump 54.Extend oil pump control flexible cord 33a from oil pump 33.Crankcase 10a is covered by side cover 55 (only with double dot dash line right flank being shown), and meanwhile, oil pump 33 and water pump 54 are also covered by side cover 55.
Fig. 7 is a motor planimetric map on every side involved in the present invention, fuel tank 8 is configured in a side (left side or right side) of vehicle body center C, solenoid valve 35 relies on vehicle body center C one side ground (eccentric distance S ground) and is configured, and oil pump 33 is configured in the opposite side (right side or left side) of vehicle body center C.
As shown in Figure 5, solenoid valve 35 can be configured in by being directly installed on suction tude 13 suction tude 13 near.Thereby, can shorten from solenoid valve 35 to suction tude 13 oily path (path oil export 35b and the 2nd socket 13b).Therefore, can reduce the outside chaotic influence that oily path causes, can precision control the flow rate of lubricating oil that supplies to suction tude 13 from solenoid valve 35 well.
In Fig. 7, the lubricant oil in the fuel tank 8 flows into oil pump 33 by suction pipe 32, and this suction pipe 32 is by the rear of motor 10.The lubricant oil of discharging from oil pump 33 passes through the oil-in 35a that discharge tube 34 flows into solenoid valves 35, and this discharge tube 34 is by the right side side of motor 10.The lubricant oil that returns from the return opening 35c of solenoid valve 35 flows into the return opening of fuel tanks 8 by return tube 36, and this return tube 36 is by the left side side of motor 10.
Because 35 discharge tube (oily path) 34 is long from oil pump 33 to solenoid valve, thus the lubricant oil of this discharge tube 34 of flowing through heated widely by the heat radiation of motor 10, thereby viscosity descends.
On the other hand, solenoid valve 35 flows through the lubricant oil (fluid) of established amount by the stream of having controlled, and its precision exists with ... viscosity to a great extent.For full-bodied lubricant oil, owing to alter a great deal instability corresponding to temperature variation viscosity so flow rate of lubricating oil is easy to become.In this, for low viscous lubricant oil, even temperature variation, viscosity change is also little, and flow rate of lubricating oil is stable.In form of implementation of the present invention,,, can improve control accuracy so the flow rate of lubricating oil of supplying with suction tude 13 from solenoid valve 35 is easy to control because oil body is little.
Below, with reference to the timing diagram of Fig. 8, describe the controlling method of the solenoid valve 35 of the control device 100 that adopts above-mentioned Fig. 2 explanation in detail.The discharge of Fig. 8 (a) expression oil pump 33/do not discharge regularly (b) is the elemental motion timing by the solenoid valve 35 of control device 100 controls, (c) is the supply timing of lubricant oil.
The valve state of opening of solenoid valve 35 means oil-in 35a and the state that oil export 35b is communicated with, and closes the valve state and means the state that oil-in 35a is communicated with return opening 35c.
In this form of implementation, there is such feature: the tap-off cycle T that calculates oil pump 8 according to engine speed Ne
2No matter engine speed is the tap-off cycle T of oil pump 8
2What are, all make the t during the valve that opens of solenoid valve 35 under each cycle
1Often be longer than the not t between expulsive stage of oil pump 8
3And be shorter than tap-off cycle T
2
As with timing controlled solenoid valve 35, then need not make the t during the valve that opens of solenoid valve 35
1Oily tap-off cycle T at oil pump 33
2More than, nor open the valve period T with what make solenoid valve 35
1T between the oily expulsive stage of oil pump
2Below, can make the t during the valve that opens of solenoid valve 35
1T between certain and oily expulsive stage
2Overlap.
Next, the controlling method that is used for increasing along with the rising of engine speed the lubricant oil delivery volume under the state of above-mentioned condition satisfying is described.
Figure 11～13 are for illustrating the tap-off cycle T of oil pump
2The timing diagram of the switching of solenoid valve 35 variation regularly when synchronously changing with engine speed change.Timing diagram when the timing diagram when Figure 11 turns round for low engine speed, Figure 12 turn round for middling speed, the timing diagram when Figure 13 is high speed rotary.
In this form of implementation, even the tap-off cycle T of oil pump
2And t between expulsive stage
2Along with engine speed change synchronously changes, also the t during the valve that opens of solenoid valve 35 can be made
1Not t between expulsive stage at oil pump
3More than and do not finish tap-off cycle T
2State under, open the valve period T corresponding to engine speed control electromagnetic valve 35
1And open valve ratio (dutycycle), increase with the delivery volume that makes lubricant oil along with the rising of engine speed.
That is, when relatively turning round with the middling speed of Figure 12 during the revolution of the low speed of Figure 11 as can be known, in oil pump, along with the rising of engine speed, tap-off cycle T
2Synchronously from T
2aT shortens
2b, accompany t between expulsive stage therewith
2Also from t
2aT shortens
2bRelative therewith, solenoid valve open t during the valve
1Also from t
1aT shortens
1b, to be formed on the not t between expulsive stage of oil pump
3More than and do not finish tap-off cycle T
2On the other hand, it opens the valve period T
1From T
1aT shortens
1b
Equally, relatively during the revolution of the middling speed of Figure 12 during with the high speed rotary of Figure 13 as can be known, in oil pump, along with engine speed rising, tap-off cycle T
2Synchronously from T
2bT further shortens
2c, accompany t between expulsive stage therewith
2Also from t
2bT further shortens
2cRelative therewith, solenoid valve open t during the valve
1From t
1bT further shortens
1c, to be formed on the not t between expulsive stage of oil pump
3More than and do not finish tap-off cycle T
2On the other hand, it opens the valve period T
1From T
1bT further shortens
1c
Like this, in this form of implementation, when rise the tap-off cycle T of oil pump along with engine speed
2And t between expulsive stage
2When synchronously shortening, shorten on the one hand the t during the valve that opens of solenoid valve 35
1To remain on the not t between expulsive stage of oil pump
3More than and do not finish tap-off cycle T
2, on the other hand, open the valve period T by shortening it
1Open t during the valve with increase
1Occurrence frequency, increase t between the expulsive stage of oil pump
2The t during the valve that opens with solenoid valve
1The coincidence number of times, thereby increase oil supply amount.
In other words, in this form of implementation, has such feature: during driving valve, be the not t between expulsive stage of oil pump
3More than and do not finish tap-off cycle T
2Scope in, open valve ratio (dutycycle) along with what the rising of engine speed improved solenoid valve.
Figure 14 illustrates an example of the solenoid valve dutycycle control mode of this form of implementation, wherein, and along with dutycycle is improved in the rising piecewise of engine speed.In addition, Figure 15 illustrates the engine speed in this form of implementation and the relation of oil supply amount and above-mentioned solenoid valve dutycycle, and is therefrom as can be known, unanimous on the whole with the oil supply amount of this form of implementation shown in the solid line and target delivery volume shown by dashed lines.
As mentioned above, according to this form of implementation, need not make the t during the valve that opens of solenoid valve
1Extend to the oily tap-off cycle T of oil pump
2More than, and need not make solenoid valve open the valve period T
1Cripetura is to t between the oily expulsive stage of oil pump
2Below, can increase oil supply amount along with the rising of engine speed, so, no matter how many engine speed is, all can suitably control oil supply amount often.
According to the present invention, can reach following such effect. (1) no matter the discharge week of oil pump Phase T2What are, always make the t during the valve that opens of magnetic valve1Not t between expulsive stage than oil pump3Long, and than tap-off cycle T2Short, so, needn't make the t during the valve that opens of magnetic valve1Especially long, nor must make out the valve cycle T1Especially short, can make the t during the valve that opens of magnetic valve1And oil t between expulsive stage2Must overlap, can control accurately oil supply amount. (2) because opening the valve phase at magnetic valve Between t1Not t between expulsive stage than oil pump3Long and than tap-off cycle T2Under the short state, along with starting What the rising of machine rotating speed improved magnetic valve opens the valve dutycycle, so, no matter how many engine speed is, Can be often with high accuracy control oil supply amount.
Claims (5)
1. the lubricating fitting of a mobile engine, be used for the lubricant oil supply engine of oil pump being discharged off and on, it is characterized in that: have opening of above-mentioned solenoid valve is controlled at the not above and do not finish control gear in the scope of tap-off cycle between expulsive stage of above-mentioned oil pump during the valve by solenoid valve.
2. the lubricating fitting of mobile engine as claimed in claim 1, it is characterized in that: above-mentioned control gear is controlled the valve cycle of opening of above-mentioned solenoid valve and is opened the valve ratio corresponding to engine speed, to increase the delivery volume of lubricant oil along with the rising of engine speed.
3. the lubricating fitting of mobile engine as claimed in claim 2 is characterized in that: above-mentioned control gear along with the rising of engine speed shorten above-mentioned solenoid valve drive valve during, and improve and open the valve ratio.
4. as the lubricating fitting of claim 2 or 3 described mobile engines, it is characterized in that: above-mentioned control gear is along with the rising of engine speed improves opening the valve cycle of above-mentioned solenoid valve.
5. as the lubricating fitting of any one described mobile engine in the claim 1～4, it is characterized in that: above-mentioned oil pump with synchronous cycle of engine speed removal of lubricant off and on.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP348549/97 | 1997-12-03 | ||
| JP34854997A JP3709957B2 (en) | 1997-12-03 | 1997-12-03 | Lubricating device for vehicle engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1218870A true CN1218870A (en) | 1999-06-09 |
| CN1090279C CN1090279C (en) | 2002-09-04 |
Family
ID=18397770
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN98122805A Expired - Fee Related CN1090279C (en) | 1997-12-03 | 1998-11-26 | Lubricating device for vehicle engine |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP3709957B2 (en) |
| CN (1) | CN1090279C (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102076999A (en) * | 2008-06-24 | 2011-05-25 | 玛格纳动力传动系统股份及两合公司 | Method and device for lubricating a transmission of a motor vehicle |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2024120124A (en) * | 2021-07-12 | 2024-09-04 | 日立Astemo株式会社 | Variable Hydraulic Control System |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DK171974B1 (en) * | 1988-11-01 | 1997-09-01 | Mitsubishi Heavy Ind Ltd | Lubricator for a cylinder in an internal combustion engine |
| US5355851A (en) * | 1992-02-10 | 1994-10-18 | Yamaha Hatsudoki Kabushiki Kaisha | Lubricating oil supplying system for two cycle engine |
-
1997
- 1997-12-03 JP JP34854997A patent/JP3709957B2/en not_active Expired - Fee Related
-
1998
- 1998-11-26 CN CN98122805A patent/CN1090279C/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102076999A (en) * | 2008-06-24 | 2011-05-25 | 玛格纳动力传动系统股份及两合公司 | Method and device for lubricating a transmission of a motor vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH11166408A (en) | 1999-06-22 |
| CN1090279C (en) | 2002-09-04 |
| JP3709957B2 (en) | 2005-10-26 |
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