CN1115002A - Two-stroke engine oil metering fump - Google Patents
Two-stroke engine oil metering fump Download PDFInfo
- Publication number
- CN1115002A CN1115002A CN95107193.9A CN95107193A CN1115002A CN 1115002 A CN1115002 A CN 1115002A CN 95107193 A CN95107193 A CN 95107193A CN 1115002 A CN1115002 A CN 1115002A
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- China
- Prior art keywords
- cam
- distributor
- oil
- distributor body
- 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
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- 239000010705 motor oil Substances 0.000 title claims description 14
- 239000003921 oil Substances 0.000 claims description 64
- 238000000605 extraction Methods 0.000 claims description 13
- 239000010721 machine oil Substances 0.000 claims description 11
- 239000000945 filler Substances 0.000 claims description 7
- 230000000694 effects Effects 0.000 claims description 6
- 238000007493 shaping process Methods 0.000 claims description 4
- 230000008676 import Effects 0.000 claims description 3
- 238000006073 displacement reaction Methods 0.000 abstract description 10
- 238000005086 pumping Methods 0.000 abstract description 4
- 239000000314 lubricant Substances 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000003068 static effect Effects 0.000 description 4
- 239000010687 lubricating oil Substances 0.000 description 3
- 230000003321 amplification Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000003199 nucleic acid amplification method Methods 0.000 description 2
- 239000000758 substrate Substances 0.000 description 2
- 230000001174 ascending effect Effects 0.000 description 1
- 239000010725 compressor oil Substances 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000005764 inhibitory process Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B7/00—Piston machines or pumps characterised by having positively-driven valving
- F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
- F04B7/06—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports the pistons and cylinders being relatively reciprocated and rotated
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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
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- 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
- F16N13/04—Adjustable reciprocating pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Reciprocating Pumps (AREA)
- Production Of Liquid Hydrocarbon Mixture For Refining Petroleum (AREA)
Abstract
The pump includes a distributor body in which there is a pumping chamber whose volume is variable by virtue of the fact that said distributorcan be displaced axially, said variation being produced as a consequence of the fact that, inside the chamber, there is a stationary piston pushed against a cover by means of a spring which in turn pushes the actual distributor in the opposite direction. Said distributor body, in addition to the alternating axial displacement, is subjected to a rotary movement in order to allow alternating communication of the inlet and outlet with the actual pumping chamber, the rotary movement being produced by means of a worm which meshes with a toothing integral with the actual distributor, whilst the axial displacement is produced by contact of a cam formed in the lower part of the distributor which alternately and at every half rotation comes into contact against the cam or the cam formed on a shaft perpendicular to the axial shaft of the distributor.
Description
The present invention relates to a kind of two-stroke engine oil metering fump, the lubricant oil that infeeds motor in this pump is according to the rotating speed continuous control of motor, and the aperture of this fuel delivery and engine charge control valve is adapted, also comprise the pump oil return line of lubricant oil and the loop of oil gas mixed steam independently with it in this pump.
Can see that in the prior art some have the oil metering fump of rotation or reciprocal distributor, the distribution plunger that links to each other with a gear in these pumps is driven by toroidal helical, thereby cause the motion of distributor, have the oil pipe outlet of side on the described distributor.In U. S. Patent W-1279480 and W-1568170, can see above-mentioned feature.
Adopting a static plunger also is known technology, and an available cam and cam follower compressor oil pump chamber in this type of device just can reach the effect of pump oil.For example in B. P. 801667, just can see this class formation.
A kind of like this oil pump structure is provided in the U. S. Patent 3353492, and camshaft wherein is arranged on the changeable angular orientation.
Two kinds of engine motor oil suction boosters have been described in the U. S. Patent 4231716 and 4797073, these two kinds of pumps all suck relevant with the volume of discharge side with machine oil, owing in chamber, be provided with a static plunger with respect to a movable body that constitutes distributor, so said engine oil sucks and the volume of discharge side can change, one end one of a said apparatus and a spring works and plunger is pressed against seal on the lid of distributor body, and the other end of spring is then pushed down the distributor body along opposite direction.
Also comprise a gear that is contained on the distributor in the pump of above-mentioned these two U. S. Patents, this gear is driven by a toroidal helical, so that distributor rotates, oil stream just can flow into chamber and make it subsequently to be forced out like this, this rotation of distributor combines with axial motion and can realize control to liquid stream (being oil stream at this), so as during the engine operation all the time the needs according to its slewing rate be lubricated.
Among the 4231716 pump embodiments that provided in above-mentioned two U. S. Patents, distributor comprises two parts: one of them part has a pivot pin, and this pin is arranged in the groove, and described groove is arranged on the base of another part of distributor; Described another part is relative with above-mentioned first portion, is provided with a pivot pin at an end relative with cam, and this cam is connected with push rod or axle on function, and described push rod or axle meet at right angles with the axle of distributor.
Need described distributor to have two parts in this system, all has optional feature in each part, so that part is down below rotated, and cam produces after the motion, make top part can produce displacement, cavity volume just can change like this, thus the lubricant oil oil stream of the motor that control sucks and discharges.
4797073 of U. S. Patents have the device the same with foregoing patent, a controlling rod is supporting on the projection that is arranged on the distributor bottom, so that control, described controlling rod also links to each other with a spring, this spring can make controlling rod change its position according to the rotation of distributor, so that it breaks away from control at any time, and between the projection of distributor bottom and push rod, push, therefore, even it is effective that this system looks, controlling rod and other parts obviously also need very high accuracy of manufacturing, assembly precision is to realize infeeding liquid stream or the oily effective control of flowing that motor is lubricated.
In addition, act on the radial force on the distributor in addition in above-mentioned two described pumps of U. S. Patent, this radial force has caused the internal leakage of centrifugal force and machine oil, owing to pump must be worked under the state of heat, so the problem of leaking can obtain certain inhibition.
Will be appreciated that, the reliability of this pump not only depends on the gap between distributor and its housing, and depend on centrifugal force in this gap, because under special back pressure effect, oil extraction during the stage in its housing the lubricating oil leakage amount in the fully eccentric distributor than high about 7 times of the lubricating oil leakage amount in the uninfluenced distributor.It should be noted that, above-mentioned lubricating oil leakage and the leakage rate in plunger must deduct from the volume of pump displacement, so just can determine actual flow, even when motor is in rated temperature work and very serious leakage is arranged, also should so calculate for obtaining suitable flow, when motor is worked at low temperatures, because the oily flow of the increase of engine oil viscosity and output surpasses the required amount of normal engine operation, so the leakage of this moment almost completely disappears.
The invention provides a kind of pump that can address the above problem, it is simple in structure and effective, and the scheme of its solution depends on the distributor of axial displacement and used cam.
Specifically, pump of the present invention comprises a camming, this camming setting or be molded on the camshaft, so that on a plate cam, produce a tangential effect, this plate cam-shaped is formed in the substrate or the bottom of distributor, so the centrifugal force of distributor is less than the centrifugal force of other type of pump, to as described in the description of those patents, the effect of a radial component is arranged in the pump of other type as the front.
In camming of the present invention, no matter which kind of material it adopts and how to handle, can allow cam that certain wearing and tearing are arranged and can not reduce its reliability greatly, the cam of distributor is along 50% slip of the cam of axle, in all cases, if lift is very little, the load that then acts on the spring of plunger can not change significantly.
The lift of pump and discharge capacity only depend on camshaft, and the reliability of this pump is compared with existing pump with validity and is greatly improved.
Distributor can move back and forth so that chamber in Volume Changes, described chamber be by it on its under pump structure form, described chamber is coupled together by the pipeline that makes progress.
Basic principle and structure as for camming of the present invention, it should be noted that and in the substrate of distributor, be provided with a flat half cam, this cam contacts with one molded lines in above-mentioned two cams, one in two above-mentioned cams is actuating cam, another then is the oil-feed cam, they all are provided with or shape on camshaft, and camshaft is below the distributor longitudinal axis.
The reliability of pump means that the flow that is provided is directly proportional with the slewing rate of motor substantially when each engine throttle is opened, and is continuous and increases with accelerator open degree corresponding to the described flow of each rotating speed.
In another embodiment, metering pump also can be used as an oil flow rate proportioning device, and this flow is only relevant with the rotating speed of motor, and is directly proportional with it.
For the relation between quantitative pump structure and it and other parts of motor, it should be noted that, this pump has the power of an input shaft, described this has another axle of fixed drive ratio to link with engine crankshaft or with this bent axle, and the engine rotation rate signal is received by this pump shaft.
A connecting line links to each other with the accelerator drive unit, it just drives a pump rod with the stroke identical with drive unit like this, to change the oil flow rate that under any one engine speed, is infeeded, this means, under a specific engine speed, can cause the flow of machine oil from the minimum to the maximum, to change continuously according to certain rules to Throttle Opening Control.
In a word, the machine oil stream that is produced will be directly proportional with the lift of oil extraction stroke, and is promptly corresponding with the displacement of distributor, and the oil extraction stroke equates that with the oil-feed stroke they all are to be determined by the distance between two parallel planes.These two planes and oil-feed cam and actuating cam are tangent, and these two planes are all perpendicular with the axle of distributor.Obviously in half cam during along the horizontal cam slide of above-mentioned two formation and camshaft, described these two tangent planes are relevant with the position of the half cam of distributor.
Cam on the camshaft is selected suitable molded lines for use, can change the lift (being the displacement of distributor) of distributor very naturally, distance between this displacement and above-mentioned two parallel planes adapts, and camshaft is rotated, the change of camshaft angle position will provide at every turn the volume of the pump oil that changes by existing rule like this, like this, under a given engine speed, the speed of toroidal helical axle and speed and distributor has also just been determined thereupon, the oil level of discharging just can be controlled according to the angular orientation of camshaft, because this camshaft is associated with the motion of accelerator drive unit again, so the load of motor is big more, the oil flow rate that provides is just big more.
In the embodiment of another pump of the present invention, described flow is only relevant with the slewing rate of motor, the velocity ratio of its direct ratio and toroidal helical one gear shaft, and also be directly proportional with oil pumping body is long-pending.This is because in this embodiment, the molded lines of camshaft comprises two circles, and in this case, the motion of this camshaft and motor accelerator is irrelevant, the difference of two radius of a circles has formed a fixing lift of distributor, thereby has constituted the fixed pump oil volume.
Also need in some cases with a pump to two different parts fuel feeding, promptly be used for one of two cylinders (cylinder, an inlet air compressor) independently lubrication system.In this case, infeed Lubricants stream in above-mentioned each parts can be identical, also can be different.
In this case, according to another characteristic of the invention, be provided with a distributor in the cylindrical shell of valve body, provide following three kinds with the distributor chamber to contact in this distributor: one is and the contacting of import, and two other is and leads to contacting the outlet of lubricated above-mentioned two parts.Be arranged on the half cam of also setting up a plane on the distributor base on the camshaft, the part that comprises two 90 degree in this cam with different in width, have three cams on the described camshaft, the i.e. actuating cam of the oil-feed cam of a centre and two ends, one in two actuating cams contacts with the distributor cam in its whole stroke all the time, and another then only contacts with the wideest that 1/4 in the distributor cam.
After adopting this structure, when chamber and oil inlet pipe connection, distributor is reduced to extreme lower position, sucks the machine oil of certain volume according to the situation of chamber and oil inlet pipe, its outlet from each oil outlet tube is discharged subsequently, each oil outlet tube is by the two-jawed appropriate section of distributor again.
In order to have one comprehensively to understand and abundant and explanation to characteristics of the present invention, existing these accompanying drawings are illustrative, but not invention is introduced all-sidely in conjunction with the accompanying drawings, wherein:
Fig. 1 is the side view of two-stroke engine oil metering fump of the present invention;
Fig. 2 is another side view of pump shown in the preceding figure, the figure shows a side relative with last figure;
Fig. 3 is a side view all inequality with preceding two figure, and this figure and the former two are rectangular, and cuts open for the part of pump and to show, to show its internal structure;
Fig. 4 is the planimetric map that the pump shown in above-mentioned each figure is cut open along horizontal plane;
Fig. 5 is the sectional drawing along the amplification of the A among Fig. 1-B line, has represented the profile of the formed cam in distributor bottom among the figure, and the setting of two cams on the camshaft, and described camshaft is across on this distributor;
Fig. 6 is and the similar side view of Fig. 1, but metering pump wherein can provide two kinds of different oil masses;
Fig. 7 is another side view of pump shown in Figure 6, the figure shows a side on the other side;
Fig. 8 is and Fig. 6 and Fig. 7 side view all inequality, and this figure and the former two are rectangular, and cuts open for the part of pump and to show, to show its internal structure;
Fig. 9 is the planimetric map that the pump shown in Fig. 6-8 is cut open along horizontal plane;
Figure 10 is the sectional drawing along the amplification of the A among Fig. 6-B line, has represented the profile of the formed cam in distributor bottom among the figure, and the setting of two cams on the camshaft, and described camshaft is across on this distributor;
Figure 11,12 and 13 has schematically shown each working procedure of cam set, their respectively corresponding oil-feed process, the beginning of oil extraction for the first time and beginnings of oil extraction for the second time.
Referring to each is schemed as mentioned above, this pump generally includes a general pump housing 1, have an import 2 and an outlet 3 on the pump housing, the top of pump has a lid 4, this lid is compressed by a plunger 5 that is positioned at chamber 6 all the time, described chamber is formed on the distributor 7, be characterized in that plunger 5 is pressed in the thrust of covering on 4 and is provided by spring or helical member 8, described spring 8 is in the end of this plunger 5 and be equipped with between the bottom of chamber 6 of this plunger, and spring also is pressed on the body 7 of distributor in opposite direction.
Have in the bottom of described distributor body 7 sides one all the time with the gear 9 or the toothed surfaces of helical toothing.
As shown in Figure 5, bottom or bottom at distributor body 7 also are provided with a tool half cam 11, and two cams 12 that process on the lateral rotation bar 14 and 13 can suitably be against on the above-mentioned cam 11, described lateral rotation bar and distributor body 7 at right angles.
The plunger 5 that is positioned at chamber 6 is static, even chamber 6 also is like this when having variable volume.When chamber was variable volume, distributor body 7 should carry out axial displacement, to change the volume of chamber 6.
Because plunger 5 is static as mentioned above, all the time Jie Chu lid 4, distributor 7 are just had to along the axial or parallel with it direction to-and-fro motion of plunger 5, to change volume, thereby discharge machine oil, they also have second kind of forms of motion in addition, promptly rotate, so that chamber 6 is connected with filler opening 2 in the oil-feed stroke, is connected with oil outlet 3 in the oil extraction stroke.
As mentioned above, rotatablely moving of distributor body 7 is to produce owing to gear 9 and toroidal helical 10, and all these is to be connected with pipeline 16 in the oil-feed stroke, to be connected with pipeline 17 in the oil extraction stroke for the pipeline in the distributor 7 15 can make pump chamber 6.Pipeline 16 directly is connected with filler opening 2, and pipeline 17 directly is connected with oil outlet 3.
The oil extraction stroke begins when plate cam 11 contacts with the molded lines of cam 13 greatly.Plate cam 11 is plane semicircle and the bottom that is arranged on distributor 7, and cam 13 then is the so-called actuating cam of machine shaping on camshaft 14.In the oil extraction stroke, the tension force that distributor 7 overcomes spring 8 moves upward, thereby discharges the oil stream of respective volume.
Greatly the oil-feed stroke begins when the half cam 11 of distributor 7 makes it to contact with cam 12 by actuating cam 13 and spring tension.Cam 12 is also referred to as the oil-feed cam, and also machine shaping on camshaft 14.In the oil-feed stroke, distributor moves downward, and the volume of pump chamber increases, thereby sucks oil stream.
The ascending amount of distributor was directly proportional when the oil that said process produced flowed with the oil extraction stroke, oil extraction stroke and oil-feed stroke equate, they all are to be determined by the distance between two parallel tangential planes, in these two planes one 12 tangent with the oil-feed cam, another and actuating cam 13 are tangent, but they are all perpendicular to the axis of distributor 7, like this when the semicircle cam 11 of distributor 7 as mentioned above when two cams 12 and 13 slide, cam 11 is positioned on these two tangential planes.
In the embodiment of another pump, cam 12 and 13 molded lines can be substituted by two circles.Be associated with the motion of motor accelerator pedal before camshaft 14 needn't resemble in this case, and two radius of a circle differences should limit a constant lift to distributor, thereby have a fixed pump oil volume.Adopt the pump of this structure can make oil stream only relevant with the slewing rate of motor, it is proportional to the gear ratio of toroidal helical and gear shaft, and it is long-pending also to be proportional to oil pumping body.
Toroidal helical 10 is preferably disposed on the specified input shaft 18 of motor.
Referring to the embodiment shown in Fig. 6-13, pump also is provided with the pump housing 21, filler opening 22 and a pair of oil outlet 23-23 ', covering 24 pairs of pump housings seals, lid 24 is arranged on the fixing plunger (25) all the time, this plunger is arranged in the cavity 26 of distributor 27, be positioned at described chamber (26) with the plunger 25 of spring 28 1 same-actions and promote distributor 27 and push down and cover 24, the surface of described distributor 27 has the transmission device 29 of crown shape, and rotatablely moving by its transmission toroidal helical 30, the inside of distributor 27 is provided with a pipeline 31, this pipeline according to each constantly distributor 27 the angular orientation successively with chamber 26, pipeline 32, pipeline 33 or pipeline 33 ' are connected.Pipeline 32 joins with filler opening 22, and pipeline 33 joins with oil outlet 23, and pipeline 32 ' then joins with oil outlet 23 '.
For finishing said structure, with a plane double-cam 34-35 is arranged with lid on 24 opposed bottom surface on the pump 27, wherein bigger part has 90 degree arguments, less part also has 90 degree arguments, camshaft 36 then also is arranged on below this two-jawed as previously mentioned, the special way of present embodiment is to have three cams on this camshaft 36, i.e. oil-feed cam 37, first actuating cam 38 and second actuating cam 39.
Shown in Figure 11-13, structure according to this, in each circulation (being the complete once motion of distributor 27) of pump, distributor 27 at first has the lift of a maximum, so that the volume minimum that chamber 26 is limited, 34 on the wideest cam of distributor this moment is in the camshaft bottom, when above-mentioned cam portion 34 leaves cam 39, distributor 27 moves downward the limit position of bottom under the effect of spring 28, cam portion 35 is supported by oil-feed cam 37 herein, and machine oil flows into from filler opening 22 by pipeline 31; Cam 34 just arrives actuating cam 38 after turning over 90 degree, and distributor 27 upwards rises, and the volumes in the chamber 26 reduce like this, exports 23 thereby cause machine oil to flow to first by pipeline 31; Described subsequently cam 34 arrives the cam 39 that axle is gone up higher position, has so just obtained secondary pump oil, because the angular displacement of distributor 27, the pipeline 31 on it has just forwarded second oil outlet 23 ' to and located.
Obviously can realize the contacting of cam and cam 34-35 on the camshaft by the position, angle of adjusting camshaft 36, and the oil mass that flows out by two pipelines also can be changed, although because the camshaft element is circular, so the flow of exporting in two pipelines is only relevant with slewing rate, be not subjected to the influence of the angular orientation of camshaft 36, and needing only the flow sum of exporting in two pipelines always adapts with the flow of importing, so, the ratio of the flow of exporting in these two pipelines can be any value.
Claims (7)
1, two-stroke engine oil metering fump, it comprises a distributor body (7), this body constitutes the chamber (6) of a variable volume, has a plunger (5) in the chamber, plunger (5) is pushed down the lid (4) of the pump housing all the time by a spring (8), the other end of spring (8) is pushed down distributor body (7) along opposite direction, have a gear that is meshed with toroidal helical (10) or profile of tooth side surface (9) on the distributor body, described toroidal helical links to each other with corresponding engine-driving axle, the rotation of the distributor body (7) that gear-rack gear produced can make pump chamber (6) be connected with import (2) and outlet (3), distributor body (7) thus rotatablely move to work and change the volume of pump chamber (6) with axial motion one, the invention is characterized in: the cam plate of a semicircle (11) is arranged on the lower end of distributor body (7), this cam can replace with the cam (12) of going up machine shaping at camshaft (14) and contacting with (13), camshaft (14) is across on distributor body (7), and it is rectangular with the axis of this body, it is each when engine throttle is opened, substantially the oil stream that is directly proportional with the slewing rate of motor just can be provided, and described oily stream is continuous and increases with throttle under each rotating speed.
2, two-stroke engine oil metering fump as claimed in claim 1, it is characterized in that: go up the cam (12) of machine shaping and the combination that (13) can be multiple cam profile at camshaft (14), rule with the rule that forms various distributor lifts and pump oil volume, these rules have been considered the factor of an outside pull bar relevant with carburetor throttle opening, the rule of this lift can be any corresponding curve, as straight line, oblique line.
The combination of horizontal line or various line styles, cam (12) and (13) produce tangential effect in distributor, thereby make distributor only be subjected to very little centrifugal force in its body, and the internal leakage of machine oil also can be minimum.
3, two-stroke engine oil metering fump as claimed in claim 1, it is characterized in that: being arranged on the semi-circular cam (11) of distributor body (7) bottom respectively is 50% with cam (12) and contacting of (13) on taking shape in camshaft (14) successively, also can not produce very big influence to its reliability even cam (12) and (13) have produced certain wearing and tearing.
4, as the described two-stroke engine oil metering fump of one of claim 1 to 3, it is characterized in that: the formed pump chamber of housing (6) by this plunger in plunger (5) and the distributor body (7) is communicated with a side pipe (16), this side pipe extends to the cylindrical outer surface of distributor always, in the oil-feed stage, pipeline (16) and the oil inlet pipe (15) that is arranged in the housing of distributor body (7) are connected, in the fuel-displaced stage, another and pipeline (16) are the pipeline (17) of about 180 degree as oil outlet tube.
5, as the described two-stroke engine oil metering fump of one of claim 1 to 4, it is characterized in that: fuel-displaced and oil-feed stroke respectively by the cam (11) on the distributor body (7) and cam (13) and (12) alternately contact determine, when cam (13) and cam (11) when contacting, pump chamber (6) volume reduces, and machine oil is discharged; And when cam (12) and cam (11) when contacting, distributor body (7) moves downward, thereby makes the volume increase of chamber (6) just correspondingly suck machine oil.
6, as the described two-stroke engine oil metering fump of one of above-mentioned every claim, it is characterized in that: the molded lines of cam (12) and (13) is circular, so that a fixed pump oil volume to be provided,, the oil that pumps is directly proportional with the rotational velocity of motor thereby only being flowed.
7, two-stroke engine oil metering fump, it comprises a distributor body (27), this body constitutes the chamber (26) of a variable volume, has a plunger (25) in the chamber, plunger (25) is pushed down the lid (24) of the pump housing all the time by a spring (28), the other end of spring (28) is pressed letter distributor body (27) along opposite direction, have a gear that is meshed with toroidal helical (30) or profile of tooth side surface (29) on the distributor body, described toroidal helical links to each other with corresponding engine-driving axle, the rotation of the distributor body (27) that gear one rack gear is produced can make pump chamber (26) be connected with filler opening and oil outlet, distributor body (27) thus rotatablely move to work and change the volume of pump chamber with axial motion one, the invention is characterized in: also have a duct (31) on the valve formula distributor (27), then have respectively three ducts (32) that are connected with filler opening (22) and each oil outlet (23-23 ') on the valve body (21), (33-33 '), the bottom of distributor (27) is provided with a plane double-cam, this cam has the argument of 180 degree altogether, but have two parts that width is different on the cam, one of them wide portions (34) has 90 degree arguments, and another narrower part (35) also has 90 degree arguments, and with the contacted auxiliary cam axle of the double-cam (34-35) of distributor (27) (36) on have a central oil-feed cam (37) and two end cams (38) and (39), first cam in these two cams is discharged oil stream to first oil outlet (23), second cam then discharged oil stream to second oil outlet (23 '), wider portion (34) in distributor (27) overhead cam can only contact with (39) with two fuel-displaced cams (38), and part (35) narrower in this cam then can only contact with oil-feed cam (37) with the first oil extraction cam (38).
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| ES9401231 | 1994-06-06 | ||
| ES9401231A ES2116841B1 (en) | 1994-06-06 | 1994-06-06 | OIL DOSING PUMP FOR TWO-STROKE ENGINES. |
| ES009500987A ES2125136B1 (en) | 1994-06-06 | 1995-05-23 | DOSING OIL PUMP FOR TWO-TIME ENGINES. |
| ES9500987 | 1995-05-23 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1115002A true CN1115002A (en) | 1996-01-17 |
| CN1064738C CN1064738C (en) | 2001-04-18 |
Family
ID=26154794
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN95107193A Expired - Fee Related CN1064738C (en) | 1994-06-06 | 1995-06-06 | Two-stroke engine oil metering fump |
Country Status (5)
| Country | Link |
|---|---|
| CN (1) | CN1064738C (en) |
| DE (1) | DE19520321A1 (en) |
| ES (1) | ES2125136B1 (en) |
| FR (1) | FR2721684B1 (en) |
| IT (1) | IT1275302B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102679123A (en) * | 2012-05-14 | 2012-09-19 | 唐作晚 | Engine oil compression pump |
| CN112896077A (en) * | 2021-01-06 | 2021-06-04 | 杭州电子科技大学 | Flexible flat soft liquid material conveying mechanism for automobile fuel cell |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19808887A1 (en) * | 1998-03-03 | 1999-09-09 | Dolmar Gmbh | Hand tool with 2-stroke internal combustion engine and separate lubrication as well as a combined feed / metering pump for such a hand tool |
| US8162632B2 (en) | 2007-09-28 | 2012-04-24 | Brp Us Inc. | Fluid pump |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2739671A (en) * | 1953-02-12 | 1956-03-27 | Dewandre Co Ltd C | Lubricating devices |
| US3302752A (en) * | 1964-10-21 | 1967-02-07 | Yamaha Motor Co Ltd | Lubricating pump for two-cycle gasoline internal combustion engine |
| DE2362194C3 (en) * | 1973-12-14 | 1978-06-08 | Audi Nsu Auto Union Ag, 7107 Neckarsulm | Lubricant metering pump |
| US4043711A (en) * | 1975-04-24 | 1977-08-23 | Mikuni Kogyo Kabushiki Kaisha | Lubricating oil pump |
| JPS59145311A (en) * | 1983-02-07 | 1984-08-20 | Honda Motor Co Ltd | Lubricating oil pump of 2-cycle engine |
| US4632648A (en) * | 1985-06-24 | 1986-12-30 | Goyne Thomas S | Grease pumps |
| US4971532A (en) * | 1989-06-02 | 1990-11-20 | Brunswick Corporation | Oil metering pump with air purge |
-
1995
- 1995-05-23 ES ES009500987A patent/ES2125136B1/en not_active Expired - Fee Related
- 1995-06-02 FR FR9506600A patent/FR2721684B1/en not_active Expired - Lifetime
- 1995-06-02 DE DE19520321A patent/DE19520321A1/en not_active Withdrawn
- 1995-06-05 IT ITMI951163A patent/IT1275302B/en active IP Right Grant
- 1995-06-06 CN CN95107193A patent/CN1064738C/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102679123A (en) * | 2012-05-14 | 2012-09-19 | 唐作晚 | Engine oil compression pump |
| CN102679123B (en) * | 2012-05-14 | 2015-03-11 | 唐作晚 | Engine oil compression pump |
| CN112896077A (en) * | 2021-01-06 | 2021-06-04 | 杭州电子科技大学 | Flexible flat soft liquid material conveying mechanism for automobile fuel cell |
| CN112896077B (en) * | 2021-01-06 | 2023-01-24 | 杭州电子科技大学 | Flexible flat soft liquid material conveying mechanism for automobile fuel cell |
Also Published As
| Publication number | Publication date |
|---|---|
| ITMI951163A0 (en) | 1995-06-05 |
| ES2125136A1 (en) | 1999-02-16 |
| DE19520321A1 (en) | 1995-12-07 |
| ITMI951163A1 (en) | 1996-12-05 |
| FR2721684A1 (en) | 1995-12-29 |
| CN1064738C (en) | 2001-04-18 |
| FR2721684B1 (en) | 1997-08-14 |
| ES2125136B1 (en) | 2000-05-01 |
| IT1275302B (en) | 1997-08-05 |
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