CN100342123C - Engine retarder device having an opening-height variable exhaust valve - Google Patents
Engine retarder device having an opening-height variable exhaust valve Download PDFInfo
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- CN100342123C CN100342123C CNB2005100571884A CN200510057188A CN100342123C CN 100342123 C CN100342123 C CN 100342123C CN B2005100571884 A CNB2005100571884 A CN B2005100571884A CN 200510057188 A CN200510057188 A CN 200510057188A CN 100342123 C CN100342123 C CN 100342123C
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Abstract
The present invention discloses an engine retarder device with an open height variable exhaust door, which comprises a driving piston, a driving spring, a spacing pin, a one-way valve and relevant oil channels, wherein the driving piston is used for controlling the rebound of an exhaust door. Through making use of the rebound, the exhaust door keeps in a throttling open degree to throttle and release air in a cylinder. In addition, as the present invention is provided with an oil draining channel, the present invention can make an engine adjust throttle open degrees formed by the exhaust door according to the rotary speed within the range of the full rotary speed of the engine. When the engine operates at high speed, the throttle open degree of the exhaust door is large. When the engine operates in low speed, the throttle open degree of the exhaust door is small. Therefore, the engine can send ideal brake force under each rotary speed. In addition, because of the existence of the oil drainage channel, the present invention has simple and novel structure and makes the acquirement of lower height of the engine be possible.
Description
Technical field
The present invention relates to a kind of mechanical hydraulic unit of controlling the engine exhaust port motion, be specifically related to the engine retardation apparatus of exhauxt valve opens alterable height; Its typical application makes motor send brake horsepower vehicle is slowed down on four-journey reciprocating piston internal combustion engine.
Background technique
Modern vehicle, particularly heavy truck, motorbus in implementing the process of slowing down, cause the drag friction by-product to give birth to a large amount of heats because the sole mass and the quality of being loaded are big, and this brings the hidden danger that is absolutely unsafe to driving.Therefore the retarder of vehicle mounting auxiliary brake deceleration seems very necessary.Our country is widely used at present is exhaust butterfly-valve slowing down speed of engine, is that a dish control valve unit is installed in the waste pipe road.After the dish valve cuts out, in outlet pipe, form a pressure that is much higher than under the normal working of engine situation, make motor at the exhaust stroke consumed energy, absorb the energy (kinetic energy or potential energy) of vehicle with this.
But the braking force of exhaust butterfly-valve slowing down speed of engine is limited, can only satisfy the braking deceleration requirement under the vehicle sections road conditions.Can adopt the measure that improves the engine exhaust back pressure to improve the braking force of motor.But the raising of exhaust back pressure is subjected to the restriction of engine exhaust port return spring, if exhaust back pressure is set up De Taigao, the pressed gas in the outlet pipe can be washed the exhaust valve that is in the intake stroke cylinder open, and this phenomenon is commonly called as the exhaust valve knock-on.
The exhaust valve knock-on brings influence can for the safe handling of motor.After exhaust valve is opened by pressed gas, gas in the outlet pipe can flow into corresponding cylinder and make pressure decline in the outlet pipe, thereby cause exhaust valve under the effect of return spring, to be closed again, but closing of this moment is not to be subjected to the control of exhaust valve driving cam, exhaust valve and air valve seat ring can produce the strong impact of taking a seat, and this impacts and can damage exhaust valve and seat ring.
U. S. Patent 3367312,3547087,4662332,5215054,5335636,5647319,6594996 discloses and has severally utilized the exhaust valve throttling to discharge gases in the cylinder in compression stroke, allows the structural principle and the method for motor produce power net loss with this.
U. S. Patent 5692469 disclosed structures are to utilize exhaust valve to bounce to make exhaust valve form a Lift (see figure 1) in compression stroke.This patent structure is to be provided with a hydraulic piston 6 between rocking arm 3 and exhaust valve 1, the pressure lubrication oil of motor is supplied with hydraulic piston 6 by oil duct 18, oil duct 16 and one-way valve 17, a draining hole 20 feeds the hydraulic pressure cavity of hydraulic piston 6, and draining hole 20 is by a bulb sealing that is positioned at the adjusting screw 22 on the fixing cantilever 21.When exhaust dish valve close make motor enter braking state after, pressure in the outlet pipe just rises, exhaust valve 1 is opened by this pressure in intake stroke, the knock-on of generation valve, after exhaust valve 1 is opened by pressurized gas, pressure lubrication oil in the oil duct 18 is just pushed one-way valve 17 open and is promoted driven plunger 6 and stretches out, and the distance that driven plunger 6 is stretched out is by spacing part 14 restrictions.When exhaust valve 1 touches hydraulic piston 6 in knock-on finishes the return process, pressure in the hydraulic pressure cavity raises rapidly, one-way valve 17 sealing of taking a seat, produce the fluid power self-locking in the hydraulic pressure cavity, hydraulic piston 6 just stops exhaust valve 1 and makes it to form an aperture, and after motor entered compression stroke, this aperture was just carried out throttling to the gas in the cylinder and discharged, just there has not been the energy return piston during to expansion stroke in the cylinder, motor produce power net loss; Then motor enters expansion stroke, drive rocking arm 3 setting in motions at expansion stroke latter end exhaust valve, draining hole 20 broke away from and contacted with the bulb of adjusting screw 22 and lose sealing this moment, lubricant oil in the hydraulic pressure cavity just flows out under the active force of valve return, hydraulic piston 6 resets, and finishes the one action circulation.
Fig. 2 is the exhaust valve motion profile of 5692469 disclosed its controls.Exhaust valve 1 certain in intake stroke of motor a bit, under the effect of exhaust back pressure, opened by pressed gas, reach its knock-on maximum opening B, exhaust valve 1 return is closed then, stopped by hydraulic piston 6 in closing closed procedure and form a Lift C that this aperture lasts till the initial point of exhaust stroke always.As can be seen: when compression stroke, the Lift of exhaust valve is a fixed value C, and this Lift does not change with the rotating speed of motor.
Analyze the gas flow process of motor in compression stroke is passed through exhaust valve throttling release cylinder, can know: when motor enters braking state and is in high rotating speed, because absolute period of exhaust is short, just require exhaust valve to keep big Lift, if the aperture of the exhaust valve that retarder is controlled is little, then the pressed gas in the cylinder has little time throttling and discharges, and when the expansion stroke of motor energy return engine piston, cause the Braking efficiency of motor to descend.On the contrary, when motor is in the slow-speed of revolution, because absolute period of exhaust is long, just require exhaust valve to keep little Lift, if the aperture of the exhaust valve that retarder is controlled is big, then the throttling release pressure of being set up in the cylinder is with little, and this also can cause the Braking efficiency of motor to descend.Therefore, the Lift of exhaust valve should change with the rotating speed of motor is different, strengthens the exhauxt valve opens height when rotating speed is high, reduces the exhauxt valve opens height when rotating speed is low.This is the problem that needs solution, in existing patented technology, does not relate to this problem.
Summary of the invention
The problems referred to above at present slowing down speed of engine existence, the object of the present invention is to provide a kind of Lift of engine exhaust port in compression stroke that make, can be in the full speed range of motor, the engine retardation apparatus of adjusting according to the size of engine speed.
Further aim of the present invention is to provide a kind of engine retardation apparatus simple in structure, with low cost.
Realize above-mentioned purpose, the present invention adopts following technical proposals: a kind of engine retardation apparatus of exhauxt valve opens alterable height, and the exhaust valve that it is directly installed on motor drives in the driven plunger hole of rocking arm, and acts on the exhaust valve; Described engine retardation apparatus comprises driven plunger, driving spring, one-way valve and oil duct, and driven plunger is arranged in the driven plunger hole, and the two forms hydraulic space; Its improvement is: establish circumferential groove in its end portion and radial direction through hole on the driven plunger; Drive fuel feeding road on the rocking arm aim at circumferential groove in its end portion and and the connection of driven plunger hole; One end of driven plunger is established axial bore, establishes axial oilhole in the bottom of axial bore and passes to radial direction through hole; The other end of driven plunger is established the arc surface that cooperates with exhaust valve; In the driven plunger aperture to being provided with limit pin hole; If position limit pin passes radial direction through hole; Limit pin hole interference fit on position limit pin two ends and the driven plunger hole;
If one-way valve is being pressed under the effect of spring on the aperture in axial oil hole; Also establish driving spring in the axial bore, an end is pressed on the bottom in driven plunger hole, and the other end is pressed in the bottom of axial bore;
In the hydraulic space zone of driven plunger and the formation of driven plunger hole, the draining passage is set.
Described draining passage is the draining hole that is axially set on the bottom in driven plunger hole.
Perhaps described draining passage for letting out of being provided with on the driven plunger to the draining hole of the lubricating oil bath of motor or letting out of being provided with on the driven plunger to the draining hole of low pressure oil duct or utilize driven plunger and the driven plunger hole between the gap form the draining passage and let out to the low pressure oil duct.
Perhaps, described draining passage is the draining hole of being located on the one-way valve.
The every cylinder of the applied motor of apparatus of the present invention has one by cam-actuated exhaust valve, and the motion between cam and the exhaust valve is by transmission such as push rod and rocking arms, and the exhaust valve return spring makes exhaust valve keep closing under the situation that is not subjected to external force; Also have a dish control valve unit in this waste pipe road and improve exhaust back pressure, exhaust valve is opened by this pressure until the pretightening force that overcomes the exhaust valve return spring.By a draining passage is set, the Lift of engine exhaust port can be adjusted in the full speed range of motor automatically, and make the lower motor height of acquisition become possibility in the structure of the present invention.The present invention is novel ingenious, reasonable in design, simple in structure, has that volume is little, an advantage such as light weight, with low cost, reliable operation, and mounting arrangements is also very convenient, is suitable for promoting the use.
Description of drawings
Fig. 1: prior art constructions principle schematic.
Fig. 2: the exhaust valve Motion curves schematic representation of existing techniques in realizing.
Fig. 3: the structural principle schematic representation of apparatus of the present invention braking state.
The A-A cross section view of Fig. 4: apparatus of the present invention Fig. 3.
Fig. 5: the structural principle schematic representation of apparatus of the present invention acting state.
Fig. 6: the exhaust valve Motion curves schematic representation that apparatus of the present invention realize.
Fig. 7: the structural principle schematic representation of another embodiment's braking state of apparatus of the present invention.
Fig. 8: apparatus of the present invention the 3rd mode of execution draining passage is provided with position view.
Fig. 9: apparatus of the present invention the 4th mode of execution draining channel position schematic representation.
Figure 10: apparatus of the present invention the 5th mode of execution draining channel position schematic representation.
Figure 11: apparatus of the present invention the 6th mode of execution draining channel position schematic representation.
Embodiment
The invention will be further described below in conjunction with the drawings and specific embodiments.
As Fig. 3, Fig. 4, shown in Figure 5, apparatus of the present invention comprise driven plunger 54, position limit pin 60, one-way valve 78, driving spring 66, draining hole 72 etc., it is directly installed on the exhaust rocker arm 3 of an internal combustion engine and aims at the exhaust valve 1 of motor, under the driving of push rod 4 with exhaust rocker arm 3 motions.
The lubrication system (not shown) of motor by pitman arm shaft 50 to the fuel feeding road 18 supply pressure lubricant oil that are arranged in exhaust rocker arm 3, processing driven plunger hole 8 and fuel feeding road 18 are communicated with on the valve end of exhaust rocker arm 3, upwards add T limit pin hole 63 (see figure 4)s in the footpath in driven plunger hole 8.Position limit pin 60 is arranged in limit pin hole 63, the two interference fit; Position limit pin 60 passes radial direction through hole 58.
One end of driving spring 66 is pressed on the bottom 76 in driven plunger hole 8, and the other end is pressed in the bottom of axial bore 64.
One-way valve 78 is on the aperture that is pressed in axial oil hole 62 under the effect of spring 74 and seal.
In the bottom 76 in driven plunger hole 8 axial draining hole 72 is set, draining hole 72 is communicated with hydraulic space 73 with engine lubrication oil sump (not shown).
Analyze the working procedure of apparatus of the present invention below, what Fig. 3, Fig. 4 represented is that apparatus of the present invention are in the engine braking working state, and shown in Figure 6 is the exhaust valve Motion curves schematic representation that apparatus of the present invention realize.
After exhaust dish valve (not shown) was closed on the engine exhaust pipeline, the gas pressure in the outlet pipe increased, and causes exhaust valve 1 to be washed open by pressed gas in intake stroke downwards, and the A1 curve among Fig. 6 is seen in the motion of exhaust valve 1.Low pressure lubricant oil in the oil duct 18 just flows to axial oilhole 62 by circumferential groove in its end portion 56, radial direction through hole 58, enter in the hydraulic space 73 at the active force pusher opening one-way valve 78 that overcomes spring 74, together driven plunger 54 is released to the direction of exhaust valve 1 with driving spring 66, touch position limit pin 60 up to radial direction through hole 58, gap 68 is formed on 76 of the bottoms in the end 70 of driven plunger 54 and driven plunger hole 8 at this moment; The low pressure lubricant oil that other has a fraction flows back to the lubricating oil bath of motor by draining hole 72, and it should be noted that: the diameter in draining hole 72 is very little, and the oil mass of being leaked under engine lubrication system pressure is minimum, is not enough to cause that pressure descends.
After the pressed gas in the gas exhaust piping flow to the cylinder (not shown) by exhaust valve 1, its pressure descended gradually, caused exhaust valve 1 to be closed under the effect of return spring (not shown) at last.Close in the closed procedure at exhaust valve 1, when it touches the driven plunger 54 of having stretched out, one-way valve 78 sealing of taking a seat, lubricant oil generation fluid power self-locking in the hydraulic space 73, stopping exhaust valve 1 closes, make exhaust valve 1 keep one initial opening E (see figure 6), this initial opening is the poor of gap 68 and emission valve clearance.Because exhaust valve 1 acts on the driven plunger 54, causes the pressure in the hydraulic space 73 to increase the formation high pressure greatly, under this high pressure, the lubricant oil in the hydraulic space 73 is by draining hole 72 flow direction engine lubricating oil baths.
Motor remains in operation, draining hole 72 continues draining, cause exhaust valve 1 to reduce Lift gradually, in ensuing compression stroke, the Lift of exhaust valve 1 continues to reduce (seeing A2 curve among Fig. 6), and formed Lift carries out throttling to the gas in the cylinder and discharges in gas exhaust piping, when motor enters expansion stroke, just do not had pressed gas in the cylinder, thereby motor produce power net loss is sent brake horsepower.
Motor enters expansion stroke, and drainings are continued in draining hole 72, and exhaust valve 1 continues to reduce Lift, when closing, because the effect of adjacent cylinder, causes exhaust valve 1 bounce once more (seeing A3 curve among Fig. 6).Driven plunger 54 is stretched out until limited pin 60 spacing by aforementioned working procedure once more.After the gas in the outlet pipe is imported cylinder, exhaust valve 1 cuts out, in closing closed procedure, touch driven plunger 54, the fluid power self-locking takes place in hydraulic space 73, stopping exhaust valve 1 closes, make exhaust valve 1 keep one initial opening E (see figure 6), this initial opening is the poor of gap 68 and emission valve clearance.Because exhaust valve 1 acts on the driven plunger 54, cause the pressure in the hydraulic space 73 to increase the formation high pressure greatly, under this high pressure, the lubricant oil in the hydraulic space 73 is by draining hole 72 flow direction engine lubricating oil baths, and exhaust valve 1 reduces Lift (seeing A4 curve among Fig. 6) gradually.
Motor enters exhaust stroke, and push rod 4 begins to move upward and drives rocking arm 3, and rocking arm 3 is given the transmission of movement of push rod 4 driven plunger 54 and exhaust valve 1 and made it move downward (seeing curve A 5 among Fig. 6) together.In this process, draining is continued in draining hole 72, touches the bottom 76 in driven plunger hole 8 until the end 70 in D1 point (see figure 6) driven plunger 54.Driven plunger 54 is finished and is resetted.
When motor enters intake stroke exhaust valve generation knock-on once more, finish the one action circulation.
Shown in Figure 5 is that apparatus of the present invention are in motor acting state.
Behind exhaust dish opening of valves, the pressure recovery in the gas exhaust piping is to normal level, and this underpressure is bounced to cause exhaust valve 1.Oil duct 18 continues to it should be noted that to hydraulic space 73 supply pressure lubricant oil: in off position, the hydraulic coupling sum of the active force of driving spring 66 and driven plunger 54 generations is not enough to overcome the return spring power of exhaust valve 1.Lubricant oil in hydraulic space 73 leaks by draining hole 72, and until the end 70 of driven plunger 54 and the 76 formation gaps 80, bottom in driven plunger hole 8, motor promptly returns to normal acting pattern, and gap 80 promptly is the aforementioned emission valve clearance of mentioning.Because exhaust valve 1 does not bounce, driven plunger 54 can't promote exhaust valve 1 separately again, and the characteristics of motion of exhaust valve 1 just can not change, and it will be by the motion of the characteristics of motion under the normal acting pattern, i.e. curve A 6 among Fig. 6.The driven plunger 54 of this moment only plays the effect of a force transfer element, with the transmission of movement supply and exhaust door 1 of exhaust rocker arm 3.
Fig. 6 is the Motion curves schematic representation of the exhaust valve that produces of apparatus of the present invention.On behalf of motor, the continous curve of A1, A2, A3, A4, A5, A6 enter the Motion curves of braking state final vacuum door 1 under high rotating speed among the figure.Curve A 1 is the Motion curves of exhaust valve 1 when intake stroke bounces, exhaust valve 1 cuts out after the gas in the gas exhaust piping is imported cylinder immediately, close and be driven piston 54 controls in the closed procedure, exhaust valve 1 forms initial opening E at this moment, its value is poor for aforementioned gap 68 and gap 80, because the draining effect in draining hole 72, exhaust valve 1 reduce Lift gradually and form the A2 Motion curves; In compression stroke, the gas in 1 pair of cylinder of exhaust valve carries out throttling and discharges, and face amount is S during its exhaust, and motor produce power net loss is sent brake horsepower; In a certain moment in expansion stroke, exhaust valve 1 bounces once more, and promptly curve A 3, and exhaust valve 1 cuts out and be driven piston 54 controls by curve A 4 motions subsequently; Motor enters exhaust stroke immediately, draining hole 72 continues draining, and the lubricant oil in the hydraulic space 73 of naming a person for a particular job at D1 all leaks, and the end 70 of driven plunger 54 touches the bottom 76 in driven plunger hole 8, driven plunger 54 is finished and is resetted, and exhaust valve 1 continues motion by curve A 6; In ensuing intake stroke, finish the one action circulation when knock-on takes place again exhaust valve 1.On behalf of motor, the continous curve of A1 ', A2 ', A3 ', A4 ', A5 ', A6 enter the Motion curves of braking state final vacuum door 1 under the slow-speed of revolution among the figure.This Motion curves has identical mechanism with Motion curves under the high rotating speed, and difference is: the aperture of exhaust valve knock-on is smaller, and promptly the height point of A1 ', A3 ' curve hangs down; In addition, face amount S ' is littler than S when the exhaust that compression stroke forms; Be exactly that driven plunger 54 is finished the CAP point D2 difference that resets in addition.Understandablely be: when turning round under a certain rotating speed of motor between high and low rotating speed, the Motion curves of exhaust valve 1 is inevitable between aforementioned two curves, does not just draw here.As can be seen: when motor was braked under high rotating speed, face amount S was big when the formed exhaust of compression stroke, and corresponding is exactly the Lift height of exhaust valve 1; When motor was braked under the slow-speed of revolution, face amount S ' was little when the formed exhaust of compression stroke, and the Lift of corresponding is exactly exhaust valve 1 is low.
Why the Lift of exhaust valve 1 in compression stroke can change with the rotating speed of motor, is because apparatus of the present invention are provided with a draining passage---and be draining hole 72.The oil mass that this draining passage is leaked in each work cycle of device can change according to the difference of engine speed.
The oil mass that flows through draining hole 72 becomes a function relation with the pressure of aperture, draining hole, working medium with the endurance, available following formula is expressed, that is:
G＝f(φ，P，t)
In the formula: G is the dredge oil amount that flows through draining hole 72
φ is the aperture in draining hole 72
P is the pressure in the hydraulic space 73
T is the absolute time that draining continues
When apparatus of the present invention in actual applications behind the design typification, the aperture in draining hole 72 is just fixing, and the pressure P in the hydraulic space also can be treated to a constant value, like this, the dredge oil amount G of device in its every work cycle is just only relevant also linearly proportional with the absolute time that draining continues.And absolute time and engine speed that draining continues are closely related, and the absolute time that draining continued when rotating speed was high is short, and dredge oil amount is just little, cause exhaust valve 1 to produce a big Lift, promptly form big throttle opening; The absolute time that draining continued when rotating speed was low is long, and dredge oil amount is just big, causes exhaust valve 1 to produce a little Lift, promptly forms little throttle opening.
Shown in Figure 7 is another embodiment of apparatus of the present invention, is in opening state.The lubrication system (not shown) of motor by pitman arm shaft 50 to the fuel feeding road 18 supply pressure lubricant oil that are arranged in exhaust rocker arm 3, processing driven plunger hole 8 on the valve end of exhaust rocker arm 3, axial oilhole 80 and 18 connections of fuel feeding road are set in the bottom 76 in driven plunger hole 8, upwards process limit pin hole 63 (referring to Fig. 4) in the footpath in driven plunger hole 8.
Radial direction through hole 58 is set on the driven plunger 154; One end of driven plunger 154 is provided with axial bore 64, and the other end is provided with arc surface 52 and exhaust valve 1 cooperating.
The two ends of position limit pin 60 and limit pin hole 63 interference fit; Position limit pin 60 passes radial direction through hole 58.
One end of driving spring 66 is pressed on the bottom 76 in driven plunger hole 8, and the other end is pressed in the bottom of axial bore 64.
One-way valve 78 is on the aperture that is pressed in axial oil hole 80 under the effect of spring 74 and seal.
In the bottom 76 in driven plunger hole 8 axial draining hole 72 is set, draining hole 72 is communicated with hydraulic space 73 with engine lubrication oil sump (not shown).
Present embodiment and Fig. 3, Fig. 4 and embodiment illustrated in fig. 5ly have identical effect and a purpose, its working principle is in full accord, just is not repeated in this description in detail.It is different that just hydraulic space 73 obtains the oil circuit of lubricant oil, and present embodiment is that the axial oilhole 80 from the bottom 76 that is positioned at driven plunger hole 8 obtains, and this is readily appreciated that.
Draining hole 72 in prior figures 3, Fig. 4 and Fig. 5 structure, and the draining hole 72 in Fig. 7 structure is to be axially disposed within on the bottom 76 in driven plunger hole 8, the flow of lubricant that it leaked is to the lubricating oil bath of motor.Understandablely be: as long as the passage of draining is set in driven plunger 54 and driven plunger hole 8 formed hydraulic spaces 73, and the lubricant oil in the described space carried out suitable leakage, both can let out lubricating oil bath to motor, also can let out to low pressure oil duct (to the oil inlet passage zone of hydraulic space 73 fuel feeding), just can reach identical effect of aforementioned means and purpose.So, the draining passage not only can be arranged on the bottom in driven plunger hole 8; Draining hole 90 also can be set on driven plunger 54 lets out to the lubricating oil bath (see figure 8) of motor or draining hole 92 is set and let out to low pressure oil duct (see figure 9); Also can utilize gap 94 between driven plunger 54 and the driven plunger hole 8 to form the draining passage lets out to low pressure oil duct (see figure 10); Also can adopt the non-sphere one-way valve, let out to low pressure oil duct (seeing Figure 11) and draining hole 96 is set on this one-way valve.Because principle is identical with working procedure, does not just carry out the description of repetition here.
By the front to the structural principle of disclosed variable exhaust valve throttle opening device and the description of working procedure, as can be seen:
Be provided with a draining passage in the disclosed structure, make apparatus of the present invention, can in the full speed range of motor, the size according to engine speed adjust exhaust valve 1 formed throttle opening, make motor under each rotating speed, all send desirable Braking efficiency.Motor is when high rotation speed operation, and exhaust valve 1 formed throttle opening is big; When motor turned round in the slow-speed of revolution, exhaust valve 1 formed throttle opening was little.This is because the oil mass that the draining passage is leaked can change with the rotating speed of motor.When engine speed was high, because the draining absolute time is short, the oil mass of being leaked was just few, and exhaust valve 1 formed throttle opening is just big; When engine speed was hanged down, because the draining absolute time is long, the oil mass of being leaked was just many, and exhaust valve 1 formed throttle opening is just little.
In addition, because the existence of draining passage with regard to not needing to be provided with separately the resetting-mechanism of driven plunger 54, causes the structure of apparatus of the present invention very simple.Compare with 5692469 patents, saved the adjusting screw 22 and the relative mounting fixing parts of cantilever 21, dribbling head, and made the lower motor height of acquisition become possibility.
Can utilize disclosed oil drainage method that prior art is transformed, to reach disclosed effect and purpose.
Claims (4)
1, a kind of engine retardation apparatus of exhauxt valve opens alterable height, the exhaust valve that it is directly installed on motor drives in the driven plunger hole (8) of rocking arm (3), and acts on the exhaust valve (1); Described engine retardation apparatus comprises driven plunger (54), driving spring (66), one-way valve (78) and oil duct, and driven plunger (54) is arranged in driven plunger hole (8), and the two forms hydraulic space (73); It is characterized in that:
Establish circumferential groove in its end portion (56) and radial direction through hole (58) on the driven plunger (54); Drive fuel feeding road (18) on the rocking arm (3) aim at circumferential groove in its end portion (56) and and driven plunger hole (8) connection; One end of driven plunger (54) is established axial bore (64), establishes axial oilhole (62) in the bottom of axial bore (64) and passes to radial direction through hole (58); The other end of driven plunger (54) is established the arc surface (52) that cooperates with exhaust valve (1);
Radially be provided with limit pin hole (63) in driven plunger hole (8); If position limit pin (6 ()) passes radial direction through hole (58); Limit pin hole (63) interference fit on position limit pin (60) two ends and driven plunger hole (8);
If one-way valve (78) is being pressed under the effect of spring (74) on the aperture of axial oil hole (62); Also establish driving spring (66) in the axial bore (64), an end is pressed on the bottom (76) of driven plunger hole (8), and the other end is pressed in the bottom of axial bore (64);
In hydraulic space (73) zone of driven plunger (54) and driven plunger hole (8) formation, the draining passage is set.
2, engine retardation apparatus according to claim 1 is characterized in that: described draining passage is the draining hole (72) on the bottom (76) that is axially set in driven plunger hole (8).
3, engine retardation apparatus according to claim 1 is characterized in that: described draining passage for letting out of go up being provided with in driven plunger (54) to the draining hole (90) of the lubricating oil bath of motor or driven plunger (54) go up letting out of being provided with to the draining hole (92) of low pressure oil duct or utilize driven plunger (54) and driven plunger hole (8) between gap (94) form the draining passage and let out to the low pressure oil duct.
4, engine retardation apparatus according to claim 1 is characterized in that: described draining passage is the draining hole of being located on the one-way valve (96).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100571884A CN100342123C (en) | 2005-07-26 | 2005-07-26 | Engine retarder device having an opening-height variable exhaust valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100571884A CN100342123C (en) | 2005-07-26 | 2005-07-26 | Engine retarder device having an opening-height variable exhaust valve |
Publications (2)
| Publication Number | Publication Date |
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| CN1737352A CN1737352A (en) | 2006-02-22 |
| CN100342123C true CN100342123C (en) | 2007-10-10 |
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| CNB2005100571884A Expired - Fee Related CN100342123C (en) | 2005-07-26 | 2005-07-26 | Engine retarder device having an opening-height variable exhaust valve |
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Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
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| KR100974764B1 (en) * | 2006-12-15 | 2010-08-06 | 현대자동차주식회사 | Rocker Arm Mechanism for Cylinder Deactivation |
| US7823553B2 (en) * | 2007-03-16 | 2010-11-02 | Jacobs Vehicle Systems, Inc. | Engine brake having an articulated rocker arm and a rocker shaft mounted housing |
| US20100108007A1 (en) * | 2007-03-16 | 2010-05-06 | Jacobs Vehicle Systems, Inc. | Rocker shaft mounted engine brake |
| DE102008032774A1 (en) * | 2008-07-11 | 2010-01-14 | Man Nutzfahrzeuge Ag | Engine braking device and method for engine braking with a valve auxiliary control unit |
| CN102003239B (en) * | 2009-08-31 | 2012-11-28 | 上海尤顺汽车部件有限公司 | Quick-braking engine brake device |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5215054A (en) * | 1990-10-22 | 1993-06-01 | Jenara Enterprises Ltd. | Valve control apparatus and method |
| WO1993025803A1 (en) * | 1992-06-17 | 1993-12-23 | Ab Volvo | Method and device for motor-braking by means of a multi-cylinder internal combustion engine |
| US5692469A (en) * | 1995-04-04 | 1997-12-02 | Steyr Nutzfahrzeuge Aktiengesellschaft | Braking a four stroke IC engine |
| CN1556311A (en) * | 2004-01-03 | 2004-12-22 | 马银良 | Motor speed slower |
-
2005
- 2005-07-26 CN CNB2005100571884A patent/CN100342123C/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5215054A (en) * | 1990-10-22 | 1993-06-01 | Jenara Enterprises Ltd. | Valve control apparatus and method |
| WO1993025803A1 (en) * | 1992-06-17 | 1993-12-23 | Ab Volvo | Method and device for motor-braking by means of a multi-cylinder internal combustion engine |
| US5692469A (en) * | 1995-04-04 | 1997-12-02 | Steyr Nutzfahrzeuge Aktiengesellschaft | Braking a four stroke IC engine |
| CN1556311A (en) * | 2004-01-03 | 2004-12-22 | 马银良 | Motor speed slower |
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| CN1737352A (en) | 2006-02-22 |
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