CN2816383Y - Wariable-valve engine speed-reducer - Google Patents
Wariable-valve engine speed-reducer Download PDFInfo
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- CN2816383Y CN2816383Y CN 200520009803 CN200520009803U CN2816383Y CN 2816383 Y CN2816383 Y CN 2816383Y CN 200520009803 CN200520009803 CN 200520009803 CN 200520009803 U CN200520009803 U CN 200520009803U CN 2816383 Y CN2816383 Y CN 2816383Y
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- driven plunger
- piston sleeve
- draining
- engine
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Abstract
The utility model has disclosed a kind of changeable air valve slowing down speed of engine, comprises housing, solenoid valve, fuel feeding road, driven plunger assembly, spring sheet, adjusting screw; The utility model makes the sealing part of structure few owing to reduced the high-pressure oil passage zone, has improved sealing effectively; Make that by position limit pin the move distance of driven plunger can be guaranteed accurately; Adjust the appropriate location of driven plunger assembly in piston hole by adjusting screw, make that the gap between driven plunger and the exhaust valve can be guaranteed accurately; Like this, the initial Lift of exhaust valve just can be guaranteed accurately; A draining passage also is set, the Lift of engine exhaust port can be adjusted in the full speed range of motor automatically.
Description
Technical field
The utility model relates to a kind of engine braking apparatus, is specifically related to a kind ofly can change valve proper motion rule, thereby makes motor can send the changeable air valve slowing down speed of engine of brake horsepower, belongs to machinery manufacturing technology field.
Background technique
In the prior art, U. S. Patent 3547087,4662332,5215054,5335636,5647319,6594996 etc. discloses the structural principle and the method for several valve throttling engine speed reducers.These methods are to allow the exhaust valve of motor keep certain aperture (forming throttle opening) that the gas in the cylinder is carried out throttling release when compression stroke, make the loss of motor produce power.In these technological schemes, the throttle opening that exhaust valve keeps in compression stroke and the rotating speed of motor are not related, and no matter rotating speed just is a constant value.
If the throttle opening of exhaust valve in compression stroke changes with the rotating speed of motor, increase throttle opening during promptly high rotating speed, reduce throttle opening during the slow-speed of revolution, then motor can both send desirable braking force under each rotating speed.Chinese patent application number is: 200510057030.7 " valve throttling engine speed reducer " referring to shown in Figure 1, is that this artificial throttle opening of exhaust valve of realizing is with the variable invention of rotating speed.This structure causes the sealing part of structure many because the high-pressure oil passage zone is long; Its one-way valve 80 is arranged in the housing 2, causes oil duct 54, annular groove 20 to be the high-pressure area, makes piston sleeve 18 and piston hole 5 under high pressure can produce leakage.Exist structure inadequately rationally, controlling unit and means complexity in the production, defectives such as cost of production height.
The model utility content
At present valve throttling engine speed reducer above shortcomings, the purpose of this utility model is to provide a kind of simplified structure, improves sealing, the changeable air valve slowing down speed of engine that the throttle opening of engine exhaust port is adjusted according to the size of engine speed.
The further purpose of the utility model is to simplify the production technology of motivation retarder, reduces production costs.
Realize above-mentioned purpose, the utility model adopts following technical proposals: the changeable air valve slowing down speed of engine comprises housing, solenoid valve, fuel feeding road, driven plunger assembly, adjusting screw; The every cylinder of this motor has push rod and the driving rocking arm drives exhaust valve, exhaust valve has return spring makes it remain the trend of closing, the driven plunger assembly is located in the piston hole on the housing, the adjusting screw that is positioned on the housing is aimed in the upper end of driven plunger assembly, and lower end aligned drives the contact platform on the rocking arm;
The fuel feeding road is communicated with solenoid valve and the piston hole of being located on the housing, in the bottom of piston hole balance oil hole is set and passes to the engine lubrication oil sump;
The driven plunger assembly comprises piston sleeve, driven plunger, position limit pin and one-way valve; The piston sleeve periphery is provided with circumferential stepped annular groove, and orthogonal radial direction through hole and limit pin hole are set in annular groove; In the bottom in driven plunger hole the draining passage is set; At the top of piston sleeve setting drain pan and draining channel connection radially;
Driven plunger is arranged in the driven plunger hole, but unrestricted motion; Its lower end is provided with bulb and cooperates the work of contact platform, the return shaft shoulder is set applies returning place force by spring sheet; In its periphery circumferential groove in its end portion is set and aims at radial direction through hole and limit pin hole on the piston sleeve; Radial direction through hole is set in circumferential groove in its end portion; At its other end axial bore and axial oilhole are set, the two transition forms conical surface; Axially oilhole and radial direction through hole are communicated with;
If the two ends interference fit of position limit pin in limit pin hole, and is passed radial direction through hole on the driven plunger;
If an end of spring is positioned at the bottom in driven plunger hole, the other end one-way valve is pressed on the conical surface and seal shaft to oilhole.
Further improve and be the draining hole of described draining passage on piston sleeve, being provided with;
Perhaps the draining passage for the draining hole of the aligning adjusting screw that on piston sleeve, is provided with and with its in the current limliting pin established form; Also be provided with the retainer of current limliting pin in the bottom in driven plunger hole, become the axial bore and the axial hole of shoulder hole at the retainer upper mounted; The current limliting pin is arranged in axial bore;
Filter screen also is installed on annular groove to be filtered the engine lubricating oil that enters;
Further improving is that piston sleeve is a split-type structural, is made up of passing hole type piston sleeve and plug screw, and the two is by being threaded to one; The draining passage is set on the plug screw and drain pan radially is interconnected;
Described piston sleeve is that split-type structural also can and stop up and form by the passing hole type piston sleeve, and the two connects as one by interference fit; The draining passage is set in the obstruction and drain pan radially is interconnected.
The utility model makes the sealing part of structure few owing to reduced the high-pressure oil passage zone, has improved sealing effectively; Make that by position limit pin the move distance of driven plunger can be guaranteed accurately; When being assembled to the utility model device on the motor, adjust the appropriate location of driven plunger assembly in piston hole by adjusting screw again, make that the gap between driven plunger and the exhaust valve can be guaranteed accurately; Like this, when the utility model device was worked, the initial Lift of the exhaust valve that driven plunger is controlled just can be guaranteed accurately; A draining passage especially also is set in the utility model apparatus structure, the Lift of engine exhaust port can be adjusted in the full speed range of motor automatically.
The utility model is novel ingenious, reasonable in design, has advantages such as simple in structure, 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 structural representation.
Fig. 2: the structural representation of a cylinder of the utility model changeable air valve slowing down speed of engine.Be in closed condition.
Fig. 3: the structural representation of a cylinder of the utility model changeable air valve slowing down speed of engine.Be in opening state.
Fig. 4: the sectional view of driven plunger assembly 100 among Fig. 2.Be in closed condition.
Fig. 5: the A-A sectional view of driven plunger assembly 100 among Fig. 4.
Fig. 6: the sectional view of driven plunger assembly 100 among Fig. 3.Be in opening state.
Fig. 7: the Motion curves schematic representation of the exhaust valve that the utility model changeable air valve slowing down speed of engine is controlled.
Fig. 8: second mode of execution of piston sleeve in the utility model.
Fig. 9: the 3rd mode of execution of piston sleeve in the utility model.
Figure 10: second mode of execution of driven plunger assembly 100 in the utility model.
Figure 11: the 3 D stereo schematic representation of the drain pan 150 at piston sleeve 407 tops among Figure 10.
Embodiment
The utility model is described in further detail below in conjunction with the drawings and specific embodiments.
Fig. 2 or shown in Figure 3, the utility model changeable air valve slowing down speed of engine comprises housing 2, solenoid valve 66, fuel feeding road 72, driven plunger assembly 100, spring sheet 6, adjusting screw 36 etc.It is directly installed on the cylinder cap 3 of an internal combustion engine, the every cylinder of this motor has push rod 9 and driving rocking arm 13 drives exhaust valve 1, exhaust valve 1 has return spring 7 makes it remain the trend of closing, and drives rocking arm 13 and is provided with contact platform 11, and other structure of motor is not drawn.
The lubrication system (not shown) of motor is supplied with the lubricant oil of low pressure to solenoid valve 66 by oil input channel 68.Draining road 70 is communicated with solenoid valve 66 with engine lubrication oil sump (not shown).Fuel feeding road 72 is communicated with solenoid valve 66 and the piston hole 5 that is arranged on the housing 2.When solenoid valve 66 energising, the lubricant oil of low pressure flows through oil input channel 68, solenoid valve 66 and enters fuel feeding road 72; When solenoid valve 66 outages, when solenoid valve 66 ends oil input channel 68 fuel feeding road 72 and draining road 70 are communicated with, at this moment, the lubricant oil in the fuel feeding road 72 flows back to the engine lubrication oil sump through solenoid valve 66, draining road 70.
In the bottom of piston hole 5 lubricating oil bath that equalizing orifice 28 leads to motor is set.
Driven plunger assembly 100 is set in piston hole 5, and the adjusting screw 36 that is positioned on the housing 2 is aimed in the upper end of driven plunger assembly 100, and lower end aligned drives the contact platform 11 on the rocking arm 13.Adjusting screw 36 is locked by nut 34.
One end of spring sheet 6 is pressed on the return shaft shoulder 103 of driven plunger 105 (seeing Fig. 4, Fig. 5, Fig. 6) and applies returning place force, and the other end is fixed on the housing 2 by screw 4.
As Fig. 4, Fig. 5, shown in Figure 6, be the structure of driven plunger assembly 100, comprise piston sleeve 107, driven plunger 105, position limit pin 139, filter screen 115 and one-way valve 119 etc.
Axial driven plunger hole 109 is set in the inside of piston sleeve 107 and circumferential stepped annular groove 111 and annular groove 113 aligning oil ducts 72 is set, orthogonal radial direction through hole 145 and limit pin hole 143 are set in annular groove 113 in periphery; 115 pairs of engine lubricating oils that enter of filter screen are installed on annular groove 111 to be filtered; In the bottom in driven plunger hole 109 draining hole 127 is set; The drain pan 150 and the draining hole 127 that are provided with radially at the top of piston sleeve 107 are communicated with.
If the two ends interference fit of position limit pin 139 in limit pin hole 143, and is passed radial direction through hole 141 on the driven plunger 105, the difference in diameter of radial direction through hole 141 and position limit pin 139 is S0.
If an end of spring 121 is positioned at the bottom in driven plunger hole 109, the other end is pressed in one-way valve 119 on the conical surface 135 and seals.
Formed definition space is a hydraulic space 128 between driven plunger 105, one-way valve 119 and the driven plunger hole 109.
Analyze the working procedure of the utility model changeable air valve slowing down speed of engine below:
What Fig. 2, Fig. 4, Fig. 5 represented is that the utility model changeable air valve slowing down speed of engine is in closed condition.
Give solenoid valve 66 outages, when oil input channel 68 is cut off, fuel feeding road 72 and draining road 70 are communicated with, flow of lubricant in the fuel feeding road 72 loses pressure to the engine lubrication oil sump, lubricant oil in the hydraulic space 128 leaks away the back by draining hole 127 and just can't be replenished, spring sheet 6 is upwards pressed to position limit pin 139 with driven plunger 105, make radial direction through hole 141 touch position limit pin 139, thereby piston sleeve 107 is pressed on the adjusting screw 36, the bulb 101 of driven plunger 105 forms gap S1 with contacting to disengage between the platform 11, and retarder keeps closed condition.This moment, motor was not influenced by any of retarder by normal acting mode operation, and it drives rocking arm 13 and there is a valve clearance S2 in 1 of exhaust valve.
Fig. 3, shown in Figure 6 is that the utility model changeable air valve slowing down speed of engine is in opening state.
In service at vehicle, give solenoid valve 66 energisings, draining road 70 is cut off, the lubricant oil of low pressure just passes through solenoid valve 66 from oil input channel 68, fuel feeding road 72, annular groove 111, filter screen 115, annular groove 113, radial direction through hole 145, circumferential groove in its end portion 117, radial direction through hole 141, axial oilhole 137 and flow to one-way valve 119, behind the active force that overcomes spring 121 and push one-way valve 119 open, thereby flow in the hydraulic space 128, promote driven plunger 105 and move downward behind the active force that overcomes spring sheet 6, other has a fraction of lubricant oil to flow to drain pan 150 by draining hole 127, the bottom of piston hole 5, balance oil hole 28 and flow back to the lubricating oil bath of motor.After driven plunger 105 is crossed gap S1, if motor is in exhaust stroke, then driven plunger 105 continues to move downward up to limited pin 139 spacing preventions, otherwise will touching contact platform 11 and promote rocking arm 13, the bulb 101 of driven plunger 105 crosses stop motion behind the S2 of gap, wait for that motor enters exhaust stroke, just continue then to move downward, up to limited pin 139 spacing preventions.Motor remains in operation, in the closed procedure of the pass of exhaust valve 1, when contact platform 11 touches the bulb 101 of driven plunger 105, because the active force of return spring 7 acts on the driven plunger 105, the pressure of lubricant oil in the hydraulic space 128 is increased rapidly, the sealing thereby one-way valve 119 is taken a seat, driven plunger 105 just stops exhaust valve 1 and closes, make exhaust valve 1 form an initial opening S3, S3=S0-S1-S2.Because pressure increases in the hydraulic space 128, makes lubricant oil flow through the bottom of drain pan 150, piston hole 5, the lubricating oil bath that balance oil hole 28 flows back to motor by draining hole 127 under this pressure.Motor remains in operation, and draining hole 127 continues draining, makes exhaust valve 1 reduce Lift gradually, up to entering compression stroke.In compression stroke, draining is continued in draining hole 127 makes the Lift of exhaust valve 1 continue reduction, formed Lift carries out throttling to the gas in the cylinder and is discharged in the gas exhaust piping, when motor enters expansion stroke, just there has not been pressed gas in the cylinder, thereby motor produce power net loss is sent brake horsepower.
When motor entered exhaust stroke once more, driven plunger 105 was stretched out under lubricating oil pressure again, finished the one action circulation.In each circulation, stop exhaust valve 1 from exhaust stroke latter end driven plunger 105, finish the lubricants capacity that flows out by draining hole 127 in during this period of time and the diameter and a function relation of delivery time existence in the pressure in the hydraulic space 128, draining hole 127 up to compression stroke.Behind design typification, the diameter in pressure in the hydraulic space 128 and draining hole 127 just can be treated to a constant, and the lubricants capacity of outflow is just only linearly proportional with the delivery time.And the delivery time is relevant with engine speed, and the rotating speed height is the delivery time weak point then, and the lubricants capacity of outflow is just few, and the Lift of exhaust valve 1 is just big, also is that throttle opening is big; The low then delivery time of rotating speed is long, and the lubricants capacity of outflow is just many, and the Lift of exhaust valve 1 is just little, also is that throttle opening is little.
Shown in Figure 7, be the Motion curves schematic representation of the utility model valve throttling engine speed reducer exhaust valve.Curve 300 is Motion curvess of motor exhaust valve when high rotating speed among the figure, and curve 400 is Motion curvess of motor exhaust valve when the slow-speed of revolution.When turning round under a certain rotating speed of motor between high and low rotating speed, its Motion curves is inevitable between curve 300 and curve 400, i.e. curve among the figure 500.S3 represents the initial opening of exhaust valve 1 among the figure, corresponding to the gap S3 among Fig. 3.By correlation curve 300 and curve 400, as can be seen: when motor was braked under high rotating speed, formed exhaust valve throttle opening was big in compression stroke; When motor was braked under the slow-speed of revolution, formed exhaust valve throttle opening was little in compression stroke.
As Fig. 8, shown in Figure 9, expression piston sleeve 107 is a split-type structural, and the function of overlapping with Fig. 4, Fig. 5 and one-piece piston shown in Figure 6 is on all four, and the effect that reaches is also suitable.Among Fig. 8: piston sleeve is made up of passing hole type piston sleeve 207 and plug screw 147, and the two is by being threaded to one; On passing hole type piston sleeve 207, be provided with as identical driven plunger hole 109, limit pin hole 143, radial direction through hole 145 and ladder annular groove 111,113 among Fig. 4, Fig. 5 and Fig. 6; Draining hole 127 is set on plug screw 147 and drain pan radially 150 is interconnected.Among Fig. 9: piston sleeve is made up of passing hole type piston sleeve 307 and obstruction 247, and the two connects as one by interference fit; On passing hole type piston sleeve 307, be provided with as identical driven plunger hole 109, limit pin hole 143, radial direction through hole 145 and ladder annular groove 111,113 among Fig. 4, Fig. 5 and Fig. 6; On 247 draining hole 127 is set and drain pan radially 150 is interconnected stopping up.
In Fig. 4, Fig. 5, Fig. 6, Fig. 8 and the structure shown in Figure 9, be provided with draining hole 127 and finish draining, draining hole 127 can be interpreted as a draining passage, the lubricant oil in the hydraulic space 128 leaks away by this draining passage, finishes the purpose of the throttle opening of adjusting exhaust valve 1.
Shown in Figure 10, be another embodiment of draining passage, have same purpose with previous embodiment.Compare with prior figures 4, Fig. 5, Fig. 6, Fig. 8 and structure shown in Figure 9, in the structure shown in Figure 10,127 increasings of former draining hole are become draining hole 227, in draining hole 227, insert current limliting pin 125 then, for set current limiting pin 125, at the hydraulic space 128 inner retainers 123 that increase, all the other structures are in full accord.Axial draining hole 227 is set on piston sleeve 407 aims at adjusting screw 36, and the drain pan 150 (seeing Figure 11) that is provided with radially is communicated with draining hole 227; One end of spring 121 is pressed in the bottom in driven plunger hole 109 with retainer 123, and the other end is pressed in one-way valve 119 on the conical surface 135; Establish axial bore 129 and axial hole 131 on retainer 123, the two forms shoulder hole; The stream pin 125 of limiting is arranged in draining hole 227, and inserts simultaneously in the axial bore 129 of retainer 123, and the lower end of current limliting pin 125 is spacing by the ladder that axial bore 129 and axial hole 131 form, and the upper end is spacing by adjusting screw 36.Lubricant oil in the hydraulic space 128 can flow to drain pan 150 by axial hole 131, axial bore 129 and draining hole 227 under pressure after current limliting pin 125 current limlitings, thereby flows back to the lubricating oil bath of motor.The working principle of present embodiment and process and aforesaid working principle and process are in full accord, just are not repeated in this description here.
Same reason can be designed to piston sleeve 407 Fig. 8, split-type structural shown in Figure 9.
By the front to the changeable air valve slowing down speed of engine structural principle that the utility model disclosed and the description of working procedure, as can be seen:
Be provided with a position-limit mechanism and a regulating mechanism in the throttling engine speed reducer structure that the utility model disclosed, position-limit mechanism makes that the move distance (being gap S0) of driven plunger 105 can be guaranteed accurately; In the time of on slowing down speed of engine fit on motor, regulating mechanism makes that the gap S1 between driven plunger 105 and the exhaust valve 1 can be guaranteed accurately.When the utility model device was worked, the initial Lift S3 of the exhaust valve 1 that driven plunger 105 is controlled just can be precisely controlled like this.
In addition, also be provided with a draining passage in the structure that the utility model disclosed, make the changeable air valve slowing down speed of engine that the utility model disclosed, 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 force.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.Therefore, retarder of the present utility model can have been given play to desirable Braking efficiency in the full speed range of motor, and the retarder of prior art can only be at motor have been given play to desirable Braking efficiency under some or two rotating speeds.The oil drainage method that can utilize the utility model to disclose is transformed prior art, and exhaust valve 1 formed throttle opening is changed with the rotating speed of motor.
Claims (6)
1, a kind of changeable air valve slowing down speed of engine comprises housing (2), solenoid valve (66), fuel feeding road (72), driven plunger assembly (100), adjusting screw (36); The every cylinder of this motor has push rod (9) and driving rocking arm (13) drives exhaust valve (1), exhaust valve (1) has return spring (7) makes it remain the trend of closing, driven plunger assembly (100) is located in the piston hole (5) on the housing (2), the adjusting screw (36) that is positioned on the housing (2) is aimed in the upper end of driven plunger assembly (100), and lower end aligned drives the contact platform (11) on the rocking arm (13); It is characterized in that:
Fuel feeding road (72) is communicated with solenoid valve (66) and the piston hole (5) be located on the housing (2), in the bottom of piston hole (5) balance oil hole (28) is set and passes to the engine lubrication oil sump;
Driven plunger assembly (100) comprises piston sleeve (107), driven plunger (105), position limit pin (139) and one-way valve (119); Piston sleeve (107) periphery is provided with circumferential stepped annular groove (111,113), and orthogonal radial direction through hole (145) and limit pin hole (143) are set in annular groove (113); Bottom in driven plunger hole (109) is provided with the draining passage; At the top of piston sleeve (107) setting drain pan (150) and draining channel connection radially;
Driven plunger (105) is arranged in driven plunger hole (109), but unrestricted motion; Its lower end is provided with bulb (101) and cooperates contact platform (11) work, the return shaft shoulder (103) is set applies returning place force by spring sheet (6); In its periphery circumferential groove in its end portion (117) is set and aims at radial direction through hole (145) and limit pin hole (143) on the piston sleeve (107); Radial direction through hole (141) is set in circumferential groove in its end portion (117); At its other end axial bore (133) and axial oilhole (137) are set, the two transition forms conical surface (135); Axially oilhole (137) and radial direction through hole (141) are communicated with;
If the two ends interference fit of position limit pin (139) in limit pin hole (143), and is passed radial direction through hole (141) on the driven plunger (105);
If an end of spring (121) is positioned at the bottom of driven plunger hole (109), the other end one-way valve (119) is pressed in that the conical surface (135) is gone up and seal shaft to oilhole (137).
2, slowing down speed of engine according to claim 1 is characterized in that: described draining passage is for going up the draining hole (127) that is provided with at piston sleeve (107);
3, slowing down speed of engine according to claim 1 is characterized in that: described draining passage is in the draining hole (227) of the aligning adjusting screw (36) that piston sleeve (407) upward is provided with and the current limliting pin of establishing in it (125) forms; Also be provided with the retainer (123) of current limliting pin (125) in the bottom of driven plunger hole (109), become the axial bore (129) and the axial hole (131) of shoulder hole at retainer (123) upper mounted; Current limliting pin (125) is arranged in axial bore (129);
4, according to claim 1,2 or 3 described slowing down speed of engine, it is characterized in that: go up installation filter screen (115) at described annular groove (111) engine lubricating oil that enters is filtered;
5, slowing down speed of engine according to claim 4 is characterized in that: described piston sleeve (107,407) is a split-type structural, is made up of passing hole type piston sleeve (207) and plug screw (147), and the two is by being threaded to one; The draining passage is set on the plug screw (147) and drain pan radially (150) is interconnected;
6, slowing down speed of engine according to claim 4 is characterized in that: described piston sleeve (107,407) is a split-type structural, is made up of passing hole type piston sleeve (307) and obstruction (247), and the two connects as one by interference fit; Stop up and on (247) the draining passage to be set and drain pan radially (150) is interconnected.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200520009803 CN2816383Y (en) | 2005-08-18 | 2005-08-18 | Wariable-valve engine speed-reducer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200520009803 CN2816383Y (en) | 2005-08-18 | 2005-08-18 | Wariable-valve engine speed-reducer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2816383Y true CN2816383Y (en) | 2006-09-13 |
Family
ID=36996192
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200520009803 Expired - Lifetime CN2816383Y (en) | 2005-08-18 | 2005-08-18 | Wariable-valve engine speed-reducer |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2816383Y (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102493877A (en) * | 2011-11-17 | 2012-06-13 | 东风朝阳柴油机有限责任公司 | Diesel engine exhaust braking device for heavy-duty vehicle |
| CN113931712A (en) * | 2021-09-30 | 2022-01-14 | 东风商用车有限公司 | Rocker arm assembly with variable valve lift |
-
2005
- 2005-08-18 CN CN 200520009803 patent/CN2816383Y/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102493877A (en) * | 2011-11-17 | 2012-06-13 | 东风朝阳柴油机有限责任公司 | Diesel engine exhaust braking device for heavy-duty vehicle |
| CN113931712A (en) * | 2021-09-30 | 2022-01-14 | 东风商用车有限公司 | Rocker arm assembly with variable valve lift |
| CN113931712B (en) * | 2021-09-30 | 2023-06-02 | 东风商用车有限公司 | Rocker arm assembly with variable valve lift |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term |
Expiration termination date: 20150818 Granted publication date: 20060913 |
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| EXPY | Termination of patent right or utility model |