CN201666172U - System for actuating engine valve - Google Patents
System for actuating engine valve Download PDFInfo
- Publication number
- CN201666172U CN201666172U CN2009201555346U CN200920155534U CN201666172U CN 201666172 U CN201666172 U CN 201666172U CN 2009201555346 U CN2009201555346 U CN 2009201555346U CN 200920155534 U CN200920155534 U CN 200920155534U CN 201666172 U CN201666172 U CN 201666172U
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- engine braking
- rocking arm
- valve
- arm
- engine
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Abstract
The utility model relates to a system for actuating an engine valve, which comprises a rocker shaft, an engine brake rocker, a valve cross arm, a sliding pin, a cam and a spring; the rocker shaft is provided with a control liquid supply channel; the engine brake rocker can be pivoted on the rocker shaft, and is provided with central openings which are deployed around the rocker shaft, hydraulic channels which connect the central openings and control valves and liquid channels which connect the control valves and actuating piston components; the valve cross arm extends between a first engine exhaust valve and a second engine exhaust valve; the sliding pin is arranged on the valve cross arm, the sliding pin contacts with the first engine exhaust valve, and the actuating piston components contact with the sliding pin; the cam is used for applying actuation operation for engine braking to the engine brake rocker; and the spring biases the engine brake rocker to contact with the cam. According to the utility model, the engine valve can be actuated simply in high efficiency.
Description
Technical field
The utility model relates to the system that is used for start internal-combustion engine valve, relates in particular to the start exhaust valve so that realize the system of engine braking.
Background technique
Internal-combustion engine use usually machinery, valve actuating system electronics or hydraulic machinery comes the start engine valve.These systems can comprise the combination of camshaft, rocking arm and push rod, and they are driven by the rotation of engine crankshaft.When camshaft is used for the start engine valve, the time that can determine the valve start by the size and the position of salient angle on the camshaft.
For each 360 degree rotation of camshaft, motor is finished whole circulations (expansion just,, exhaust, air inlet and compression) of being made up of four strokes.During the major part of the piston expansion stroke of advancing away from the cylinder cylinder cap (just, the volume between cylinder cylinder cap and the piston crown increases), intake valve and exhaust valve all are closed and keep closing therein.In positive (positive power) operation, fuel combustion and carry positive during expansion stroke by motor.Expansion stroke finishes at lower dead centre, and at this moment, piston reverses direction and exhaust valve can be opened so that carry out main exhaust event.When piston is upwards advanced, but the salient angle synchronous operation on the camshaft is carried out main exhaust event and is forced combustion gas to leave cylinder to open exhaust valve.
Positive operation for internal-combustion engine needs above-mentioned main exhaust valve incident.Sometimes may wish has other auxiliary valve event, although optional.For example, may wish that the start exhaust valve is used for compression-release engine braking, bleeder type engine brake, exhaust gas recirculation (EGR), brake gas recirculation (BGR) or other auxiliary valve event.
About auxiliary valve event, the someone adopts the FLOW CONTROL of the waste gas of the internal-combustion engine of flowing through to control vehicle engine braking is provided.Usually, engine braking system may command exhaust-gas flow is with combination compression-release type braking principle, and exhaust gas recirculation, exhaust pressure are regulated and/or the gas escape type braking.
During compression-release type engine braking, exhaust valve is optionally opened with the internal-combustion engine that will produce power and is converted the air compressor that absorbs power at least provisionally to.During its compression stroke, to advance upwards when piston, the gas that is captured in the cylinder can be compressed.The gas of compression can obstruct moving upward of piston.When piston when upper dead center (TDC) position, at least one exhaust valve can be opened to discharge the gas that compresses in the cylinder to gas exhaust manifold, the energy that prevents the pressurized gas stored turns back to motor when subsequently expansion down stroke begins.In doing these, motor can produce deceleration power to help vehicle deceleration.
During bleeder type engine brake, as the additional of main exhaust valve incident (it occurs in during the exhaust stroke of piston) or substitute, exhaust valve is opened can remaining slightly during its excess-three engine cycles (braking of complete alternation gas escape type) or during the part (gas escape type that partly circulates is braked) in its excess-three engine cycles.Cylinder gases put into and emit the effect that cylinder can play engine retard.Usually, the initial opening of braking valve is before compression TDC (just, leading valve start) in the gas escape type brake operating, and lifting was remained unchanged in a period subsequently.Like this, bleeder type engine brake can be come the start valve owing to leading valve start needs less power, and because the quick emptying of continuous venting rather than the braking of compression-release type, so produce less noise.
Gas recirculation system (EGR) can allow to flow back in the engine cylinder in the part of positive run duration waste gas.EGR can be used to reduce the NO that is produced by motor at the positive run duration
XAmount.Egr system can be used to the pressure and temperature in engine braking cycle period control gas exhaust manifold and engine cylinder.Internal EGR system gets back in the engine cylinder exhaust gas recirculation by exhaust valve and/or intake valve.Mode of execution of the present utility model relates generally to internal EGR system.
Brake gas recirculation (BGR) system can allow that the part of waste gas flow back in the engine cylinder during engine brake operation.In aspirating stroke, exhaust gas recirculation is got back to for example can increase the gas flow that is used to compress-discharge braking in the cylinder in the engine cylinder, the result, and BGR can increase the braking effect of being realized by the braking incident.
Summary of the invention
In response to aforementioned challenges, the purpose of this utility model provide a kind of with simply, the system of the engine valve of mode start efficiently.For this reason, the claimant has researched and developed a kind of start engine exhaust port that is used for to realize the system of engine braking, comprising: pitman arm shaft, and it has control fluid supply passage; The engine braking rocking arm, it is pivotably mounted on the described pitman arm shaft, described engine braking rocking arm has: around the central opening of described pitman arm shaft setting, the hydraulic path that described central opening is connected with control valve, and the fluid passage that described control valve is connected with action piston assembly; Valve cross arm, it extends between first and second engine exhaust ports; Sliding pin, it is arranged in the described valve cross arm, and described sliding pin contacts described first engine exhaust port, and described action piston assembly contacts described sliding pin; Cam, it is used for applying engine braking to described engine braking rocking arm and operates with start; And spring, it is biased into described engine braking rocking arm with described cam and contacts.
The claimant has has also further researched and developed a kind of system that is used for the start engine valve, comprising: pitman arm shaft, and it has control fluid supply passage; Exhaust rocker arm, it is pivotably mounted on the described pitman arm shaft; Cam, it is used for applying main exhaust valve start operation to described exhaust rocker arm; Valve cross arm, it is arranged between described exhaust rocker arm and described first and second engine valves; Sliding pin, it is arranged in the described valve cross arm, and described sliding pin contacts described first engine valve; The engine braking rocking arm, its contiguous described exhaust rocker arm is pivotably mounted on the described pitman arm shaft, described engine braking rocking arm has: central opening, the hydraulic path that described central opening is connected with control valve, and the fluid passage that described control valve is connected with action piston assembly; Wherein said action piston assembly comprises actuating plunger, and it is suitable for contacting described sliding pin; Axle bush, it is arranged between described engine braking rocking arm and the described pitman arm shaft, and described axle bush has the port of aiming at described hydraulic path; Cam, it is used for applying engine braking to described engine braking rocking arm and operates with start; Plate, it is fastened on the rear end of described engine braking rocking arm; And spring, it contacts described plate, and the described engine braking rocking arm of bias voltage reaches with described cam and contacts.
According to such scheme of the present utility model, engine valve can by simply, start efficiently.
Should be appreciated that aforementioned describe, in general terms and detailed description subsequently all only are exemplary and indicative, rather than the utility model required for protection is construed as limiting.
Description of drawings
For helping to understand the utility model, referring now to accompanying drawing, identical reference character is represented identical parts among the figure.
Fig. 1 is the side sectional view according to the dedicated rocker arm that is used for engine braking of the utility model mode of execution, and wherein, break is connected, and cam bawl is on the last basic circle of cam.
Fig. 2 is the side sectional view of the rocking arm shown in Fig. 1, and wherein, break is connected, and cam bawl is on the following basic circle of cam.
Fig. 3 is the side sectional view of the rocking arm shown in Fig. 1, and wherein, break disconnects, and cam bawl is on the last basic circle of cam.
Fig. 4 is the side sectional view of the rocking arm shown in Fig. 1, and wherein, break disconnects, and cam bawl is on the following basic circle of cam.
Fig. 5 is the lateral perspective of the rocking arm shown in Fig. 1.
Fig. 6 is the perspective exploded view of the rocking arm shown in Fig. 1.
Fig. 7 is the front-side perspective view of the main exhaust rocking arm of rocking arm shown in Fig. 1 and vicinity.
Fig. 8 is the backside perspective view of rocking arm shown in Fig. 7 and main exhaust rocking arm.
Embodiment
Now will be in detail with reference to first mode of execution of the present utility model, the example of this mode of execution shown in the drawings.With reference to Fig. 1-4 and 7-8, the system 10 that is used for the preferred exhaust valve 400 of start engine valve is shown.Described engine valve constitutes poppet valve 400 and 450, and they are used for controlling motor firing chamber (for example, cylinder) and the circulation between (for example, air inlet and exhaust) manifold of supplying gas.Though system 10 also can be used for the intake valve start potentially, the part below this specification is described and is used this system's start exhaust valve 400 so that engine braking.System 10 comprises pitman arm shaft 110, and at least two rocking arms are arranged on the pitman arm shaft.Rocking arm comprises engine braking rocking arm 100 and exhaust rocker arm 500 (shown in Fig. 7 and 8).Rocking arm 100 and Rocker arm 5 00 can pivot about pitman arm shaft 110, this pivot as by camshaft 200 or some other motion transfering devices for example ejector sleeve to the result of rocking arm transmitting movement.
Engine braking rocking arm 100 can be by having engine braking pump or salient angle on it cam 200 rotation and pivoted.Cam 200 can contact the cam bawl 120 that is installed on the axle 121, and axle 121 is arranged on an end of engine braking rocking arm 100.Cam 200 can have following basic circle zone 204 and last basic circle zone 202.The last basic circle zone 202 of cam 200 is compared with the following basic circle zone 204 of cam has the bigger diameter distance apart from cam center.Therefore, cam can be fit to provide compression-release type, venting type or part bleeder type engine brake.When being related to engine piston in the compression stroke that the is in piston exhaust stroke of two-stroke braking (and/or for) near upper dead center position, opens by compression-release type engine braking exhaust valve (or auxiliary engine valve).Bleeder type engine brake is related to complete engine cycle and opens exhaust valve, and the part bleeder type engine brake is related to the major part of engine cycles and opens exhaust valve.
Substituting or adding as the last basic circle zone 202 that is used for engine braking, cam 200 can comprise one or more cam lobes, for example, exhaust gas recirculation (EGR) cam lobe (not shown) and/or brake gas recirculation (BGR) cam lobe (not shown), they are fit to engine braking rocking arm 100 is applied one or more Auxiliary valves start campaigns.Optionally the EGR salient angle is used in the positive mode process of motor operation EGR is provided incident.Optionally the BGR salient angle is used in the engine braking pattern of motor operation BGR is provided incident.
But wind spring 124 joining boards 122, back plate 122 is fastened to the rear end of engine braking rocking arm 100, thereby with the engine braking rocking arm towards cam 200 bias voltages.Spring 124 can push support 126 or other fixed component.With reference to Fig. 5, plate 122 can comprise center projections portion 123, and this center projections portion is fit to keep the middle position of spring 124 with respect to plate.Plate 122 also can comprise forward tab 125 and side lug 127, and they are bonded on the mating groove that is provided with on the engine braking rocking arm 100. Lug 125 and 127 helps retaining plate 122 in place, particularly in the installation process of spring 124.Spring 124 can have enough power to be kept engine braking rocking arm 100 and contacts with cam 200 during camshaft rotation always.
Referring to Fig. 1-4, pitman arm shaft 110 can comprise that one or more internal paths are used for the hydraulic fluid such as engine oil is sent to the rocking arm of installing on pitman arm shaft again.Specifically, pitman arm shaft 110 can comprise constant fluid supply passage 114 and control fluid supply passage 112.Constant fluid supply passage 114 can provide lubricating fluid to one or more rocking arms at the motor run duration.Control fluid supply passage 112 can and be specially action piston assembly 140 to engine braking rocking arm 100 provides hydraulic fluid to be used for the start of dynamic braking valve to control it.
Referring to Fig. 5 and 6, engine braking rocking arm 100 comprises rocker shaft hole, and this hole extends laterally across the central part of rocking arm so that receive axle bush 115.Axle bush 115 can be fit to receive pitman arm shaft 110.Axle bush 115 can comprise one or more grooves 116 and the port one 18 that is formed in the axle bush wall, to receive fluid from the fluid passage that is formed on the pitman arm shaft 110.Port one 18 can be aimed at the hydraulic path 102 that cooperates in being arranged on the engine braking rocking arm.
Engine braking rocking arm 100 can comprise one or more internal paths, is used for hydraulic fluid is transmitted by the engine braking rocking arm, and this fluid is received from port one 18.Again referring to Fig. 1-4 and 7-8, the internal path in the engine braking rocking arm 100 can allow hydraulic fluid for example engine oil be provided to control valve 130 and action piston assembly 140.Under the control of other electrically-controlled valve shown in solenoid valve 600 or Fig. 5 and 6, hydraulic fluid can optionally be fed to control valve 130 and actuating plunger 140.Solenoid valve 600 can be installed on the camb cap and hydraulic path can be set in engine cylinder cover and/or the camb cap, to provide hydraulic fluid to the control fluid supply passage 112 in the pitman arm shaft 110.By opening and closing solenoid valve 600, hydraulic fluid can optionally be supplied to path 112.A solenoid valve 600 is served a plurality of valve actuating systems 10 that motor is provided with.
Engine braking rocking arm 100 comprises that the valve with action piston assembly 140 does the moved end.Action piston assembly can comprise the slidably actuating plunger 141 that is arranged in the hole that is arranged in the engine braking rocking arm.Actuating plunger 141 can have hollow inside, is used for receiving slidably the bottom of gap adjustment screws 142.The top of the hollow inside of actuating plunger 141 can have the collar 143, and it utilizes the maintenance packing ring in the actuating plunger and is fixed to a position.Spring 144 can be arranged between the enlarged of bottom of the collar 143 and gap adjustment screws 142.Spring 144 can be by act on the bias voltage actuating plunger 141 that makes progress on the actuating plunger via the collar 143, away from sliding pin 310.Gap adjustment screws 142 can be outstanding from the top of engine braking rocking arm 100, and allow to regulate the bottom surface of actuating plunger 141 and the clearance space 150 between the sliding pin 310.Gap adjustment screws 142 can be passed through nut 145 locks in place.
With reference to Fig. 5 and 6, engine braking rocking arm 100 can comprise control valve seat 104.Control valve 130 can be arranged in the hole that forms in the control valve seat 104.Control valve 130 may command hydraulic fluids are to the supply of action piston assembly 140.Hydraulic path 102 can be connected to control valve seat 104 port one 18 in the axle bush 115.Path 102 can be realized sealing by plug 137 on the outer surface of rocking arm 100.
Fig. 6 shows the details of control valve 130.Control valve 130 can comprise control valve piston 131, and piston 131 is elements of general cylindrical shape shape and has one or more internal paths 132, but and its connecting inner control safety check (not shown).Safety check can allow fluid from the central authorities of hydraulic path 102 by control valve piston 131, and leaves internal path 132 arrival action piston assemblies 140 by the fluid passage in the engine braking rocking arm 100 105, but does not allow to pass through on opposite direction.Control valve piston 131 can be biased in the control valve bore towards internal path 102 by one or more control valve springs 133 and 134.Control valve spring 133 and 134 can be held in place by packing ring 135 and C shape ring 136.The central interior path can extend axially towards the middle part of the safety check placed of control valve piston from the inner of control valve piston 131.Central interior path in the control valve piston 131 can be communicated with the one or more paths 132 that extend to annular recessed portion 138 at the diameter that passes through control valve piston 131.When in hydraulic path 102, providing fluid, the result who causes with respect to the translation in its hole as control valve piston 131, the path 132 that extends through control valve piston 131 is optionally aimed at port, and this port is connected the control valve bore sidewall with the fluid passage 105 that extends to action piston assembly 140.Punctual when 105 pairs of the path that extends through control valve piston 131 and fluid passages, low-pressure fluid can flow into action piston assemblies 140 from hydraulic path 102 by control valve piston 131.The outer end of fluid passage 105 can be sealed by plug 146.
To explain the operation according to the utility model first method mode of execution now, this mode of execution has utilized the system's 10 start engine valves shown in Fig. 1 to 8.Referring to figs. 1 through 8,210 rotations of motor operation causing cam.The rotation of cam 210 cause that exhaust rocker arm 500 pivots about pitman arm shaft 110 and in response to the interaction between main exhaust lobe on the cam 210 and the exhaust cam roller 510 as main exhaust event start exhaust valve 400 and 410.Similarly, the last basic circle portion 202 on the cam 200 can cause that engine braking rocking arm 100 pivots about pitman arm shaft 110.
Fig. 3 and 4 illustrates the system 10 of motor at positive (non-engine braking) run duration.Positive run duration in system, solenoid valve 600 can not operate to can supply the hydraulic fluid of low pressure to control fluid supply passage 112 continuously.As a result, the hydraulic fluid pressure in hydraulic path 102 is not enough to overcome the bias voltage of control valve spring 133 and 134.This makes spring 133 and 134 retentive control valve pistons 131 be in again and prevents that hydraulic fluid is fed to the position of action piston assembly 140, and allows hydraulic fluid pressure to discharge from action piston assembly on the contrary.Any considerable existence of hydraulic fluid pressure in action piston assembly 140 allows spring 144 to promote the top position (Fig. 3 and 4 shown in) of actuating plunger 141 to it, produces clearance space 150 between actuating plunger and sliding pin 310.(shown in Fig. 3) when following basic circle portion 204 when cam bawl 120 and cam contacts (shown in Fig. 4) when the last basic circle portion 202 of cam bawl 120 and cam 200 contacts, clearance space 150 is all big fully, so that has this space between actuating plunger 141 and sliding pin 310.Therefore, in the whole rotary course of the positive run duration cam 200 of motor, actuating plunger 141 does not contact with sliding pin 310, exhaust valve 400 not can for engine braking by start.
Fig. 1 and 2 is illustrated in the system 10 during the engine brake operation.When being engine braking (or EGR, and/or BGR) when needing the exhaust valve start, the hydrodynamic pressures in the control fluid supply passage 112 can be increased.Solenoid valve 600 can be used to be controlled at applying of the control fluid supply passage 112 interior hydrodynamic pressures that increase.The hydrodynamic pressure that increases in control fluid supply passage 112 affacts control valve piston 131 by hydraulic path 102.As a result, control valve piston 131 can overcome being biased in the control valve bore of spring 133 and 134 and is displaced to " engine braking connection " position.When these took place, control valve piston 131 moved so that its internal fluid passageway 132 is aimed at fluid passage 105.Safety check in the control valve piston can prevent to enter the fluid reflux of fluid passage 105 by control valve piston 131.Hydrodynamic pressure in the fluid passage 105 can be enough to overcome the biasing force of the spring 144 in the action piston assembly 140.As a result, action piston assembly 140 can be full of hydraulic fluid, and actuating plunger 141 can stretch out the hole of piston assembly downwards, reduces the clearance space 150 between actuating plunger and sliding pin 310 thus.As long as low-pressure fluid is kept control valve piston 131 in " engine braking connection " position, actuating plunger 141 can be fixed on the position that this stretches out by hydraulic check valve.
Afterwards, the pivot of the engine braking rocking arm 100 that is upwards caused by the last basic circle portion 202 actuating cam rollers 120 of cam 200 can produce the start of engine braking valve corresponding to the shape and size of last basic circle portion.Because the last basic circle portion 202 of cam 200 pivots engine braking rocking arm 100 clockwise, it is downward that this pivot causes that actuating plunger (being in the position that it stretches out) promotes sliding pin 310, it promotes exhaust valve 400 again and opens (as shown in fig. 1), so the engine braking incident takes place.When basic circle portion 204 contacts with cam bawl 120 under cam 200 rotations consequently, between actuating plunger 141 and sliding pin 310, become little clearance space 150, it allows exhaust valve 400 to close (as shown in Figure 2).
When no longer needing the start of engine braking valve, the pressure in the control fluid supply passage 112 can be reduced or emit, and control valve piston 131 will turn back to " engine braking cuts out " position.Then, the fluid in the action piston assembly 140 can be put back to by fluid passage 105 and leave control valve 130.System 10 turns back to the positive operation then.
Under the situation that does not break away from scope and spirit of the present utility model, one of ordinary skill in the art will readily recognize that remodeling and the improvement that to make the utility model.For example, be appreciated that under the situation that does not break away from the utility model protection domain, exhaust rocker arm 500 can be implemented as intake rocker, and engine braking rocking arm 100 can be used to the auxiliary intake valve start.In addition, different mode of executions of the present utility model can comprise or not comprise the device that is used to make 100 biasings of engine braking rocking arm, and this biasing arrangement can utilize, and different springs is directed to be realized.Under the situation that does not break away from the utility model protection domain, the improvement of these and other that can carry out the above-mentioned mode of execution of the utility model.
Claims (13)
1. one kind is used for the start engine exhaust port to realize the system of engine braking, it is characterized in that, comprising:
Pitman arm shaft (110), it has control fluid supply passage (112);
Engine braking rocking arm (100), it is pivotably mounted on the described pitman arm shaft (110), described engine braking rocking arm has: around the central opening of described pitman arm shaft (110) setting, the hydraulic path (102) that described central opening is connected with control valve (130), and the fluid passage (105) that described control valve is connected with action piston assembly (140);
Valve cross arm (300), it extends between first and second engine exhaust ports (400,450);
Sliding pin (310), it is arranged in the described valve cross arm (300), and described sliding pin contacts described first engine exhaust port (400), and described action piston assembly (140) contacts described sliding pin (310);
Cam (200), it applies engine braking to described engine braking rocking arm (100) and operates with start; And
Spring (124), it is biased into described engine braking rocking arm (100) with described cam (200) and contacts.
2. the system as claimed in claim 1 is characterized in that, also comprises:
Exhaust rocker arm (500), its contiguous described engine braking rocking arm (100) is pivotably mounted on the described pitman arm shaft (110); And
Cam (210), it applies main exhaust valve start operation to described exhaust rocker arm (500).
3. system as claimed in claim 2 is characterized in that, also comprises:
Plate (122), it is fastened on the rear end of described engine braking rocking arm (100), described plate comprises center projections portion (123), forward tab (125) and two side lugs (127), described center projections portion receives the end of spring (124), and described lug (125,127) is bonded in the mating groove in the described engine braking rocking arm (100).
4. system as claimed in claim 3 is characterized in that, also comprises:
Axle bush (115), it is arranged between described engine braking rocking arm (100) and the described pitman arm shaft (110), the port (118) that described axle bush has groove (116) and aims at described hydraulic path (102).
5. system as claimed in claim 4 is characterized in that, described action piston assembly comprises:
Actuating plunger (141) slidably, it is arranged in the hole that is arranged in the described engine braking rocking arm, and described actuating plunger has hollow inside;
Gap adjustment screws (142), it extends through the described hollow inside that described engine braking rocking arm (100) enters into described actuating plunger (141), and described gap adjustment screws (142) has enlarged in the bottom;
The collar (143), it is fixed in the top of hollow inside of described actuating plunger (141); And
Spring (144), it is arranged between the described enlarged of described bottom of the described collar (143) and described gap adjustment screws (142).
6. system as claimed in claim 5 is characterized in that, described control valve comprises:
Control valve piston (131), it has internal path (132); And
Spring (133,134), the described control valve piston of its bias voltage (131) enters described engine braking rocking arm (100).
7. system as claimed in claim 6 is characterized in that, described sliding pin (310) comprises the shoulder that is positioned at the middle part, and described valve cross arm (300) comprises the hole, and described hole has the cooperation shoulder that is used for the sliding pin shoulder.
8. the system as claimed in claim 1 is characterized in that, also comprises:
Plate (122), it is fastened on the rear end of described engine braking rocking arm (100), described plate comprises center projections portion (123), forward tab (125) and two side lugs (127), described center projections portion receives the end of spring (124), and described lug (125,127) is bonded in the mating groove in the described engine braking rocking arm (100).
9. the system as claimed in claim 1 is characterized in that, also comprises:
Axle bush (115), it is arranged between described engine braking rocking arm (100) and the described pitman arm shaft (110), the port (118) that described axle bush has groove (116) and aims at described hydraulic path (102).
10. the system as claimed in claim 1 is characterized in that, described action piston assembly comprises:
Actuating plunger (141) slidably, it is arranged in the hole that is arranged in the described engine braking rocking arm, and described actuating plunger has hollow inside;
Gap adjustment screws (142), it extends through the described hollow inside that described engine braking rocking arm (100) enters into described actuating plunger (141), and described gap adjustment screws (142) has enlarged in the bottom;
The collar (143), it is fixed in the top of hollow inside of described actuating plunger (141); And
Spring (144), it is arranged between the described enlarged of described bottom of the described collar (143) and described gap adjustment screws (142).
11. the system as claimed in claim 1 is characterized in that, described control valve comprises:
Control valve piston (131), it has internal path (132); And
Spring (133,134), the described control valve piston of its bias voltage (131) enters described engine braking rocking arm (100).
12. the system as claimed in claim 1 is characterized in that, described sliding pin (310) comprises the shoulder that is positioned at the middle part, and described valve cross arm (300) comprises the hole, and described hole has the cooperation shoulder that is used for the sliding pin shoulder.
13. a system that is used for the start engine valve is characterized in that, comprising:
Pitman arm shaft (110), it has control fluid supply passage (112);
Exhaust rocker arm (500), it is pivotably mounted on the described pitman arm shaft (110);
Cam (210), it applies main exhaust valve start operation to described exhaust rocker arm (500);
Valve cross arm (300), it is arranged between described exhaust rocker arm (500) and described first and second engine valves (400,450);
Sliding pin (310), it is arranged in the described valve cross arm (300), and described sliding pin contacts described first engine valve (400);
Engine braking rocking arm (100), its contiguous described exhaust rocker arm (500) is pivotably mounted on the described pitman arm shaft (110), described engine braking rocking arm has: central opening, the hydraulic path (102) that described central opening is connected with control valve (130), and the fluid passage (105) that described control valve is connected with action piston assembly (140); Wherein said action piston assembly comprises actuating plunger (141), and described actuating plunger is suitable for contacting described sliding pin (310);
Axle bush (115), it is arranged between described engine braking rocking arm (100) and the described pitman arm shaft (110), and described axle bush has the port of aiming at described hydraulic path (102) (118);
Cam (200), it applies engine braking to described engine braking rocking arm (100) and operates with start;
Plate (122), it is fastened on the rear end of described engine braking rocking arm (100); And
Spring (124), it contacts described plate (122), and the described engine braking rocking arm of bias voltage (100) reaches with described cam (200) and contacts.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009201555346U CN201666172U (en) | 2009-05-27 | 2009-05-27 | System for actuating engine valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009201555346U CN201666172U (en) | 2009-05-27 | 2009-05-27 | System for actuating engine valve |
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| Publication Number | Publication Date |
|---|---|
| CN201666172U true CN201666172U (en) | 2010-12-08 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009201555346U Expired - Lifetime CN201666172U (en) | 2009-05-27 | 2009-05-27 | System for actuating engine valve |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102588030A (en) * | 2011-01-05 | 2012-07-18 | 上海尤顺汽车部件有限公司 | Auxiliary valve driving mechanism of engine |
| CN109690037A (en) * | 2016-09-14 | 2019-04-26 | 麦加戴恩国际有限公司 | Engine valve system |
| CN109899162A (en) * | 2019-03-19 | 2019-06-18 | 潍柴动力股份有限公司 | A kind of exhaust and brake system and engine |
| US10526926B2 (en) | 2015-05-18 | 2020-01-07 | Eaton Srl | Rocker arm having oil release valve that operates as an accumulator |
| CN111089005A (en) * | 2018-10-23 | 2020-05-01 | 通用汽车环球科技运作有限责任公司 | Camshaft assembly and method of operating the same |
-
2009
- 2009-05-27 CN CN2009201555346U patent/CN201666172U/en not_active Expired - Lifetime
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102588030A (en) * | 2011-01-05 | 2012-07-18 | 上海尤顺汽车部件有限公司 | Auxiliary valve driving mechanism of engine |
| CN102588030B (en) * | 2011-01-05 | 2016-08-10 | 上海尤顺汽车部件有限公司 | The auxiliary valve driving mechanism of electromotor |
| US9416692B2 (en) | 2011-01-05 | 2016-08-16 | Shanghai Universoon Autoparts Co., Ltd. | Auxiliary valve actuating mechanism of engine |
| US9732643B2 (en) | 2011-01-05 | 2017-08-15 | Shanghai Universoon Autoparts Co., Ltd. | Engine valve actuation mechanism for producing a variable engine valve event |
| US10526926B2 (en) | 2015-05-18 | 2020-01-07 | Eaton Srl | Rocker arm having oil release valve that operates as an accumulator |
| CN109690037A (en) * | 2016-09-14 | 2019-04-26 | 麦加戴恩国际有限公司 | Engine valve system |
| CN111089005A (en) * | 2018-10-23 | 2020-05-01 | 通用汽车环球科技运作有限责任公司 | Camshaft assembly and method of operating the same |
| CN111089005B (en) * | 2018-10-23 | 2021-09-21 | 通用汽车环球科技运作有限责任公司 | Camshaft assembly and method of operating the same |
| CN109899162A (en) * | 2019-03-19 | 2019-06-18 | 潍柴动力股份有限公司 | A kind of exhaust and brake system and engine |
| CN109899162B (en) * | 2019-03-19 | 2022-04-26 | 潍柴动力股份有限公司 | Exhaust braking system and engine |
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Granted publication date: 20101208 |