CN202140128U - Integrated air-leakage type engine brake device - Google Patents
Integrated air-leakage type engine brake device Download PDFInfo
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- CN202140128U CN202140128U CN201120048690U CN201120048690U CN202140128U CN 202140128 U CN202140128 U CN 202140128U CN 201120048690 U CN201120048690 U CN 201120048690U CN 201120048690 U CN201120048690 U CN 201120048690U CN 202140128 U CN202140128 U CN 202140128U
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Abstract
An integrated air-leakage type engine brake device includes a brake driving mechanism and a brake control mechanism, wherein the brake driving mechanism includes a brake piston, an oil unloading mechanism and a support mechanism; the brake piston is placed above an internal exhaust valve of an engine and positioned in a piston hole of a valve bridge; the oil unloading mechanism is provided with an oil unloading passage in the valve bridge; the support mechanism is adjustably integrated in a rocking arm, provided with the lower part closely adjoined to the valve bridge, and can be used for sealing the oil unloading passage; and the brake control mechanism includes an exhaust brake. When the exhaust brake is closed, the exhaust back pressure of the engine increases, the internal exhaust valve bounces and is opened, the brake piston extends downwards along with the internal exhaust valve and is locked in an operation position, the slight-opening and constant-opening of the internal exhaust valve are guaranteed, so as to generate air-leakage type brake; and when the engine cam drives the valve bridge to move downwards, the valve bridge is separated from the support mechanism integrated in the rocking arm, the oil unloading passage in the valve bridge is opened for oil unloading, and the brake piston retracts to a non-operation position from the operation position. The integrated air-leakage type engine brake device has simple brake principle and compact structure, and can be installed and adjusted conveniently.
Description
Technical field:
The utility model relates to mechanical field, relates in particular to the disappointing h type engine h braking device in the valve actuation field, particularly a kind of integrated form of vehicle motor.
Background technique:
The engine braking technology can be divided into the cylinder inside brake and cylinder is braked outward.The cylinder inside brake of motor only needs temporarily to convert motor into compressor.Cut off fuel oil in the transfer process; When the approaching end of engine piston compression stroke, open exhaust valve; Allowing to be compressed gas (being air during braking) is released; The motor energy that pressurized gas absorbed in compression stroke can not turn back to engine piston at expansion stroke subsequently, but dissipate through the exhaust and the radiation system of motor.Final result is effective engine braking, slows down the speed of vehicle.
The outer braking technology of the cylinder of motor has just had (seeing U.S. Patent number 2730090) as far back as 1956; Be in waste pipe, to use current-limiting apparatus; Like the exhaust butterfly valve; The exhaust back pressure of rising motor makes the resistance of motor on engine piston in the middle of the exhaust stroke increase, and produces engine braking.Exhaust brake is in the outer braking of the cylinder of motor again, and exhaust butterfly valve or other exhaust current-limiting apparatus are exhaust brake again.
The cylinder inside brake of motor can be divided into the compression-release braking again and the type braking of losing heart.The braking of the compression-release of motor is opened exhaust valve when finishing in the engine piston compression stroke, finishes back (expand or the expansion stroke initial stage, exhaust valve is normal open before) in compression stroke and closes exhaust valve.A precedent of compression-release break is disclosed at U.S. Patent number 3220392 in nineteen sixty-five by comings (Cummins).Braking system is gone the same way through hydraulic pressure the machinery input is delivered to the exhaust valve that will open.Be usually included in reciprocating main piston in the master piston bore on the oil hydraulic circuit, this to-and-fro motion comes from the Engine Mechanical input, such as the motion of the motion of motor injection cam or adjacent exhaust cam.The hydraulic fluid that moves through of main piston is delivered to the sub-piston on the oil hydraulic circuit, makes its to-and-fro motion in slave piston bore, and sub-piston acts on the exhaust valve directly or indirectly, produces the valve motion of engine braking running.
The disappointing type braking of motor is that exhaust valve is except normal unlatching; Also in partial periodicity, keep a small amount of perseverance to open (partial periodicity loses heart and brakes); Or (aspirating stroke, compression stroke and expansion or expansion stroke) keeps a small amount of perseverance to open (disappointing braking of complete period) in the cycle of non-exhaust stroke.Partial periodicity loses heart and brakes and the disappointing main distinction of braking of complete period, is that the former does not open exhaust valve in most aspirating stroke.The inventor provides relevant explanation and instance for the h type engine h brake system that loses heart with method at U.S. Patent number 6594996.
A precedent of disappointing braking system of motor complete period is disclosed for No. 3525317 at U. S. Patent in 1970 by Miu Er (Muir).This braking system is divided into third gear with engine braking.First grade is the frictional loss that causes of motor and each moving element of vehicle and the braking that produces.Second grade is disappointing braking of complete period that continuous permanent the opening in a small amount of the exhaust valve maintenance of motor produced.Third gear is to increase the exhaust butterfly valve on losing heart the basis of braking second grade complete period, produces Associated brake.
Germany graceful (M1N) discloses disappointing braking system of engine section cycle in 1992 for No. 5086738 at U. S. Patent.Exhaust valve trace when the engine charge stroke finishes is soon opened during engine braking, in whole compression stroke, keeps perseverance to open then, closes at the initial stage of expansion or expansion stroke at last.
Motor loses heart, and the type break is general unites use with engine exhaust and brake device (like the exhaust butterfly valve), the formation Associated brake.Use exhaust butterfly valve or other exhaust current-limiting apparatus that exhaust back pressure is raise and to cause exhaust valve knock-on or float (float valve).The motor industry is generally to the float valve disapprove, because the opening and closing of exhaust valve are not by cam-actuated during float valve, the seating velocity of valve is uncontrollable.Too big valve crash speed might be damaged motor.Yet Canadian PacBrake discloses the braking method that uses exhaust brake raising exhaust back pressure to cause float valve in 1989 for No. 4848289 at U. S. Patent, thinks that high exhaust back pressure float valve helps the compression-release engine braking.
The Volvo of Sweden (Volvo) discloses Associated brake method that a kind of compression-release engine braking with exhaust brake use No. 5146890 in 1992 at U. S. Patent.Wherein the brake cam of motor has increased exhaust gas recirculatioon (EGR) boss except compression discharges the braking boss.Like this, exhaust valve is opened near the aspirating stroke lower dead center, the high back pressure tail gas (being air during braking) that produces by exhaust brake, and the anti-engine cylinder that fills in the outlet pipe increases compression brake power.
Germany graceful (M1N) discloses a kind of exhaust brake that utilizes in 1997 for No. 5692469 at U. S. Patent and has improved the apparatus and method that exhaust back pressure causes float valve and then opens gas bleed brake.When exhaust back pressure was enough high, exhaust valve closes in aspirating stroke floatingly when finishing to be left or bounces.Float therebetween at this exhaust valve, it is intervened, just before floating exhaust valve closing of opening with a braking device; Piston through an oil pressure control stops it; Stop it to close, let it keep a small amount of perseverance to open, produce the disappointing braking of partial periodicity (exhaust valve cuts out) after exhaust stroke.This braking system is the motor that is used for the single valve of every cylinder.2006, Germany's graceful (M1N) (No. the 7013867th, U. S. Patent, No. the 200310123153.7th, Chinese patent) was with the motor of above-mentioned technological expansion to the double valve of every cylinder.
The reliability and the durability of the above-mentioned disappointing h type engine h braking system of Germany graceful (M1N) are faced with a lot of problems, and open or unsteady because it depends on the intermittence of braking exhaust valve, this all is inconsistent on time and size.As everyone knows, the flying height of exhaust valve depends on exhaust back pressure, and exhaust back pressure depends on the rotating speed of motor, and receives the quality of exhaust brake and the influence of control and gas exhaust manifold design.In, during low speed, the unsteady of exhaust valve possibly not have inadequately or at all, engine braking apparatus can't start.And the demand of engine braking is very high at this moment, because motor is to use in such speed mostly.In addition, the exhaust valve (outer valve) that too high exhaust back pressure not only floats and is braked, the exhaust valve (interior valve) that also floats and do not brake simultaneously.The seating velocity of interior valve will be too big, influence the reliability and the durability of motor.Also have, this disappointing h type engine h break needs an extra carriage, is used to bear brake load and is the engine braking emptying.This extra carriage (supporting mechanism) separates with the exhaust valve drive system of motor, brings difficulty for the design of motor.Not only install and inconvenient debugging, also might increase the height and the weight of motor.
Summary of the invention:
The purpose of the utility model is to provide a kind of disappointing h type engine h braking device of integrated form, and the disappointing h type engine h braking device of described this integrated form will solve in the existing technology reliability that the h type engine h braking technology of losing heart exists and durability is bad, installation and inconvenient debugging and technical problems such as increase motor height and weight.
The device of the disappointing h type engine h braking method of this integrated form of the utility model; Comprise braking drive organ and braking control mechanism, described motor comprises cam, rocking arm, pitman arm shaft, valve bridge, interior exhaust valve and outer exhaust valve, and described interior exhaust valve is near pitman arm shaft; Described outer exhaust valve departs from pitman arm shaft; Wherein, described braking drive organ comprises brake piston, piston position-limit mechanism, oil feeding mechanism, emptying mechanism and supporting mechanism, and described brake piston is placed in interior exhaust valve top and is arranged in the piston hole of valve bridge; Described piston position-limit mechanism is arranged between valve bridge and the brake piston; Described oil feeding mechanism is communicated with piston hole in the valve bridge, and described emptying mechanism comprises an emptying passage that is arranged in the valve bridge, and described emptying passage is communicated with piston hole in the valve bridge; Described supporting mechanism is integrated to be arranged in the described rocking arm; The outlet of the lower end closed emptying passage of supporting mechanism, described braking control mechanism comprises exhaust brake, described exhaust brake has a closed position and an enable possition.
Further, described emptying mechanism has a fuel feeding position and an emptying position, and in described fuel feeding position, described supporting mechanism and valve bridge are close to, and in described emptying position, described supporting mechanism separates with the valve bridge.
Further, described oil feeding mechanism comprises unidirectional delivery valve and fuel feeding runner, and described unidirectional delivery valve is placed between fuel feeding runner and the brake piston.
Further, described oil feeding mechanism and described supporting mechanism are integrated, and described oil feeding mechanism comprises a unidirectional delivery valve, and described unidirectional delivery valve is arranged in the described supporting mechanism.
Further, also include a decompression mechanism in the described braking drive organ.
Further, also include an automatic valve clearance controlling mechanism in the described braking drive organ.
Further; Also include a variable exhaust valve spring mechanism that is arranged on the described interior exhaust valve in the described braking control mechanism; Described variable exhaust valve spring mechanism contains the variable exhaust valve acting force of the spring; Described variable exhaust valve acting force of the spring comprises two-stage exhaust valve acting force of the spring at least; Described two-stage exhaust valve acting force of the spring comprises braking uses acting force of the spring with acting force of the spring and non-braking; Described non-braking is suitable with the active force that acting force of the spring and described effluxes laterostigmatal conventional exhaust valve spring, and described braking is used acting force of the spring with acting force of the spring less than non-braking, said in exhaust valve during brake valve rises, bear braking and use acting force of the spring.
Further; Described variable exhaust valve spring mechanism comprises two exhaust valve springs that are placed on the described interior exhaust valve; The combined force of described two exhaust valve springs on interior exhaust valve is suitable with the active force that effluxes laterostigmatal conventional exhaust valve spring, wherein has only an exhaust valve spring internal exhaust valve during brake valve rises to apply spring force.
Further; Described variable exhaust valve spring mechanism comprises inner spring and the outer spring that is set on the described interior exhaust valve; Described outer spring is longer than inner spring; Described outer spring internal exhaust valve during brake valve rises applies spring force, and described inner spring internal exhaust valve during brake valve rises does not apply spring force, and described outer spring and the inner spring combined force on interior exhaust valve equates with the active force that effluxes laterostigmatal conventional exhaust valve spring.
Further; Described supporting mechanism is integrated in the described rocking arm adjustablely; Described supporting mechanism comprises by nut and is fixed on the adjusting screw on the rocking arm, adjusting screw with resemble the foot pad and link to each other, resemble of the outlet of the lower end of foot pad near emptying passage in valve bridge and the draught excluder bridge.
Further; Described supporting mechanism supporting mechanism is integrated in the described rocking arm adjustablely; Described supporting mechanism comprises by nut and is fixed on the adjusting screw on the rocking arm; Be provided with delivery piston below the adjusting screw, oil supply gallery and unidirectional delivery valve are contained in the inside of delivery piston, and the lower end of delivery piston is near the outlet of emptying passage in valve bridge and the draught excluder bridge.
The working principle of the utility model is: when the needs engine braking, the braking control mechanism is opened, and exhaust brake cuts out, and the exhaust back pressure in the engine exhaust pipe at the exhaust brake upper reaches raises.Pressure is low higher constantly (when aspirating stroke finishes soon with exhaust back pressure in engine cylinder; This moment, exhaust cam was positioned on the basic circle; Exhaust rocker arm and valve bridge are in static relatively position); The active force and the cylinder of making every effort to overcome clothes exhaust valve spring in exhaust back pressure acts on the exhaust valve are pressed, and the exhaust valve knock-on is opened downwards in making.Being positioned at brake piston on the exhaust valve follows exhaust valve at the piston hole of valve bridge and moves on to operating position from off position downwards.The low-pressure oil of motor is from fuel feeding runner and unidirectional delivery valve fuel feeding in the brake piston hole, and machine oil is full of the gap that brake piston forms downwards.Because unidirectional delivery valve does not allow fluid to flow backwards, the sealing of emptying passage supported body forms the hydraulic pressure link between brake piston and the valve bridge, and the interior exhaust valve that knock-on is opened downwards withstands, and does not allow its valve seat that falls back.From the aspirating stroke latter stage of motor, through whole compression stroke and most expansion stroke, interior exhaust valve remains a small amount of perseverance and opens, and produces the h type engine h braking of losing heart.Brake load by interior exhaust valve through the hydraulic pressure that forms between brake piston, brake piston and the valve bridge link, valve bridge, supporting mechanism and rocking arm, pass to the cam of basic circle position in being in.When cam turns to conventional exhaust boss from interior basic circle, the cam-driven valve bridge moves downward.The valve bridge separates with supporting mechanism, opens and unloads the circulation road emptying.Brake piston just is withdrawn into off position from operating position.The valve bridge opens and closes two exhaust valves under the promotion of cam together.Cam turns over conventional exhaust boss, and on the basic circle, start anew braking period in getting back to.So braking period, circulation repeatedly is till the braking control mechanism cuts out.At this moment; Exhaust brake (butterfly valve) is opened; Exhaust back pressure in the engine exhaust pipe at the exhaust brake upper reaches reduces, and exhaust valve can't bounce and open (active force of exhaust valve spring is much larger than brake spring), and brake piston is in off position in the piston hole of valve bridge; Motor withdraws from braking state, gets back to fired state.
The utility model is compared with prior art, and its effect is actively with tangible.It is inner that the utility model is integrated in the existing valve actuation chain of motor with whole disappointing type arrestment mechanism, and compact structure has reduced the weight and the height of motor, has simplified engine braking apparatus, has increased the reliability and the durability of engine operation.
Description of drawings:
Fig. 1 is that first embodiment of disappointing h type engine h braking device of the integrated form in the utility model is at the schematic representation of its off-position.
Fig. 2 is that first embodiment of the disappointing h type engine h braking device of the integrated form in the utility model " opens " schematic representation of position at it.
Fig. 3 is that second embodiment of disappointing h type engine h braking device of the integrated form in the utility model is at the schematic representation of its off-position.
Fig. 4 is that second embodiment of the disappointing h type engine h braking device of the integrated form in the utility model " opens " schematic representation of position at it.
Fig. 5 is that the 3rd embodiment of disappointing h type engine h braking device of the integrated form in the utility model is at the schematic representation of its off-position.
Fig. 6 is that the 3rd embodiment of the disappointing h type engine h braking device of the integrated form in the utility model " opens " schematic representation of position at it.
Embodiment:
Embodiment 1:
As depicted in figs. 1 and 2, first embodiment of the disappointing h type engine h braking device of the integrated form of the utility model is respectively in its " pass " and " opening " position.Comprise four chief components among the figure: exhaust valve actuator 200, exhaust valve 300 (exhaust valve 3001 and outer exhaust valve 3002 in comprising), engine braking driving mechanism 100 and engine braking control mechanism 50.
When the needs engine braking; Braking control mechanism 50 is opened; Exhaust brake cuts out, the air-flow in the restriction tailpipe 710, and the exhaust back pressure in the engine exhaust pipe at the exhaust brake upper reaches (comprising outlet pipe 610, outlet pipe 620 and outlet pipe 630 etc.) raises.In engine cylinder pressure low with exhaust back pressure when higher (aspirating stroke latter stage; This moment, exhaust cam 230 was positioned on the basic circle 225; Exhaust rocker arm 210 is in static relatively position with valve bridge 400); The active force and the cylinder of making every effort to overcome clothes exhaust valve spring 310 that exhaust back pressure acts on the exhaust valve 300 are pressed, and make the exhaust valve knock-on open 330 (Fig. 2) downwards in a small amount.Being positioned at brake piston 160 on the exhaust valve 3001 follows exhaust valve 3001 at the piston hole of valve bridge and moves on to operating position (Fig. 2) from off position (Fig. 1) downwards.The low-pressure oil of motor gets into high-pressure oil duct 412 from the fuel feeding runner through unidirectional delivery valve 172, is full of the gap 234 that brake piston 160 forms downwards.Because unidirectional delivery valve 172 does not allow fluid to flow backwards, 125 sealings of emptying passage 197 supported bodies form the hydraulic pressure link between brake piston 160 and the valve bridge 400, and the interior exhaust valve 3001 that knock-on is opened downwards withstands, and does not allow its valve seat 320 that falls back.From the aspirating stroke latter stage of motor, through whole compression stroke and most expansion stroke, interior exhaust valve 3001 remains a small amount of perseverance and opens, and produces the h type engine h braking of losing heart.Brake load by interior exhaust valve 3001 through the hydraulic pressure that forms between brake piston 160, brake piston 160 and the valve bridge link, valve bridge 400, supporting mechanism 125 and rocking arm 210, pass to the cam 230 of basic circle 225 positions in being in.
When cam 230 turns to conventional exhaust boss 220 from interior basic circle 225, cam 230 drives rocking arms 210 and valve bridges 400, and valve bridge 400 moves downward.Distance between valve bridge 400 and the supporting mechanism 125 (resembling foot pad 1142) increases, and both separate gradually.The circulation road 197 that unloads in the valve bridge 400 is opened emptying, and brake piston 160 pushes back off position (active force of exhaust valve spring 3101 is much larger than brake spring 177) from operating position.Valve bridge 400 opens and closes interior exhaust valve 3001 with outer exhaust valve 3002 under the promotion of cam 230 and rocking arm 210 together.Cam 230 turns over conventional exhaust boss 220, and on the basic circle 225, start anew braking period in getting back to, and circulation is repeatedly closed up to braking control mechanism 50.At this moment; Exhaust brake (butterfly valve) is opened, and the air-flow in the tailpipe 710 is unrestricted, and the exhaust back pressure in the engine exhaust pipe at the exhaust brake upper reaches (outlet pipe 610, outlet pipe 620 and outlet pipe 630 etc.) reduces; Exhaust valve can't bounce and open (active force of exhaust valve spring 3101 is much larger than brake spring 177); Brake piston 160 is in off position (Fig. 1) in the piston hole of valve bridge, motor withdraws from braking state, gets back to fired state.
Embodiment 2:
Like Fig. 3 and shown in Figure 4, second embodiment of the disappointing h type engine h braking device of the integrated form of the utility model is respectively in its " pass " and " opening " position.The main distinction between the present embodiment and first embodiment is:
1. increased automatic valve clearance controlling mechanism.Automatically the valve clearance controlling mechanism comprises regulating piston 162 and Regulation spring 166.Regulating piston 162 is positioned at the center hole that valve bridge 400 is upwards opened.Regulation spring 166 upwards is close to regulating piston 162 biasing and resembles foot pad 114 between regulating piston 162 and valve bridge 400.The unidirectional delivery valve of oil feeding mechanism is positioned at regulating piston 162.Be provided with a valve clearance 130 between regulating piston 162 and the valve bridge 400.Valve clearance 130 is less than the stroke 234 (distance between off position and the operating position) of brake piston 160; Exhaust valve 3001 and outer exhaust valve 3002 expands with heat and contract with cold in mainly being used for regulating; The precalculated position that keeps cam 230 when interior basic circle 225 positions, to design between rocking arm 210 and the valve bridge 400; Make following (the resembling foot pad 1142) that be integrated in the supporting mechanism 125 in the rocking arm 210 near valve bridge 400, the emptying passage 197 in the draught excluder bridge.
2. increased decompression mechanism.Decompression mechanism comprises the relief hole 152 in the brake piston 160.When the oil pressure in brake piston 160 holes 190 increases; Increase through the gap between brake piston 160 and the hole 190, locating slot 137 and the lubricating oil leakage of relief hole 152 on the brake piston 160 thereupon, make the oil pressure that acts on the brake piston 160 be no more than the predetermined value that is designed.
3. increased the variable exhaust valve spring mechanism bearing on the interior exhaust valve 3001 of brake load.The variable exhaust valve spring mechanism contains the variable exhaust valve acting force of the spring.The variable exhaust valve acting force of the spring comprises two-stage exhaust valve acting force of the spring at least.Two-stage exhaust valve acting force of the spring comprises braking uses acting force of the spring with acting force of the spring and non-braking.Non-braking is suitable with the active force of the conventional exhaust valve spring on acting force of the spring and the outer exhaust valve 3002.The braking that interior exhaust valve 3001 bears during brake valve rises is used acting force of the spring with acting force of the spring less than non-braking.The variable exhaust valve spring mechanism of present embodiment comprises exhaust valve spring 3101 (outer spring) and the exhaust valve spring 312 (inner spring) that is placed on the interior exhaust valve 3001.Be provided with a spacing 131 (Fig. 3) between inner spring 312 and the spring seat 3021.Spacing 131 rises 330 (Fig. 4) roughly the same (being generally less than 2mm) with brake valve.Like this, inner spring 312 internal exhaust valve 3001 during brake valve rises does not apply spring force, 3001 active forces that bear outer spring 3101 of interior exhaust valve.Because the active force of outer spring 3101 is less than the active force of conventional exhaust valve spring (as 3102), so during brake valve rises, the spring force that the spring force that interior exhaust valve 3001 bears bears less than outer exhaust valve 3002.But in case the lift of interior exhaust valve 3001 surpasses braking lift 131 (or brake valve rises 330); The active force of the conventional exhaust valve spring 3102 on exhaust valve spring 3101 and the combined force (non-brake spring power) of exhaust valve spring 312 on interior exhaust valve 3001 and the outer exhaust valve 3002 is suitable, thereby has guaranteed the isostatic movement of interior exhaust valve 3001 and outer exhaust valve 3002.
When the needs engine braking, braking control mechanism 50 is opened, and exhaust brake cuts out, the air-flow in the restriction tailpipe 710, and the exhaust back pressure in the engine exhaust pipe at the exhaust brake upper reaches (outlet pipe 610, outlet pipe 620 and outlet pipe 630 etc.) raises.In engine cylinder pressure low with exhaust back pressure when higher (aspirating stroke latter stage; This moment, exhaust cam 230 was positioned on the basic circle 225; Exhaust rocker arm 210 is in static relatively position with valve bridge 400); Active force of making every effort to overcome clothes outer spring 3101 and cylinder in exhaust back pressure acts on the exhaust valve 3001 are pressed, and 330 (Fig. 4) are opened in exhaust valve 3001 knock-ons downwards in a small amount in making.Be positioned at brake piston 160 on the exhaust valve 3001 at the piston hole 190 of valve bridge 400 from off position (Fig. 3) to moving down into operating position (Fig. 4).The low-pressure oil of motor gets into high-pressure oil duct 412 from the fuel feeding runner through unidirectional delivery valve 172, is full of the gap 234 that brake piston 160 forms downwards.Because unidirectional delivery valve 172 does not allow fluid to flow backwards, 125 sealings of emptying passage 197 supported bodies form the hydraulic pressure link between brake piston 160 and the valve bridge 400, and the interior exhaust valve 3001 that knock-on is opened downwards withstands, and does not allow its valve seat 320 that falls back.From the aspirating stroke latter stage of motor, through whole compression stroke and most expansion stroke, interior exhaust valve 3001 remains a small amount of perseverance and opens, and produces the h type engine h braking of losing heart.Brake load by interior exhaust valve 3001 through the hydraulic pressure that forms between brake piston 160, brake piston 160 and the valve bridge link, valve bridge 400, supporting mechanism 125 and rocking arm 210, pass to the cam 230 of basic circle 225 positions in being in.
When cam 230 turns to conventional exhaust boss 220 from interior basic circle 225, cam 230 drives rocking arms 210 and valve bridges 400, and valve bridge 400 moves downward.Distance between valve bridge 400 and the supporting mechanism 125 (resembling foot pad 1142) increases, and both separate gradually.The circulation road 197 that unloads in the valve bridge 400 is opened emptying, and brake piston 160 pushes back off position (active force of exhaust valve spring 3101 is much larger than brake spring 177) from operating position.Valve bridge 400 is opened interior exhaust valve 3001 then simultaneously with outer exhaust valve 3002 and to be closed under the promotion of cam 230 and rocking arm 210.Cam 230 turns over conventional exhaust boss 220, and on the basic circle 225, start anew braking period in getting back to, and circulation is repeatedly closed up to braking control mechanism 50.
Because the active force of the outer spring 3101 that the active force of the spring 3102 that bears of outer exhaust valve 3002 bears greater than interior exhaust valve 3001; When interior exhaust valve 3001 bounces because of exhaust back pressure raises when opening, outer exhaust valve 3002 can not bounce to open or bounce to open and reduce.Like this, when interior exhaust valve 3001 more was prone to open braking, outer exhaust valve 3002 was difficult for opening, thereby reduced its seating velocity, increased the reliability and the durability of motor.
Embodiment 3:
Like Fig. 5 and shown in Figure 6, the 3rd embodiment of the disappointing h type engine h braking device of the integrated form of the utility model is respectively in its " pass " and " opening " position.The oil feeding mechanism of present embodiment and supporting mechanism 125 are integrated.There is a delivery piston 162 adjusting screw 1102 inside of supporting mechanism 125.One hydraulic pressure runner 115 is arranged in the delivery piston 162,, communicate with rocking arm 210 interior hydraulic pressure runners 214 through the horizontal oilhole 113 in the adjusting screw 1102.Be mounted with unidirectional delivery valve 172 in the hydraulic pressure runner 115.Emptying passage in the valve bridge 400 197 also is an oil supply gallery simultaneously in addition.Being placed in seal ring 173 in delivery piston 162 end faces can prevent because of the surface of contact out-of-flatness or not line up the leakage that causes.
When the needs engine braking, braking control mechanism 50 is opened, and exhaust brake cuts out, the air-flow in the restriction tailpipe 710, and the exhaust back pressure in the engine exhaust pipe at the exhaust brake upper reaches (outlet pipe 610, outlet pipe 620 and outlet pipe 630 etc.) raises.In engine cylinder pressure low with exhaust back pressure when higher (aspirating stroke latter stage; This moment, exhaust cam 230 was positioned on the basic circle 225; Exhaust rocker arm 210 is in static relatively position with valve bridge 400); Active force of making every effort to overcome clothes outer spring 3101 and cylinder in exhaust back pressure acts on the exhaust valve 3001 are pressed, and 330 (Fig. 6) are opened in exhaust valve 3001 knock-ons downwards in a small amount in making.Be positioned at brake piston 160 on the exhaust valve 3001 at the piston hole 190 of valve bridge 400 from off position (Fig. 5) to moving down into operating position (Fig. 6).The low-pressure oil of motor directly gets in brake piston 160 holes 190 with unidirectional delivery valve 172 and valve bridge 400 interior emptying passages 197 from the fuel feeding runner 115 in the supporting mechanism 125, is full of the gaps 234 that brake piston 160 forms downwards.Because unidirectional delivery valve 172 does not allow fluid to flow backwards, 125 sealings of emptying passage 197 supported bodies form the hydraulic pressure link between brake piston 160 and the valve bridge 400, and the interior exhaust valve 3001 that knock-on is opened downwards withstands, and does not allow its valve seat 320 that falls back.From the aspirating stroke latter stage of motor, through whole compression stroke and most expansion stroke, interior exhaust valve 3001 remains a small amount of perseverance and opens, and produces the h type engine h braking of losing heart.Brake load by interior exhaust valve 3001 through the hydraulic pressure that forms between brake piston 160, brake piston 160 and the valve bridge 400 link, valve bridge 400, supporting mechanism 125 and rocking arm 210, pass to the cam 230 that is in interior basic circle 225 positions.
When cam 230 turns to conventional exhaust boss 220 from interior basic circle 225, cam 230 drives rocking arms 210 and valve bridges 400, and valve bridge 400 moves downward.Distance between valve bridge 400 and the supporting mechanism 125 (resembling foot pad 1142) increases.Delivery piston 162 in the supporting mechanism 125 glides under oil pressure (also can increase spring in the above like needs) effect.The distance of glide of delivery piston 162 is by the snap ring that is installed in internal piston 176 decisions.After the downslide, delivery piston 162 will block the cross-drilled hole 113 in the adjusting screw 1102, stop to unidirectional delivery valve 172 fuel feeding.Like this during unloading circulation road and opened in 197 minutes in delivery piston 162 and valve bridge 400, can past external leakage from the machine oil of oil supply gallery.In case but the circulation road 197 that unloads in the valve bridge 400 is opened emptying, brake piston 160 just pushes back off position (active force of exhaust valve spring 3101 is much larger than brake spring 177) from operating position.Valve bridge 400 is opened two exhaust valves 3001 and 3002 then simultaneously and to be closed under the promotion of cam 230 and rocking arm 210.Cam 230 turns over conventional exhaust boss 220, and on the basic circle 225, start anew braking period in getting back to, and circulation is repeatedly closed up to braking control mechanism 50.
Above-mentioned explanation has disclosed the disappointing h type engine h braking device and the method for new integrated form.Above-mentioned many embodiments should not be regarded as the restriction to the utility model scope, but as some concrete illustrations of representing the utility model, many other differentiation all might therefrom produce.For instance, the disappointing h type engine h braking device and the method for the integrated form here not only can be used for overhead camshaft type engine, also are applicable to push rod engine.
Also have, the exhaust brake of braking control mechanism not only can be the exhaust butterfly valve, also can be the current-limiting apparatus of other form, like the variable geometry turbine machine.As long as can realize increasing the exhaust back pressure function of motor.
In addition, unidirectional delivery valve can be a ball valve, also can be the valve of other form, like video disc valve etc.Also have, brake piston 160 can be varied, like " H " type and T-shape etc.
Also have, the automatic valve clearance controlling mechanism that is used for embodiment 2 also can be used for other embodiment.
In addition; Braking also can be adopted various ways with the variable exhaust valve spring mechanism on the interior exhaust valve; Can be a spring or many springs, can adopt the spring of helical spring or other form, as long as the acting force of the spring on the exhaust valve is less than the acting force of the spring on the conventional exhaust valve (outer exhaust valve) in can being implemented in during the brake valve liter (about 0 to 2mm); And during the valve lift more than brake valve rises, act on roughly the same the getting final product of spring force on inside and outside two exhaust valves.
Therefore, the scope of the utility model should not decided by above-mentioned concrete illustration, but is decided by claim.
Claims (11)
1. the disappointing h type engine h braking device of an integrated form; Comprise braking drive organ and braking control mechanism; Described motor comprises cam, rocking arm, pitman arm shaft, valve bridge and an interior exhaust valve and an outer exhaust valve, and described interior exhaust valve is near pitman arm shaft, and described outer exhaust valve departs from pitman arm shaft; It is characterized in that: described braking drive organ comprises brake piston, piston position-limit mechanism, oil feeding mechanism, emptying mechanism and supporting mechanism; Exhaust valve top and be arranged in the piston hole of valve bridge in described brake piston is placed in, described piston position-limit mechanism is arranged between valve bridge and the brake piston, and described oil feeding mechanism links to each other with piston hole in the valve bridge; Described emptying mechanism comprises an emptying passage that is arranged in the valve bridge; Described emptying passage is communicated with piston hole in the valve bridge, and described supporting mechanism is integrated to be arranged in the described rocking arm, the outlet of the lower end closed emptying passage of supporting mechanism; Described braking control mechanism comprises exhaust brake, and described exhaust brake has a closed position and an enable possition.
2. the disappointing h type engine h braking device of integrated form as claimed in claim 1; It is characterized in that: described emptying mechanism has a fuel feeding position and an emptying position; In described fuel feeding position; Described supporting mechanism and valve bridge are close to, and in described emptying position, described supporting mechanism separates with the valve bridge.
3. the disappointing h type engine h braking device of integrated form as claimed in claim 1, it is characterized in that: described oil feeding mechanism comprises unidirectional delivery valve and fuel feeding runner, described unidirectional delivery valve is placed between fuel feeding runner and the brake piston.
4. the disappointing h type engine h braking device of integrated form as claimed in claim 1; It is characterized in that: described oil feeding mechanism and described supporting mechanism are integrated; Described oil feeding mechanism comprises a unidirectional delivery valve, and described unidirectional delivery valve is arranged in the described supporting mechanism.
5. the disappointing h type engine h braking device of integrated form as claimed in claim 1 is characterized in that: also include a decompression mechanism in the described braking drive organ.
6. the disappointing h type engine h braking device of integrated form as claimed in claim 1 is characterized in that: also include an automatic valve clearance controlling mechanism in the described braking drive organ.
7. the disappointing h type engine h braking device of integrated form as claimed in claim 1; It is characterized in that: also include a variable exhaust valve spring mechanism that is arranged on the described interior exhaust valve in the described braking control mechanism; Described variable exhaust valve spring mechanism contains the variable exhaust valve acting force of the spring; Described variable exhaust valve acting force of the spring comprises two-stage exhaust valve acting force of the spring at least; Described two-stage exhaust valve acting force of the spring comprises braking uses acting force of the spring with acting force of the spring and non-braking; Described non-braking is suitable with the active force that acting force of the spring and described effluxes laterostigmatal conventional exhaust valve spring, and described braking is used acting force of the spring with acting force of the spring less than non-braking, said in exhaust valve during brake valve rises, bear braking and use acting force of the spring.
8. the disappointing h type engine h braking device of integrated form as claimed in claim 7; It is characterized in that: described variable exhaust valve spring mechanism comprises two exhaust valve springs that are placed on the described interior exhaust valve; The combined force of described two exhaust valve springs on interior exhaust valve is suitable with the active force that effluxes laterostigmatal conventional exhaust valve spring, wherein has only an exhaust valve spring internal exhaust valve during brake valve rises to apply spring force.
9. the disappointing h type engine h braking device of integrated form as claimed in claim 7; It is characterized in that: described variable exhaust valve spring mechanism comprises inner spring and the outer spring that is set on the described interior exhaust valve; Described outer spring is longer than inner spring; Described outer spring internal exhaust valve during brake valve rises applies spring force, and described outer spring and the inner spring combined force on interior exhaust valve equates with the active force that effluxes laterostigmatal conventional exhaust valve spring.
10. the disappointing h type engine h braking device of integrated form as claimed in claim 1; It is characterized in that: described supporting mechanism is integrated in the described rocking arm adjustablely; Described supporting mechanism comprises by nut and is fixed on the adjusting screw on the rocking arm; Pad links to each other adjusting screw with resembling enough, resembles the outlet of the lower end of foot pad near emptying passage in valve bridge and the draught excluder bridge.
11. the disappointing h type engine h braking device of integrated form as claimed in claim 3; It is characterized in that: described supporting mechanism is integrated in the described rocking arm adjustablely; Described supporting mechanism comprises by nut and is fixed on the adjusting screw on the rocking arm; Be provided with delivery piston below the adjusting screw, oil supply gallery and unidirectional delivery valve are contained in the inside of delivery piston, and the lower end of delivery piston is near the outlet of emptying passage in valve bridge and the draught excluder bridge.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201120048690U CN202140128U (en) | 2011-02-25 | 2011-02-25 | Integrated air-leakage type engine brake device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201120048690U CN202140128U (en) | 2011-02-25 | 2011-02-25 | Integrated air-leakage type engine brake device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202140128U true CN202140128U (en) | 2012-02-08 |
Family
ID=45551188
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201120048690U Expired - Lifetime CN202140128U (en) | 2011-02-25 | 2011-02-25 | Integrated air-leakage type engine brake device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202140128U (en) |
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| CN102650224A (en) * | 2011-02-25 | 2012-08-29 | 奚勇 | Braking method and device of integrated exhaust type engine |
| CN102691542A (en) * | 2011-03-24 | 2012-09-26 | 奚勇 | Engine brake device positioned by air valve rod |
| CN104454064A (en) * | 2013-09-19 | 2015-03-25 | 曼卡车和巴士股份公司 | Device and method for actuating at least one exhaust valve of a valve-controlled combustion engine |
| GB2540736A (en) * | 2015-06-24 | 2017-02-01 | Eaton Srl | Valvetrain for diesel engine having de-compression engine brake |
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| CN102650224A (en) * | 2011-02-25 | 2012-08-29 | 奚勇 | Braking method and device of integrated exhaust type engine |
| CN102650224B (en) * | 2011-02-25 | 2014-07-02 | 奚勇 | Braking method and device of integrated exhaust type engine |
| CN102691542A (en) * | 2011-03-24 | 2012-09-26 | 奚勇 | Engine brake device positioned by air valve rod |
| WO2012126166A1 (en) * | 2011-03-24 | 2012-09-27 | 奚勇 | Engine brake device positioned by valve stem |
| CN104454064A (en) * | 2013-09-19 | 2015-03-25 | 曼卡车和巴士股份公司 | Device and method for actuating at least one exhaust valve of a valve-controlled combustion engine |
| CN106150589B (en) * | 2015-04-28 | 2019-01-15 | 上海尤顺汽车部件有限公司 | A kind of list valve compression-release valve bridge brake apparatus and method |
| US10329972B2 (en) | 2015-04-28 | 2019-06-25 | Shanghai Universoon Auto Parts Co., Ltd. | Single valve compression release bridge brake |
| GB2540736A (en) * | 2015-06-24 | 2017-02-01 | Eaton Srl | Valvetrain for diesel engine having de-compression engine brake |
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| CN107035450A (en) * | 2015-10-16 | 2017-08-11 | 现代自动车株式会社 | Changeable air valve opens duration/variable valve lift system and engine |
| CN107035450B (en) * | 2015-10-16 | 2020-12-11 | 现代自动车株式会社 | Variable valve opening duration and variable valve lift system and engine |
| CN109790764A (en) * | 2016-08-05 | 2019-05-21 | 优特卡洛股份公司 | Hydraulic tappet |
| WO2020038609A1 (en) * | 2018-08-20 | 2020-02-27 | Eaton Intelligent Power Limited | Bridge based passive bleeder brake |
| CN109538325A (en) * | 2018-12-20 | 2019-03-29 | 皆可博(苏州)车辆控制系统有限公司 | A kind of integrated engine braking device |
| CN110173314A (en) * | 2019-05-15 | 2019-08-27 | 浙江大学 | A kind of air valve bridge and its exhaust brake method of achievable compression-release type engine braking |
| CN110173314B (en) * | 2019-05-15 | 2023-07-18 | 浙江大学 | Valve bridge capable of realizing compression release type engine braking and exhaust braking method thereof |
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