CN105917086A - Exhaust valve drive device and internal combustion engine with same - Google Patents
Exhaust valve drive device and internal combustion engine with same Download PDFInfo
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- CN105917086A CN105917086A CN201480064357.4A CN201480064357A CN105917086A CN 105917086 A CN105917086 A CN 105917086A CN 201480064357 A CN201480064357 A CN 201480064357A CN 105917086 A CN105917086 A CN 105917086A
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- Prior art keywords
- pressure
- start oil
- jumper bar
- oil
- exhaust valve
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
- F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
- F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
- F01L9/14—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L2001/054—Camshafts in cylinder block
Abstract
Provided is an exhaust valve drive device which adopts a cam hydraulic drive system in which the timing of opening and closing an exhaust valve is variable, the exhaust valve drive device not causing problems in the operation of the internal combustion engine and being highly reliable. A communication hole (12) connecting from a pressurizing chamber (29), in which hydraulic oil is pressurized by a plunger (11), to an outer peripheral surface opening (11d) located at the outer peripheral surface of the plunger (11) is formed in the plunger (11). A groove (30) is formed in the inner peripheral surface of a second cylinder (27), the groove (30) communicating with the outer peripheral surface opening (11d) for a part of the period of time of a reciprocating stroke of the plunger (11). A hydraulic oil discharge path (31) for discharging hydraulic oil is connected to the groove (30). A discharge amount regulation valve (33) is provided in the hydraulic oil discharge path (31).
Description
Technical field
The present invention relates to one by cam-actuated mechanical type exhaust valve actuator and there is this air bleeding valve drive dressThe internal combustion engine of putting.
Background technology
For example, as the marine diesel (internal combustion engine) of low speed two stroke diesel engine, it utilizes oil sector to drive exhaustValve. Use magnetic valve this oil sector to be carried out, in the electronic control type engine of oil pressure control, arrange according to operating load controlThe switching time of air valve, makes it keep best. On the other hand, what mechanical engine adopted is cam oil pressure actuated mode,Utilize actuated by cams jumper bar, and the type of drive of the pressure variation operation exhaust valve actuator of the corresponding oil pressure because of jumper bar generation,Because the switching time of air bleeding valve depends on cam contour, be therefore difficult to change in operation process.
In order to address the above problem, in patent documentation 1, adopt from the pressurization start oil sources of other setting to start oilPipe is supplied with the structure of high pressure start oil, and described start oil pipe is supplied with start oil to the exhaust valve actuator that drives air bleeding valve. Specifically, by switching Electronic Control oil pressure valve, carry out the start oil of self-pressurization start oil sources to start oil pipe additional services, make exhaustValve open the moment early than the moment being determined by cam contour. And, do by additional services in during the start of camMoving oil, makes the close moment of air bleeding valve be later than the moment being determined by cam contour.
Prior art document
Patent documentation
Patent documentation 1: Japanese Patent Laid-Open 2010-106843 communique
Summary of the invention
The problem that invention will solve
But, in the exhaust valve actuator of recording at patent documentation 1, in the pump generation event because of as pressurization start oil sourcesBarrier waits and in situation that oil pressure declines, the close moment of air bleeding valve determines by cam contour, cannot be by appending to start oil pipeSupply with start oil and the close moment of postponement air bleeding valve. And, the in the situation that of high engine load, cannot postpone to originalThe exhaust valve closure moment, thus can cause compression pressure and combustion pressure in cylinder larger than common, and may cause exceeding establishingCount allowable pressure and damage engine. In addition, under the state of closing at Electronic Control oil pressure valve, adhere, thereby cannot be to workUnder moving oil pipe additional services start oil condition, also may there is problem same as described above.
In addition, under the state of opening at Electronic Control oil pressure valve, adhere, thereby from pressurization start oil sources to start oilPipe is supplied with under start oil condition always continuously, cannot close air bleeding valve, may cause engine to remain in operation.
The present invention completes in view of the above fact, a kind of exhaust valve actuator is provided and has had this air bleeding valve to driveThe internal combustion engine of device, described exhaust valve actuator adopts the variable cam oil pressure actuated mode of switching time of air bleeding valve, andAnd running that can combustion motor causes obstacle, and reliability is higher.
Technical scheme
For solving above-mentioned problem, exhaust valve actuator of the present invention and there is the internal combustion engine of this exhaust valve actuatorAdopt following methods.
The first embodiment of the present invention is a kind of exhaust valve actuator, and it has: actuator, its driving internal combustion engineAir bleeding valve; Oil hydraulic circuit, its supply makes the start oil of this actuator action; Jumper bar, it is connected with this oil hydraulic circuit; Cylinder, itsReceive this jumper bar; And cam, it moves back and forth described jumper bar, and wherein, described actuator is by being pressurizeed by described jumper barDescribed start oil moves and opens described air bleeding valve, and described actuator enters the described start oil of pressurization by described jumper barRow decompression and move and close described air bleeding valve is formed with intercommunicating pore on described jumper bar, and it is from the described start of pressurizeing of this jumper barThe pressurization space of oil is communicated to the outer peripheral face peristome on the outer peripheral face that is positioned at this jumper bar, on the inner peripheral surface of described cylinder, formsHave slot part, it is communicated with described outer peripheral face peristome in during described jumper bar moves back and forth a part for stroke, at this grooveThe start oil being connected with in portion for discharging described start oil is discharged loop, discharges on loop and is provided with discharge rate at this start oilControl valve.
The present invention is the mechanical type exhaust valve actuator that makes jumper bar action by cam. , according to the action by camAnd the reciprocating motion of the jumper bar driving is carried out switch to air bleeding valve.
In first embodiment of the invention described above, on jumper bar, be provided with intercommunicating pore, it makes start oil from jumper bar pairThe pressurization space that start oil pressurizes flows to the peristome of jumper bar outer peripheral face. And, on the inner peripheral surface of cylinder, be formed withSlot part, connects with the outer peripheral face peristome of described intercommunicating pore in the interval of a part for its stroke moving back and forth at jumper barLogical. Start oil in slot part is discharged loop via start oil and is discharged from slot part. Thus, at the intercommunicating pore of jumper bar and the slot part of cylinderDuring being communicated with, can be from utilizing the pressurization space that jumper bar pressurizes to start oil to discharge start oil. Therefore, jumper bar to doIn the process that moving oil pressurizes, the start oil in pressurization is discharged via the intercommunicating pore of jumper bar, thereby has delayed the pressure of start oilPower rises, and can postpone opening the moment of air bleeding valve. On the other hand, the mistake that the start oil after jumper bar is to pressurization reduces pressureCheng Zhong, because the start oil pressure that flows away of start oil in pressurization declines, therefore can shift to an earlier date the close moment of air bleeding valve.
And, in first embodiment of the invention described above, discharge on loop discharge rate control valve be set at start oil,Delivery flow to the start oil from pressurization space regulates, and therefore can start oil be pressurizeed Adjust and use jumper barTime pressure rise degree and utilize jumper bar pressurization after the decline degree that reaches pressure of start oil, and can change arbitrarilyAir bleeding valve open moment and close moment.
In addition, in first embodiment of the invention described above, do not adopt to oil hydraulic circuit and supply with by arranging in additionThe structure of start oil of pressurized source pressurization, thereby but discharge start oil via intercommunicating pore and adjust the pressure of start oil and change,Therefore there is no need to arrange in addition the pressurized source of start oil. Therefore, in first embodiment of the invention described above, without bearingBecause the break down running of combustion motor of the pressurized source arranging in addition causes the risk of obstacle, can realize higher reliableProperty.
As discharge rate control valve, can use by electronically controlled proportional control valve or there is switching political loyalty of frame for movementStream device etc.
In the related exhaust valve actuator of first embodiment of the invention described above, described discharge rate control valve canTo be, its aperture is controlled as the structure increasing along with the decline of described engine load.
When by the control of discharge rate control valve being the direction that increases of aperture while opening direction, the decline degree of start oil pressure increasesGreatly, therefore, the close moment of air bleeding valve in advance. The close moment of air bleeding valve more early, is sealed in combustion chamber when exhaust valve closureAir capacity is more, and therefore the air of compression (new air) increases, and the compression pressure of internal combustion engine and combustion pressure raise. Therefore,Along with the load of internal combustion engine decline and by the control of discharge rate control valve for opening direction, thereby even under underload, also can changeThe burning of kind internal combustion engine also improves specific fuel consumption.
In addition, when control discharge rate control valve make its along with the decline of the load of diesel engine for opening direction, and postponeAir bleeding valve open the moment time, though likely shorten the time that burning gases and new air carry out gas exchange in cylinder,Under the part load condition that load declines, because the rotating speed of internal combustion engine is lower, therefore can fully guarantee for gas exchangeTime. And, by postponing the opening the moment of air bleeding valve, can maintain after burning having postponed in the time period of opening the momentCylinder pressure does not reduce, and therefore can obtain more axle rotation from the interior gas of cylinder that is maintained the cylinder pressure this burningPower, and further improve specific fuel consumption.
In the related exhaust valve actuator of first embodiment of the invention described above, can set described slot part relativeDuring the connection of described outer peripheral face peristome, taking the described discharge rate control valve of box lunch during as maximum opening, at described air bleeding valveIn the moment of closing, even if described internal combustion engine is high load capacity, the compression pressure of this internal combustion engine and combustion pressure also can hold in designPermitted below pressure.
The close moment of air bleeding valve more early, is sealed in air capacity in combustion chamber more when exhaust valve closure, therefore compressionNew air increase, the compression pressure of internal combustion engine and combustion pressure raise. And the close moment of air bleeding valve is row the earliest timeWhen going out adjustable valve and being maximum opening. So, during having determined the connection of slot part with respect to outer peripheral face peristome, with box lunchWhen discharge rate control valve is maximum opening, even if internal combustion engine is high load capacity, compression pressure and the combustion pressure of internal combustion engine also canBelow design allowable pressure. That is, during the delivery flow of start oil depends on the connection of slot part with respect to outer peripheral face peristome,Even if therefore discharge rate control valve is that the discharge rate of maximum opening and start oil is maximum, also can limit slot part with respect to peripheryDuring the connection of face peristome, the compression pressure of internal combustion engine and combustion pressure are being designed below allowable pressure. Therefore, evenDischarge rate control valve occurs adhesion at the state of maximum opening for a certain reason, and the delivery flow of start oil also canBe limited in safe range, therefore compression pressure and combustion pressure can not be increased to and exceed design allowable pressure, can keep awayExempt from the damage of internal combustion engine.
In the related exhaust valve actuator of first embodiment of the invention described above, described discharge rate control valve canBe made as full cut-off.
By discharge rate control valve is made as to full cut-off, can be made as the shape of not discharging start oil from the pressurization space of jumper barState. Thus, air bleeding valve can move along with the profile of cam.
In addition, as described in above-mentioned exhaust valve actuator, during determining the connection of slot part with respect to outer peripheral face peristome, withJust discharge rate control valve is under maximum opening, even if internal combustion engine is high load capacity, the compression pressure of internal combustion engine and combustion pressure are alsoCan design below allowable pressure, in this case, even if discharge rate control valve is sent out at the state of full cut-off for a certain reasonWhen raw adhesion, because air bleeding valve is only with cam contour action, the close moment of air bleeding valve can be later than discharge rate control valve for maximumIn moment when aperture, therefore compression pressure and combustion pressure can not be increased to and exceed design allowable pressure, can avoid internal combustionThe damage of machine.
The second embodiment of the present invention is a kind of internal combustion engine, and it has: above-mentioned air bleeding valve described in any one drivesDevice; The described air bleeding valve that driven by this exhaust valve actuator; And the combustion chamber of receiving this air bleeding valve.
Owing to possessing above-mentioned any one exhaust valve actuator, therefore can provide the internal combustion engine that reliability is higher.
Beneficial effect
Due in the present invention, do not adopt the work pressurizeing by the pressurized source arranging in addition to oil hydraulic circuit additional servicesMoving oily structure, but discharge start oil via intercommunicating pore, thus adjust the pressure variation of start oil, therefore without pressurization is setStart oil sources. Therefore, cause the risk of obstacle, energy without bearing because of the break down running of combustion motor of pressurization start oil sourcesThe higher reliability of enough realizations.
Brief description of the drawings
Fig. 1 is the summary pie graph that represents the related exhaust valve actuator of one embodiment of the present invention.
Fig. 2 is that the pressure of the start oil while representing to use the exhaust valve actuator of Fig. 1 changes and air bleeding valve lifting becomesThe chart of changing.
Detailed description of the invention
Referring to accompanying drawing, embodiment involved in the present invention is described.
In Fig. 1, represent the related exhaust valve actuator of present embodiment 1. Exhaust valve actuator 1 is arranged on boats and shipsOn diesel engine for main frame (internal combustion engine). Diesel engine for marine main engine (hereinafter referred to as " diesel engine ") is for example low speed two-stroke machine,Adopt the uniflow type of the uniflow scavenging of the exhaust upward of supplying gas from below. The output of diesel engine is via not shown screwAxle is connected with screw directly or indirectly.
As shown in Figure 1, exhaust valve actuator 1 has: air bleeding valve 5, it enters the exhaust flow path being formed in cylinder head 3Row switch; Piston (actuator) 7, it drives air bleeding valve 5; Oil hydraulic circuit 9, it supplies with start oil to piston 7; Jumper bar 11, its withOil hydraulic circuit 9 connects; And cam 13, it moves back and forth jumper bar 11.
Piston 7 is connected with the axial region 5a of air bleeding valve 5 extending along the vertical direction, and in the first cylinder 15 along the vertical directionMove back and forth. The hydraulic chamber 17 being formed with piston 7 by the first cylinder 15 is connected with one end 9a of oil hydraulic circuit 9. And, air bleeding valve5 is the direction application of force of the first cylinder 15 by application of force unit such as not shown air springs upward.
In oil hydraulic circuit 9, be connected with the throttling branching out from the first branch point 9a and use loop 19. Use loop 19 in throttlingUpper, be provided with the throttling arrangement 21 as fixed restrictive valve.
When the pressure in oil hydraulic circuit 9 is in the time that setting is above, the start oil of ormal weight is discharged to oil from throttling arrangement 21The outside of hydraulic circuit 9. Thus, by the start oil of ormal weight being discharged to oil hydraulic circuit 9 in the time utilizing jumper bar 11 to pressurizeOutside, and reduce and remain in oil mass in oil hydraulic circuit 9 in the time utilizing jumper bar 11 to reduce pressure, piston 7 and air bleeding valve 5 with addWhen pressure, compare and remain on top (exhaust valve closure direction). And, in the time forcing down jumper bar 11 and suck start oil, suck and pressurizationTime equivalent oil mass, above therefore piston 7 was conscientiously attracted to before completing decompression by jumper bar 11 and air bleeding valve 5 is stable closesClose.
In oil hydraulic circuit 9, be connected with the low pressure start oil supply circuit 23 branching out from the second branch point 9c. Low at thisPress on start oil supply circuit 23 work while being used for air bleeding valve 5 to carry out switch from not shown low pressure start oil sources supplyFor the oil pressure of benchmark. On low pressure start oil supply circuit 23, be provided with check valve 25, when the oil pressure in oil hydraulic circuit 9 is on ruleWhen definite value is following, from the start oil of low pressure start oil supply circuit 23 undersupply parts. Maintain thus the oil pressure as benchmark, toolBody is the minimum start oil pressure shown in Fig. 2 (c), i.e. reference pressure. On the other hand, when the pressure in oil hydraulic circuit 9 is on ruleWhen definite value is above, check valve 25 is closed condition always. ,, while pressurizeing program by jumper bar 11, check valve 25 is closed.
Jumper bar 11 moves back and forth along the vertical direction in the second cylinder 27. The pressurization being formed by the second cylinder 27 and jumper bar 11Chamber (pressurization space) 29 is connected with the other end 9d of oil hydraulic circuit 9. On jumper bar 11, be formed with intercommunicating pore 12, its connecting end surface is openedOral area 11b and outer peripheral face peristome 11d, described end face peristome 11b is arranged on towards the end face 11a of compression chamber 29 upper, described inOuter peripheral face peristome 11d is arranged on the outer peripheral face 11c that forms jumper bar 11 sides. Intercommunicating pore 12 is by the 12a of central shaft hole portion and halfHole, the footpath 12b of portion forms, and the described central shaft hole 12a of portion forms along the central shaft of jumper bar 11, the described radius hole 12b of portion and central shaft holeThe lower end connection of the 12a of portion and outward side face 11c are formed on radial direction. Start oil in compression chamber 29 is by this connectionHole 12 is discharged to outside from outer peripheral face peristome 11d. In addition, the shape of intercommunicating pore 12 nonspecific, as long as can be by startOil is discharged to outside shape from compression chamber 29.
Forming on the inner peripheral surface of side of the second cylinder 27, with the position of outer peripheral face peristome 11d subtend, be formed withSlot part 30. The height of slot part 30 is of a size of jumper bar 11 in a reciprocating part on jumper bar 11 vibration-directionsThe size being communicated with outer peripheral face peristome 11d in during stroke. Particularly, the lower end of slot part 30 is set in when 11 of jumper barsThe position that outer peripheral face peristome 11d is communicated with slot part 30 in the time of bottom dead centre, the upper end of slot part 30 is set in jumper bar 11 and is positioned atThe position that before dead point, slot part 30 is stopped up by the outer peripheral face 11c of jumper bar 11. More specifically, determine that slot part 30 is with respect to outer peripheral faceDuring the connection of peristome 11d, taking convenient discharge rate control valve 33 during as maximum opening, even if diesel engine is high load capacity, in cylinderCompression pressure and combustion pressure also can be below design allowable pressure, and according to the height that determines slot part 30 during described.
Between slot part 30 and low pressure start oil supply circuit 23, be connected with start oil and discharge loop 31. Start oil rowGo out on loop 31, be provided with discharge rate control valve 33. Use by electronically controlled proportional control valve or there is frame for movementVariable throttling device thereofs etc. are as discharge rate control valve 33, and by not shown its aperture of control part control. Discharge rate is adjustedThe aperture of joint valve 33 can stepless adjustment, also can be full cut-off. Carry out the aperture of discharge rate control valve 33 according to the load of diesel engineAdjust, in the time that diesel engine is high load capacity, be adjusted into full cut-off, along with the decline of diesel load is to opening direction adjustment.
In the bottom of jumper bar 11, connecting axle 35 is installed, be provided with cam roller 37 in the lower end of this connecting axle 35. CamRoller 37, along the outer peripheral face of the cam 13 of below, rotates on cam contour.
Cam 13 is fixed on camshaft 39, rotation together with camshaft 39. The crankshaft-synchronous of camshaft 39 and diesel engineRotation.
Next, the action of the exhaust valve actuator 1 to said structure describes.
First, the situation that is full cut-off to discharge rate control valve 33 describes, then to discharge rate control valve 33 for openingSituation describe.
<discharge rate control valve 33: full cut-off>
In the time that discharge rate control valve 33 is full cut-off, owing to can not discharging start oil from compression chamber 29, therefore air bleeding valve 5 along withThe profile of cam 13 carries out switch. The load that the situation that discharge rate control valve 13 is full cut-off is mainly diesel engine is near high load capacitySituation.
In Fig. 2, (a) represent the lifting amount of cam 13, (b) represent the valve opening of discharge rate control valve 33, (c) represent oilStart oil pressure on hydraulic circuit 9, (d) the lifting amount of expression air bleeding valve 5. In this figure, represent discharge rate control valve 33 with solid lineFor the situation of full cut-off.
As shown in this figure (b), in the one-period that the aperture of discharge rate control valve 33 rises and declines in cam lifting amountIt is full cut-off always.
In the t0 moment, when cam lifting amount increases along with the profile of cam 13 and when jumper bar 11 starts to promote, compression chamber29 is that the start oil pressure of oil hydraulic circuit 9 starts to rise. Then,, in the t1 moment, cam lifting amount reaches maximum and jumper bar 11 quiltsBe promoted to top dead-centre, start oil pressure reaches maximum, and now in the t2 moment, the oil pressure performance in the hydraulic chamber 17 of piston 7 sides is doneWith, overcome the application of force of not shown air spring and cylinder pressure and piston 7 is forced down. Thus, air bleeding valve lifting increases,Air bleeding valve 5 is opened. At this moment, along with forcing down piston 7, start oil enters hydraulic chamber 17, and therefore start oil pressure sharply reduces.
And, maintain top dead-centre at jumper bar 11 along with the profile of cam 13 until during the t3 moment, exhaustValve lifting amount also maintains maximum, and air bleeding valve 5 is open mode always.
In the t3 moment, when cam lifting amount reduces along with the profile of cam 13 and when jumper bar 11 starts to decline, start oilPress off and begin to decline. In the time that start oil pressure drops to setting, the application of force and the cylinder pressure of not shown air spring account forWind, starts piston 7 from the t4 moment and is pushed to top, and air bleeding valve lifting amount starts to reduce thus. When cam lifting amount reaches minimumWhen value and jumper bar 11 drop to bottom dead centre, air bleeding valve 5 becomes full-shut position in the t5 moment.
<discharge rate control valve 33: open>
Next, following situation is described, that is, reduce when the load of diesel engine and be near underload time, according toFrom the instruction of not shown control part, discharge rate control valve 33 is only opened to ormal weight. As the dotted line institute in Fig. 2 (b)Show, in the one-period that the aperture of discharge rate control valve 33 rises and declines in cam lifting amount, its regulation aperture keeps fixing.
As shown in Fig. 2 (c), in the t0 moment, even if cam lifting amount increases along with the profile of cam 13 and jumper bar 11 is openedBegin to promote, until the specified time limit in t0 ' moment, start oil pressure also can not rise. Reason is, at jumper bar 11 this periodIntercommunicating pore 12 is communicated with the slot part 30 of the second cylinder 27, even if jumper bar 11 rises, because the start oil in compression chamber 29 is discharged toJumper bar 11 outsides, therefore compression chamber 29 is that the pressure of oil hydraulic circuit 9 can not rise.
And, exceeding after t0 ' moment, intercommunicating pore 12 is no longer communicated with slot part 30, and therefore start oil pressure starts to rise. ThisSample one, during with discharge rate control valve 33 full cut-off, compared with (solid line), shown in dotted line, the moment of the pressure rise of start oil is from t0Moment postponed to t0 ' moment, and therefore the moment of opening of air bleeding valve 5 also can postpone. , air bleeding valve lifting amount is from postponing than the t2 momentThe moment t2 ' of stipulated time starts to rise.
In the t3 moment, when cam lifting amount reduces along with the profile of cam 13 and when jumper bar 11 starts to decline, start oilPress off and begin to decline. At this moment, because the time being communicated with at intercommunicating pore 12 and slot part 30 is to discharge ormal weight between moment t0 to t0 'Start oil, therefore the start oil pressure of (solid line) when start oil pressure ratio discharge rate control valve 33 full cut-off as shown in dotted line in Fig. 2 (c)Low. Thus, the application of force of not shown air spring and cylinder pressure overcome start oil pressure in advance, therefore air bleeding valve lifting amountStart to reduce in the t4 ' moment more Zao than the t4 moment, its result is that air bleeding valve 5 was closed completely in the t5 ' moment more Zao than the t5 moment.
So, known with reference to the variation of the air bleeding valve lifting amount of Fig. 2 (d), by opening discharge rate control valve 33, energyEnough postpone opening the moment of air bleeding valve 5, and shift to an earlier date the close moment of air bleeding valve 5. And, according to the control from not shownThe aperture of the instruction timely adjustment discharge rate control valve 33 of portion processed, can regulate the switching time of air bleeding valve 5.
According to the exhaust valve actuator 1 of present embodiment, can play following action effect.
Intercommunicating pore 12 is set on jumper bar 11, and it makes start oil from the peristome 11b of the end face 11a of jumper bar 11 to jumper bar 11Outer peripheral face peristome 11d flow. And, on the inner peripheral surface of the second cylinder 27, forming slot part 30, it carries out past at jumper bar 11In the interval of a part for the stroke of reciprocating cutter, be communicated with the outer peripheral face peristome 11d of described intercommunicating pore 12. In addition, in slot part 30Start oil discharge loop 31 via start oil and discharge from slot part 30. Thus, at intercommunicating pore 12 and second cylinder 27 of jumper bar 11Slot part 30 be communicated with during, can be from utilizing jumper bar 11 to discharge start oil to moving the compression chamber 39 that oil pressurizes. Therefore,In the process of start oil being pressurizeed at jumper bar 11, the start oil in pressurization is discharged via the intercommunicating pore 12 of jumper bar 11, therebyDelay the pressure rise of start oil, and can postpone opening the moment of air bleeding valve 5. On the other hand, jumper bar 11 to pressurization afterIn the process that start oil reduces pressure, because the start oil pressure that flows away of start oil in pressurization declines, therefore can shift to an earlier date air bleeding valve 5Close moment.
And, discharge on loop 31 discharge rate control valve 33 is set at start oil, to the start oil from compression chamber 29Delivery flow regulates, degree and the profit of pressure rise when therefore can Adjust and use jumper bar 11 start oil pressurizationBy the decline degree that reaches pressure of the start oil after jumper bar 11 pressurization, and can change arbitrarily air bleeding valve 5 open the moment andClose moment.
In addition, do not adopt to oil hydraulic circuit 9 and supply with pressurized source (for example pressurization of patent documentation 1 arranging by additionStart oil sources) structure of start oil of pressurization, but discharge start oil via intercommunicating pore 12, thus regulate the pressure of start oil to becomeChange, therefore without the pressurized source that start oil is set in addition. Therefore, without bear pressurized source because arranging in addition break down rightThe running of diesel engine causes the risk of obstacle, can realize higher reliability.
In addition, when discharge rate control valve 33 being controlled when opening direction, the decline degree of start oil pressure increases, therefore rowThe close moment of air valve 5 in advance. The close moment of air bleeding valve 5 more early, is sealed in the air capacity in combustion chamber when exhaust valve closureMore, therefore the new air of compression increases, and the compression pressure in cylinder and combustion pressure raise. Therefore, control discharge rate control valve33 make its along with the decline of the load of diesel engine for opening direction, thereby even under underload, also can improve diesel engineBurning, and improve specific fuel consumption.
In addition, be closing direction when control discharge rate control valve 33 makes it along with the decline of the load of diesel engine, and push awayLate air bleeding valve 5 open the moment time, though likely shorten the time that burning gases and new air carry out gas exchange in cylinder,Under the part load condition declining at load, because the rotating speed of diesel engine is lower, therefore can fully guarantee to exchange for gasTime. And, by postponing the close moment of air bleeding valve 5, can within the time period of having postponed close moment, maintain burningAfter cylinder pressure do not reduce, therefore can be in being maintained the cylinder of cylinder pressure this burning gas obtain more axle and revolveTurn power, and can further improve specific fuel consumption.
As mentioned above, the close moment of air bleeding valve 5 more early, get over by the air capacity being sealed in when exhaust valve closure in combustion chamberMany, therefore the new air of compression increases, and the compression pressure of internal combustion engine and combustion pressure raise. And, when the closing of air bleeding valve 5While carving the earliest, be that discharge rate control valve 33 is during for maximum opening. So, determined that slot part 30 is with respect to outer peripheral face peristomeDuring the connection of 11d, taking convenient discharge rate control valve 33 during as maximum opening, even if diesel engine is high load capacity, the compression in cylinderPressure and combustion pressure also can be below design allowable pressures. , the delivery flow of start oil depend on slot part 30 with respect toDuring the connection of outer peripheral face peristome 11d, even if therefore discharge rate control valve 33 for the discharge rate of maximum opening and start oil isMaximum, during also can limiting the connection of slot part 30 with respect to outer peripheral face peristome 11d, makes compression pressure and the combustion of diesel engineBurn pressure below design allowable pressure. Therefore, though discharge rate control valve 33 for a certain reason at the state of maximum openingSet out in raw situation of adhering, the delivery flow of start oil also can be restricted, and therefore compression pressure and combustion pressure can notBe increased to and exceed design allowable pressure, can avoid the damage of diesel engine.
By discharge rate control valve 33 is made as to full cut-off, can be made as the compression chamber 29 from jumper bar 11 not and discharges start oilState. Thus, air bleeding valve 5 can move along with the profile of cam 13.
In addition, as mentioned above, during determining the connection of slot part 30 with respect to outer peripheral face peristome 11d, so that discharge rate is adjustedJoint valve 33 is under maximum opening, even if diesel engine is high load capacity, the compression pressure in cylinder and combustion pressure also can hold in designPermitted below pressure, therefore, even if discharge rate control valve 33 is for a certain reason in the time there is adhesion in the state of full cut-off, due to exhaustValve 5 only moves with cam contour, the moment when close moment of air bleeding valve 5 can be later than discharge rate control valve 33 for maximum opening,Therefore compression pressure and combustion pressure can not be increased to and exceed design allowable pressure, can avoid the damage of diesel engine.
In addition, above-mentioned exhaust valve actuator 1 can be set on each inflator of diesel engine, or can be on each inflatorPiston 7, the first cylinder 15, cam 13 and jumper bar 11 are set, and between multiple inflators, share start oil discharge loop 31 withAnd discharge rate control valve 33.
Brief description of the drawings
1 exhaust valve actuator
3 cylinder head
5 air bleeding valves
7 pistons
9 oil hydraulic circuits
11 jumper bars
11d outer peripheral face peristome
12 intercommunicating pores
13 cams
15 first cylinders
17 hydraulic chamber
Loop is used in 19 throttlings
21 throttling arrangements
23 low pressure start oil supply circuits
25 check valves
27 second cylinders
29 compression chambers
30 slot parts
31 start oil are discharged loop
33 discharge rate control valves
35 connecting axles
37 cam rollers
Claims (according to the amendment of the 19th article of treaty)
1.[2015 May 1, (01.05.2015) international affairs bureau accepted]
[after amendment]
A kind of exhaust valve actuator, it has: actuator, it drives the air bleeding valve of internal combustion engine;
Oil hydraulic circuit, it supplies with start oil to described actuator;
Jumper bar, it is connected with described oil hydraulic circuit;
Cylinder, it receives described jumper bar; And
Cam, it moves back and forth described jumper bar,
Wherein said actuator moves and opens described air bleeding valve by the described start oil being pressurizeed by described jumper bar, described inExhaust valve actuator is characterised in that,
On described jumper bar, be formed with intercommunicating pore, it is communicated to and is positioned at institute from the pressurize pressurization space of described start oil of described jumper barState the outer peripheral face peristome on the outer peripheral face of jumper bar,
On the inner peripheral surface of described cylinder, be formed with slot part, its during described jumper bar moves back and forth a part for stroke in andDescribed outer peripheral face peristome is communicated with,
The start oil being connected with on described slot part for discharging described start oil is discharged loop,
Discharge on loop and be provided with the controlled discharge rate control valve of aperture at described start oil.
2. exhaust valve actuator according to claim 1, is characterized in that, controls described discharge rate control valve, makes itAperture increases with the decline of described engine load.
3. exhaust valve actuator according to claim 1 and 2, is characterized in that, sets described slot part with respect to describedDuring the connection of outer peripheral face peristome, taking the described discharge rate control valve of box lunch during as maximum opening, in described exhaust valve closureIn the moment, even if described internal combustion engine is high load capacity, the compression pressure of described internal combustion engine and combustion pressure also can be allowed pressure in designBelow power.
4. according to the exhaust valve actuator described in any one in claims 1 to 3, it is characterized in that, described discharge rate regulatesValve can be full cut-off.
5. an internal combustion engine, is characterized in that, has:
Exhaust valve actuator in claim 1 to 4 described in any one;
The described air bleeding valve that driven by described exhaust valve actuator; And
Receive the combustion chamber of described air bleeding valve.
Claims (5)
1. an exhaust valve actuator, it has: actuator, it drives the air bleeding valve of internal combustion engine;
Oil hydraulic circuit, it supplies with start oil to described actuator;
Jumper bar, it is connected with described oil hydraulic circuit;
Cylinder, it receives described jumper bar;
And cam, it moves back and forth described jumper bar,
Wherein said actuator moves and opens described air bleeding valve by the described start oil being pressurizeed by described jumper bar, described inExhaust valve actuator is characterised in that,
On described jumper bar, be formed with intercommunicating pore, it is communicated to and is positioned at institute from the pressurize pressurization space of described start oil of described jumper barState the outer peripheral face peristome on the outer peripheral face of jumper bar,
On the inner peripheral surface of described cylinder, be formed with slot part, its during described jumper bar moves back and forth a part for stroke in andDescribed outer peripheral face peristome is communicated with,
The start oil being connected with on described slot part for discharging described start oil is discharged loop,
Discharge on loop and be provided with discharge rate control valve at described start oil.
2. exhaust valve actuator according to claim 1, is characterized in that, controls described discharge rate control valve, makes itAperture increases with the decline of described engine load.
3. exhaust valve actuator according to claim 1 and 2, is characterized in that, sets described slot part with respect to describedDuring the connection of outer peripheral face peristome, taking the described discharge rate control valve of box lunch during as maximum opening, in described exhaust valve closureIn the moment, even if described internal combustion engine is high load capacity, the compression pressure of described internal combustion engine and combustion pressure also can be allowed pressure in designBelow power.
4. according to the exhaust valve actuator described in any one in claims 1 to 3, it is characterized in that, described discharge rate regulatesValve can be full cut-off.
5. an internal combustion engine, is characterized in that, has:
Exhaust valve actuator in claim 1 to 4 described in any one;
The described air bleeding valve that driven by described exhaust valve actuator; And
Receive the combustion chamber of described air bleeding valve.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-003456 | 2014-01-10 | ||
| JP2014003456A JP6141209B2 (en) | 2014-01-10 | 2014-01-10 | Exhaust valve driving device and internal combustion engine provided with the same |
| PCT/JP2014/075566 WO2015104875A1 (en) | 2014-01-10 | 2014-09-26 | Exhaust valve drive device and internal combustion engine with same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105917086A true CN105917086A (en) | 2016-08-31 |
Family
ID=53523717
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201480064357.4A Pending CN105917086A (en) | 2014-01-10 | 2014-09-26 | Exhaust valve drive device and internal combustion engine with same |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP6141209B2 (en) |
| KR (1) | KR101761123B1 (en) |
| CN (1) | CN105917086A (en) |
| WO (1) | WO2015104875A1 (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0158740U (en) * | 1987-10-06 | 1989-04-12 | ||
| JPH05156912A (en) * | 1991-05-22 | 1993-06-22 | New Sulzer Diesel Ag | Exhaust valve control mechanism of reciprocation type combustion engine |
| JPH0726922A (en) * | 1993-07-07 | 1995-01-27 | Zexel Corp | Valve control device for internal combustion engine |
| CN1199811A (en) * | 1997-05-16 | 1998-11-25 | 曼B与W狄赛尔公司 | Hydraulic system for two-stroke crosshead engine |
| JP2010106843A (en) * | 2009-12-17 | 2010-05-13 | Man Diesel Filial Af Man Diesel Se Tyskland | Cam drive exhaust valve operating system for large-sized two-cycle diesel engine |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0720459Y2 (en) * | 1988-04-12 | 1995-05-15 | 株式会社イナックス | Stopcock valve body |
-
2014
- 2014-01-10 JP JP2014003456A patent/JP6141209B2/en active Active
- 2014-09-26 WO PCT/JP2014/075566 patent/WO2015104875A1/en active Application Filing
- 2014-09-26 CN CN201480064357.4A patent/CN105917086A/en active Pending
- 2014-09-26 KR KR1020167014094A patent/KR101761123B1/en active IP Right Grant
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0158740U (en) * | 1987-10-06 | 1989-04-12 | ||
| JPH05156912A (en) * | 1991-05-22 | 1993-06-22 | New Sulzer Diesel Ag | Exhaust valve control mechanism of reciprocation type combustion engine |
| JPH0726922A (en) * | 1993-07-07 | 1995-01-27 | Zexel Corp | Valve control device for internal combustion engine |
| CN1199811A (en) * | 1997-05-16 | 1998-11-25 | 曼B与W狄赛尔公司 | Hydraulic system for two-stroke crosshead engine |
| JP2010106843A (en) * | 2009-12-17 | 2010-05-13 | Man Diesel Filial Af Man Diesel Se Tyskland | Cam drive exhaust valve operating system for large-sized two-cycle diesel engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2015132192A (en) | 2015-07-23 |
| WO2015104875A1 (en) | 2015-07-16 |
| KR101761123B1 (en) | 2017-07-25 |
| KR20160077170A (en) | 2016-07-01 |
| JP6141209B2 (en) | 2017-06-07 |
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Effective date of registration: 20170814 Address after: Japan's Tokyo port harbor two chome 16 No. 5 Applicant after: Mit-subishi Heavy Industries Ltd. Applicant after: Japan motor Limited by Share Ltd Address before: Japan's Tokyo port harbor two chome 16 No. 5 Applicant before: Mit-subishi Heavy Industries Ltd. |
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