CN103953413B - Multi-stage booster valve exhaust gear - Google Patents
Multi-stage booster valve exhaust gear Download PDFInfo
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- CN103953413B CN103953413B CN201410107950.4A CN201410107950A CN103953413B CN 103953413 B CN103953413 B CN 103953413B CN 201410107950 A CN201410107950 A CN 201410107950A CN 103953413 B CN103953413 B CN 103953413B
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- 239000010720 hydraulic oil Substances 0.000 claims abstract description 200
- 230000000740 bleeding effect Effects 0.000 claims abstract description 43
- 239000003921 oil Substances 0.000 claims abstract description 35
- 230000008676 import Effects 0.000 claims description 35
- 239000012530 fluid Substances 0.000 claims description 34
- 238000002485 combustion reaction Methods 0.000 abstract description 10
- 239000000446 fuel Substances 0.000 abstract description 4
- 239000007788 liquid Substances 0.000 description 6
- 238000000034 method Methods 0.000 description 6
- 230000008569 process Effects 0.000 description 6
- 239000007789 gas Substances 0.000 description 5
- 230000009471 action Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000007246 mechanism Effects 0.000 description 2
- 239000002912 waste gas Substances 0.000 description 2
- KXLUWEYBZBGJRZ-POEOZHCLSA-N Canin Chemical compound O([C@H]12)[C@]1([C@](CC[C@H]1C(=C)C(=O)O[C@@H]11)(C)O)[C@@H]1[C@@]1(C)[C@@H]2O1 KXLUWEYBZBGJRZ-POEOZHCLSA-N 0.000 description 1
- GPFVKTQSZOQXLY-UHFFFAOYSA-N Chrysartemin A Natural products CC1(O)C2OC2C34OC3(C)CC5C(CC14)OC(=O)C5=C GPFVKTQSZOQXLY-UHFFFAOYSA-N 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 239000000295 fuel oil Substances 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 230000001502 supplementing effect Effects 0.000 description 1
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Abstract
The object of the present invention is to provide multi-stage booster valve exhaust gear, by the open and close of hydraulic-driven air bleeding valve, adopt first stage piston and second piston respectively with different pressure ratios to the hydraulic oil supercharging in elementary booster cavity, utilize the hydraulic oil in the 2-level hydraulic oil pocket after supercharging to drive again three grades of pistons with different pressure ratios, the hydraulic oil in secondary booster cavity to be carried out to supercharging respectively from level Four piston, thereby drive the unlatching of air bleeding valve with different boost pressures, by the break-make of 3-position-3-way solenoid directional control valve control PA and AT hydraulic circuit and low-pressure hydraulic oil circuit, exhaust timing and the exhaust duration that can realize air bleeding valve are variable. the present invention is simple in structure, large to the free degree of air bleeding valve control, drives the charge oil pressure of hydraulic oil low, can further improve the economy of fuel and the discharge of internal combustion engine, is conducive to improve the power performance of internal combustion engine.
Description
Technical field
What the present invention relates to is a kind of engine, the specifically exhaust gear of engine.
Background technology
Gas extraction system is the important component part of Valve System of Internal Combustion Engine, and its Main Function is at official hourInterior the waste gas discharge combustion chamber after burning, exhaust phase place and exhaust duration economy, the internal combustion to fuel oilAcc power and discharge all have a significant impact. The valve actuating mechanism of tradition mechanical type camshaft actuated exhaust valve, valveThe machine driving moving through between bent axle and camshaft and camshaft and each cylinder valve controlRegularly, all the time, it is simple, effective, reliable and cheap that this mechanical drive mechanism is proved to be,But exhaust valve opening moment, duration and the valve lift etc. of this exhaust gear are on structural parametersBe changeless, can only ensure that internal combustion engine performance under a certain operating mode reaches best, this becomes applying working conditionIt is disadvantageous changing internal combustion engine frequently.
Summary of the invention
The object of the present invention is to provide that hydraulic-driven, exhaust phase place are controlled, driving pressure and exhaust durationVariable multi-stage booster valve exhaust gear
The object of the present invention is achieved like this:
Multi-stage booster valve exhaust gear of the present invention, is characterized in that: exhaust unit, one-level booster, twoLevel booster, hydraulic oil container, 3-position-3-way solenoid directional control valve; Exhaust unit comprise piston bush, hydraulic piston,Reseting spring sleeve, air bleeding valve, air bleeding valve shell, hydraulic piston be arranged in piston bush and with piston bush upper wallBetween form hydraulic cavities, piston bush is fixed on back-moving spring and puts, reseting spring sleeve is fixed on air bleeding valve shellUpper, back-moving spring and return spring holder are installed in reseting spring sleeve, back-moving spring be arranged on return spring holder andBetween air bleeding valve housing, the valve rod end of air bleeding valve is arranged in hydraulic piston, the valve head of air bleeding valve and exhaustDelivery valve seat on valve chest matches; One-level booster comprises booster housing, first stage piston, secondary workPlug, one-level hydraulic plunger, be hollow structure in booster housing, on booster housing, has hydraulic oilOutlet one, low-pressure hydraulic oil inlet one, the import of one-level hydraulic oil, the top of booster housing hollow structure is dividedBe not connected in hydraulic oil outlet one, low-pressure hydraulic oil inlet one, first stage piston, second piston, one-level liquidHydraulic plunger is arranged in booster housing from bottom to top successively, and first stage piston lower end and booster housing form oneLevel hydraulic fluid chamber, first stage piston lower end has one-level hydraulic pressure through hole, one-level hydraulic pressure through hole, one-level hydraulic fluid chamber,The import of one-level hydraulic oil is connected, and between one-level hydraulic plunger and the top of booster housing hollow structure, formsElementary booster cavity; Two-stage supercharger is identical with one-level supercharger structure, the hydraulic oil of one-level booster outlet one,Low-pressure hydraulic oil inlet one, the import of one-level hydraulic oil respectively with hydraulic oil outlet two, the low pressure of two-stage superchargerHydraulic oil import two, 2-level hydraulic oil inlet are corresponding, and the import of one-level hydraulic oil is communicated with 3-position-3-way electromagnetism and changesTo valve, 3-position-3-way solenoid directional control valve is communicated with hydraulic oil container by low-pressure hydraulic oil pipe and high-pressure and hydraulic oil pipe,Cleaner, hydraulic oil oil transfer pump, high-pressure and hydraulic oil pump are installed on high-pressure and hydraulic oil pipe, and low-pressure hydraulic oil pipe connectsLogical low-pressure hydraulic oil oil inlet pipe one, installs the first hydraulic pressure in line check valve on low-pressure hydraulic oil oil inlet pipe one, lowHydraulic fluid force feed oil inlet pipe one is communicated with low-pressure hydraulic oil inlet one and low-pressure hydraulic oil oil inlet pipe two, low-pressure hydraulic oilThe second hydraulic pressure in line check valve is installed on oil inlet pipe two, and low-pressure hydraulic oil oil inlet pipe two is communicated with low-pressure hydraulic oil and entersMouth two, hydraulic oil outlet one is communicated with 2-level hydraulic oil inlet, hydraulic pressure oil-out two-way by pressurization hydraulic oil pipeCross hydraulic oil pipe and be communicated with hydraulic cavities.
The present invention can also comprise:
1, the cross-sectional area that first stage piston is positioned at one-level hydraulic fluid chamber one end is greater than the cross-sectional area of its other end,One-level hydraulic oil import the maximum cross-section area is greater than one-level hydraulic plunger cross-sectional area, the import of one-level hydraulic oil withThe cut-away section that one-level hydraulic fluid chamber is connected is shaped as trapezoidal.
2, the one-level hydraulic pressure through hole having on first stage piston is greater than one-level near the cross-sectional area of second piston endThe cross-sectional area of hydraulic plunger, one-level hydraulic pressure through hole the maximum cross-section area is greater than one-level hydraulic plunger cross sectionLong-pending, one-level hydraulic pressure through hole is trapezoidal near the section shape of second piston end.
3, the maximum cross-section area of first stage piston is greater than the cross-sectional area of second piston, the cross section of second pistonThe long-pending cross-sectional area that is greater than one-level hydraulic plunger.
Advantage of the present invention is: the present invention is by the first stage piston on one-level booster and second piston differenceWith different pressure ratios to the hydraulic oil supercharging in elementary booster cavity, thereby supercharging drives on two-stage superchargerThree grades of pistons carry out supercharging with different pressure ratios to the hydraulic oil in secondary hydraulic cavities from level Four piston, and thenIn the process of exhaust valve opening, drive with different boost pressures, be conducive to reduce the fuel feeding that drives hydraulic oilPressure, the circulating direction of employing solenoid control hydraulic oil, large to the free degree of air bleeding valve control, can be flexiblyControl exhaust timing and exhaust duration, can further improve the discharge of internal combustion engine and the economy of fuel oil.
Brief description of the drawings
Fig. 1 is structural representation of the present invention;
Fig. 2 is elementary booster cavity and secondary booster cavity internal pressure change curve schematic diagram.
Detailed description of the invention
For example the present invention is described in more detail below in conjunction with accompanying drawing:
In conjunction with Fig. 1～2, the present invention is by hydraulic oil pipe 1, hydraulic cavities 2, hydraulic piston 3, air bleeding valve 4, multiplePosition spring base 5, back-moving spring 6, exhaust outlet 7, delivery valve seat 8, hydraulic oil outlet 29, secondary superchargingChamber 10,2-level hydraulic plunger 11, two-stage supercharger 12, level Four piston 13, three grades of pistons 14, secondary liquidPress through hole 15,2-level hydraulic oil pocket 16,2-level hydraulic oil inlet 17, low-pressure hydraulic oil inlet 2 18, threePosition three-way solenoid valve 19, high-pressure and hydraulic oil pump 20, hydraulic oil oil transfer pump 21, cleaner 22, hydraulic pressureFuel tank 23, low-pressure hydraulic oil pipe 24, one-level hydraulic oil import 25, one-level hydraulic fluid chamber 26, one-level hydraulic pressureThrough hole 27, first stage piston 28, hydraulic pressure in line check valve 29, second piston 30, one-level booster 31, oneLevel hydraulic plunger 32, elementary booster cavity 33, low-pressure hydraulic oil inlet 1, hydraulic oil outlet 1 and increasingHydraulic fluid pressuring oil pipe 36 forms. It is characterized in that: between first stage piston 28 and one-level booster 31 bodies, form one-levelHydraulic fluid chamber 26, one-level hydraulic fluid chamber 26 is by the one-level hydraulic oil import 25 on one-level booster 31 bodiesBe connected with 3-position-3-way solenoid directional control valve 19, on first stage piston 28, have one-level hydraulic pressure through hole 27, hydraulic pressureOil is when being communicated with one-level hydraulic fluid chamber 26 and being slided due to second piston 30 by one-level hydraulic pressure through hole 27 and one-levelThe hydraulic fluid chamber forming between piston 28, first stage piston 28 can reciprocatingly slide in one-level booster 31,First stage piston 28 is connected with second piston 30 as the piston bush of second piston 30, and second piston 30 canIn first stage piston 28, reciprocatingly slide, one-level hydraulic plunger 32 is due to the liquid of elementary booster cavity 33 interior hydraulic oilPressure-acting is closely connected with second piston 30, shape between one-level hydraulic plunger 32 and one-level booster 31 bodiesBecome elementary booster cavity 33, elementary booster cavity 33 enters by the low-pressure hydraulic oil having on one-level booster 31 bodiesMouthfuls 1 are communicated with hydraulic pressure in line check valves 29, hydraulic pressure in line check valve 29 by low-pressure hydraulic oil pipe 24 withHydraulic oil container 23 is connected, and elementary booster cavity 33 is by the hydraulic oil outlet having on one-level booster 31 bodiesOne 35 are connected with pressurization hydraulic oil pipe 36, and pressurization hydraulic oil pipe 36 is by opening on two-stage supercharger 12 bodiesSome 2-level hydraulic oil inlets 17 are connected with 2-level hydraulic oil pocket 16, three grades of pistons 14 and two-stage superchargerBetween 12 bodies, form on 16, three grades of pistons 14 of 2-level hydraulic oil pocket and have 2-level hydraulic through hole 15, hydraulic oilWhen being communicated with 2-level hydraulic oil pocket 16 and sliding due to level Four piston 13 by 2-level hydraulic through hole 15 and three grades of workThe hydraulic fluid chamber forming between plug 14, three grades of pistons 14 can reciprocatingly slide in two-stage supercharger 12, and threeLevel piston 14 is connected with level Four piston 13 as the piston bush of level Four piston 13, and level Four piston 13 can beIn three grades of pistons 14, reciprocatingly slide, 2-level hydraulic plunger 11 is due to the hydraulic pressure of secondary booster cavity 10 interior hydraulic oilPower effect is closely connected with level Four piston 13, between 2-level hydraulic plunger 11 and two-stage supercharger 12 bodies, formsSecondary booster cavity 10, secondary booster cavity 10 is by the low-pressure hydraulic oil inlet having on two-stage supercharger 12 bodies2 18 are communicated with hydraulic pressure in line check valve 29, and hydraulic pressure in line check valve 29 is by low-pressure hydraulic oil pipe 24 and liquidForce feed case 23 is connected, and secondary booster cavity 10 is by the hydraulic oil outlet two having on two-stage supercharger 12 bodies9 are connected with hydraulic oil pipe 1, and hydraulic oil pipe 1 is connected with the hydraulic cavities 2 of hydraulic piston 3 upper ends.
Fig. 1 is the overall structure schematic diagram of multi-stage booster valve exhaust gear of the present invention, comprises hydraulic oil pipe1, hydraulic cavities 2, hydraulic piston 3, air bleeding valve 4, return spring holder 5, back-moving spring 6, exhaust outlet 7,Delivery valve seat 8, hydraulic oil outlet 29, secondary booster cavity 10,2-level hydraulic plunger 11, two-stage supercharger12, level Four piston 13, three grades of pistons 14,2-level hydraulic through hole 15,2-level hydraulic oil pocket 16, secondary liquidForce feed import 17, low-pressure hydraulic oil inlet 2 18,3-position-3-way solenoid directional control valve 19, high-pressure and hydraulic oil pump20, hydraulic oil oil transfer pump 21, cleaner 22, hydraulic oil container 23, low-pressure hydraulic oil pipe 24, one-level hydraulic pressureOil inlet 25, one-level hydraulic fluid chamber 26, one-level hydraulic pressure through hole 27, first stage piston 28, hydraulic pressure oil-feed are unidirectionalValve 29, second piston 30, one-level booster 31, one-level hydraulic plunger 32, elementary booster cavity 33, low pressureHydraulic oil import 1, hydraulic oil outlet 1 and pressurization hydraulic oil pipe 36. First stage piston 28 increases with one-levelBetween depressor 31 bodies, form one-level hydraulic fluid chamber 26, one-level hydraulic fluid chamber 26 is by one-level booster 31 bodiesOn one-level hydraulic oil import 25 be connected with 3-position-3-way solenoid directional control valve 19A mouth, one-level hydraulic oil entersMouth 25 is greater than the cross-sectional area away from first stage piston 28 ends, one-level near the cross-sectional area of first stage piston 28 endsHydraulic oil import 25 the maximum cross-section areas are greater than the cross-sectional area of one-level hydraulic plunger 32, as shown in Figure 1,The import 25 of one-level hydraulic oil is trapezoidal near the section shape of first stage piston 28 ends, 3-position-3-way electromagnetic switchValve 19P mouth successively with high-pressure and hydraulic oil pump 20, hydraulic oil oil transfer pump 21, cleaner 22 and hydraulic oil container 23Be connected, 3-position-3-way solenoid directional control valve 19T mouth is connected with hydraulic oil container 23 by low-pressure hydraulic oil pipe 24Logical, on first stage piston 28, have one-level hydraulic pressure through hole 27, one-level hydraulic pressure through hole 27 is near second piston 30The cross-sectional area of end is greater than the cross-sectional area away from second piston 30 ends, and one-level hydraulic pressure through hole 27 is maximum transversalArea is greater than the cross-sectional area of one-level hydraulic plunger 32, and as shown in Figure 1, one-level hydraulic pressure through hole 27 is near twoThe section shape of level piston 30 ends is trapezoidal, and hydraulic oil is communicated with one-level hydraulic oil by one-level hydraulic pressure through hole 27Chamber 26 and the hydraulic fluid chamber forming while sliding due to second piston 30 and between first stage piston 28, first stage piston28 can reciprocatingly slide in one-level booster 31, and first stage piston 28 is as the piston bush of second piston 30Be connected with second piston 30, second piston 30 can reciprocatingly slide in first stage piston 28, one-level hydraulic columnPlug 32 action of hydraulic force due to elementary booster cavity 33 interior hydraulic oil are closely connected with second piston 30, one-levelHydraulic plunger 32 can reciprocatingly slide in one-level booster 31, one-level hydraulic plunger 32 and one-level boosterBetween 31 bodies, form elementary booster cavity 33, elementary booster cavity 33 is low by what have on one-level booster 31 bodiesHydraulic fluid force feed import 1 is communicated with hydraulic pressure in line check valve 29, and hydraulic pressure in line check valve 29 passes through low-pressure hydraulicOil pipe 24 is connected with hydraulic oil container 23, and elementary booster cavity 33 is by having on one-level booster 31 bodiesHydraulic oil outlet 1 is connected with pressurization hydraulic oil pipe 36, and pressurization hydraulic oil pipe 36 passes through two-stage superchargerThe 2-level hydraulic oil inlet 17 having on 12 bodies is connected with 2-level hydraulic oil pocket 16,2-level hydraulic oil inlet17 are greater than the cross-sectional area away from three grades of piston 14 ends, secondary liquid near the cross-sectional area of three grades of piston 14 endsForce feed import 17 the maximum cross-section areas are greater than the cross-sectional area of 2-level hydraulic plunger 11, as shown in Figure 1, and twoLevel hydraulic oil import 17 is trapezoidal near the section shape of three grades of piston 14 ends, and three grades of pistons 14 increase with secondaryBetween depressor 12 bodies, form on 16, three grades of pistons 14 of 2-level hydraulic oil pocket and have 2-level hydraulic through hole 15, twoLevel hydraulic pressure through hole 15 is greater than the cross section away from level Four piston 13 ends near the cross-sectional area of level Four piston 13 endsLong-pending, 2-level hydraulic through hole 15 the maximum cross-section areas are greater than 2-level hydraulic plunger 11 cross-sectional areas, as Fig. 1 instituteShow, 2-level hydraulic through hole 15 is trapezoidal near the section shape of level Four piston 13 ends, and hydraulic oil passes through secondaryWhen hydraulic pressure through hole 15 is communicated with 2-level hydraulic oil pocket 16 and slides due to level Four piston 13 and three grades of pistons 14 itBetween form hydraulic fluid chamber, three grades of pistons 14 can reciprocatingly slide in two-stage supercharger 12, three grades of pistons14 piston bush as level Four piston 13 are connected with level Four piston 13, and level Four piston 13 can be three grades of workIn plug 14, reciprocatingly slide, 2-level hydraulic plunger 11 is due to the action of hydraulic force of secondary booster cavity 10 interior hydraulic oilClosely be connected with level Four piston 13, between 2-level hydraulic plunger 11 and two-stage supercharger 12 bodies, form secondary increasingPress chamber 10,2-level hydraulic plunger 11 can reciprocatingly slide in two-stage supercharger 12, secondary booster cavity 10Be communicated with hydraulic pressure in line check valve 29 by the low-pressure hydraulic oil inlet 2 18 having on two-stage supercharger 12 bodies,Hydraulic pressure in line check valve 29 is connected with hydraulic oil container 23 by low-pressure hydraulic oil pipe 24, secondary booster cavity10 are connected with hydraulic oil pipe 1 by the hydraulic oil outlet 29 having on two-stage supercharger 12 bodies, hydraulic pressureOil pipe 1 is connected with the hydraulic cavities 2 of hydraulic piston 3 upper ends, and hydraulic piston 3 upper ends are due in hydraulic cavities 2The action of hydraulic force of hydraulic oil is close to air bleeding valve 4, and return spring holder 5 is fixed on the valve rod of air bleeding valve 4,Motion together thereupon, back-moving spring 6 is pressed on return spring holder 5, and air bleeding valve 4 is by delivery valve seat 8Spacing. In the time that 3-position-3-way solenoid directional control valve 19 is in meta, A mouth, P mouth and T mouth all do not connect to each otherLogical, each charged piston in one-level booster 31 and two-stage supercharger 12 and hydraulic plunger all keep initialPosition, does not move; In the time that 3-position-3-way solenoid directional control valve 19 commutates to right position, PA path is connected, hydraulic pressureHydraulic oil in fuel tank 23 is input to high-pressure and hydraulic oil pump 20 via cleaner 22 by hydraulic oil oil transfer pump 21,Hydraulic oil after the interior supercharging of the high-pressure and hydraulic oil pump 20 3-position-3-way solenoid directional control valve 19 of flowing through, flows through hydraulic pressureOil pipe flows into one-level hydraulic fluid chamber 26 by one-level hydraulic oil import 25, because the import 25 of one-level hydraulic oil is closeThe cross-sectional area of first stage piston 28 ends is greater than the cross-sectional area away from first stage piston 28 ends, as shown in Figure 1,The import 25 of one-level hydraulic oil is trapezoidal near the section shape of first stage piston 28 ends, and the hydraulic oil of inflow passes throughAfter one-level hydraulic oil import 25, act on the active area that first stage piston 28 is larger, again because one-level is aliveThe maximum cross-section area of plug 28 is greater than the cross-sectional area of second piston 30, and the cross-sectional area of second piston 30 is largeIn the cross-sectional area of one-level hydraulic plunger 32, along with the interior continuous infeed high-pressure and hydraulic of one-level hydraulic fluid chamber 26Oil, due to the pressure differential at first stage piston 28 and one-level hydraulic plunger 32 two ends, it is subject to force unbalance, one-levelPiston 28 drives second piston 30 to promote one-level hydraulic plunger 32 and moves upward, now, and elementary booster cavityLow-pressure hydraulic oil in 33 is by first stage piston 28 superchargings, the pressurization hydraulic oil pipe 36 of flowing through of the hydraulic oil after superchargingFlow into 2-level hydraulic chamber 16 by 2-level hydraulic oil inlet 17, because 2-level hydraulic oil inlet 17 is near three gradesThe cross-sectional area of piston 14 ends is greater than the cross-sectional area away from three grades of piston 14 ends, as shown in Figure 1, and secondaryHydraulic oil import 17 is trapezoidal near the section shape of three grades of piston 14 ends, and the hydraulic oil of inflow passes through secondaryAfter hydraulic oil import 17, act on the active area that three grades of pistons 14 are larger, again because three grades of pistons 14The maximum cross-section area be greater than the cross-sectional area of level Four piston 13, the cross-sectional area of level Four piston 13 is greater than twoThe cross-sectional area of level hydraulic plunger 11, along with the interior continuous infeed boost fluid force feed of 2-level hydraulic oil pocket 16,Due to the pressure differential at three grades of pistons 14 and 2-level hydraulic plunger 11 two ends, it is subject to force unbalance, three grades of pistons14 drive level Four piston 13 to promote 2-level hydraulic plunger 11 moves upward, now, and in secondary booster cavity 10Low-pressure hydraulic oil by three grades of piston 14 superchargings, when the pressure of secondary booster cavity 10 interior hydraulic oil is greater than exhaustWhen the gentle gas in the jar of valve back-moving spring 6 upwards pressure sum to air bleeding valve 4, air bleeding valve 4 departs from air bleeding valveValve seat 8, air bleeding valve 4 start open, waste gas is discharged via exhaust outlet 7, and at air bleeding valve 4 from firm unlatchingReach in the opening process of maximum lift, along with air bleeding valve 4 and the increase of delivery valve seat 8 distances, valveAperture area increases, and gas gas in the jar increases by the discharge rate of exhaust outlet 7, and cylinder pressure reduces,The suffered gas pressure upwards of air bleeding valve 4 reduces, now, if continued by a pressure ratio secondary superchargingHydraulic oil supercharging in chamber 10 certainly will require high-pressure and hydraulic oil pump 20 constantly to feed the hydraulic oil of high pressure, causesThe loss of the loss of extra mechanical work and high pressure liquid force feed energy, thus the present invention at air bleeding valve 4 from just openingOpening in the opening process that reaches maximum lift adopts first stage piston 28 and second piston 30 respectively with differentPressure ratio, to the hydraulic oil supercharging in elementary booster cavity 33, recycles 13 points, three grades of pistons 14 and level Four pistonNot with different pressure ratios to the hydraulic oil supercharging in secondary booster cavity 10, thereby drive with different hydraulic pressuresThe unlatching of moving air bleeding valve 4, when first stage piston 28 superchargings in one-level booster 31 drive one-level hydraulic plunger32, and then promote three grades of pistons, 14 superchargings driving 2-level hydraulic plungers 11, the pressure foot in hydraulic cavities 3After enough large, air bleeding valve 4 is opened, when air bleeding valve 4 is opened to certain lift but does not reach maximum lift, and one-levelPiston 28 and three grades of pistons 14 are limited, and first stage piston 28 and three grades of pistons 14 stop continuing to move upward,Now, hydraulic oil drives second piston 30 to continue by the one-level hydraulic pressure through hole 27 having on first stage piston 28The upwards hydraulic oil in the elementary booster cavity 33 of supercharging, flow through pressurization hydraulic oil pipe 36 of the hydraulic oil after supercharging is logicalCrossing three grades of 2-level hydraulic through holes 15 on piston 14 drives level Four piston to continue the secondary hydraulic cavities 10 of upwards superchargingInterior hydraulic oil, promotes air bleeding valve hydraulic piston 3 and continues to move downward together with air bleeding valve 4, until air bleeding valve4 reach maximum lift opens completely. In the time that 3-position-3-way solenoid directional control valve 19 commutates to left position, AT pathConnect, the high pressure liquid force feed in one-level hydraulic fluid chamber 26 is flowed through through 3-position-3-way solenoid directional control valve 19 rapidlyLow-pressure hydraulic oil pipe 24 flow back in hydraulic oil container 23, now, due to the effect of pressure differential, elementary superchargingHydraulic oil after the interior supercharging in chamber 33 promotes one-level hydraulic plunger 32 and drives second piston 30 to promote first stage piston28 are seated in extreme lower position, same, and the hydraulic oil after the interior supercharging of secondary booster cavity 10 promotes 2-level hydraulicPlunger 11 drives level Four piston 13 to promote three grades of pistons 14 and is seated in extreme lower position, the supercharging in hydraulic cavities 2After hydraulic fluid pressure reduce rapidly, air bleeding valve 4 again falls under the elastic force effect of air bleeding valve back-moving spring 6Seat to air bleeding valve valve seat 8, because air bleeding valve 4 various pieces all can exist the leakage of hydraulic oil, be also forAvoid the die-offing due to pressure in descending process due to one-level hydraulic plunger 32 and 2-level hydraulic plunger 11Cause vacuumizing of hydraulic oil, in hydraulic oil, produce bubble etc., elementary booster cavity 33 and secondary booster cavityHydraulic oil in 10 carries out supplementing of hydraulic oil from hydraulic oil container 23 by hydraulic pressure in line check valve 29. Figure2 is the elementary booster cavity 33 of multi-stage booster valve exhaust gear of the present invention and the interior hydraulic oil of secondary booster cavity 10Pressure is along with the schematic diagram of time changing curve. As seen from Figure 2, elementary booster cavity 33 interior hydraulic oilPressure is less with respect to the pressure of secondary hydraulic cavities, but because three grades of pistons 14 and level Four piston 13 are to twoThe different supercharging section ratio of level hydraulic plunger 11, makes to adopt less hydraulic pressure also can supercharging to becomeLarge hydraulic pressure. The present invention is by first stage piston 28 and second piston 30 and one on one-level booster 31The different pressure ratio of level hydraulic plunger 32, carries out supercharging to the hydraulic oil in elementary booster cavity 33, therebyThree grades of pistons 14 on supercharging two-stage supercharger 12 and level Four piston 13, and then the secondary booster cavity 10 of superchargingInterior hydraulic oil, finally drives the unlatching of air bleeding valve 4 with different boost pressures, the present invention can realizeDifferent Pressure control in air bleeding valve 4 opening processes, by controlling 3-position-3-way solenoid directional control valve 19The break-make moment of PA, AT oil circuit, can control exhaust timing and the exhaust duration of air bleeding valve 4, can enterOne step is improved the economy of fuel and the discharge of internal combustion engine, has improved the power performance of internal combustion engine. Above-mentioned enforcementMode is one of mode of the invention process, and the present invention is not only confined to this kind of embodiment, thisInvention can be by the interior first stage piston 28 of one-level booster 31 and second piston 30 and two-stage supercharger 12Three grades of piston 14 operating positions different with level Four piston 13 coordinate realizes different supercharging modes, equally canTo increase boost pressure that the number of booster realizes multilevel more to reduce the charge oil pressure of hydraulic oil.
Multi-stage booster valve exhaust gear of the present invention comprises hydraulic oil pipe, hydraulic cavities, hydraulic piston, exhaustValve, return spring holder, back-moving spring, exhaust outlet, delivery valve seat, hydraulic oil outlet two, secondary booster cavity,2-level hydraulic plunger, two-stage supercharger, level Four piston, three grades of pistons, 2-level hydraulic through hole, 2-level hydraulicOil pocket, 2-level hydraulic oil inlet, low-pressure hydraulic oil inlet two, 3-position-3-way solenoid directional control valve, high-pressure and hydraulicOil pump, hydraulic oil oil transfer pump, cleaner, hydraulic oil container, low-pressure hydraulic oil pipe, the import of one-level hydraulic oil,One-level hydraulic fluid chamber, one-level hydraulic pressure through hole, first stage piston, hydraulic pressure in line check valve, second piston, one-levelBooster, one-level hydraulic plunger, elementary booster cavity, low-pressure hydraulic oil inlet one, hydraulic oil outlet one and increasingHydraulic fluid pressuring oil pipe. Between first stage piston and one-level supercharging body, form one-level hydraulic fluid chamber, one-level supercharging bodyOn have the import of one-level hydraulic oil, on first stage piston, have one-level hydraulic pressure through hole, one-level hydraulic pressure through hole be communicated with oneLevel hydraulic fluid chamber and the hydraulic fluid chamber forming while sliding due to second piston and between first stage piston, first stage pistonPiston bush as second piston is connected with second piston, and second piston can reciprocatingly slide in first stage piston,Between one-level hydraulic plunger and one-level supercharging body, form elementary booster cavity, elementary booster cavity passes through pressurization hydraulicOil pipe is connected with 2-level hydraulic oil pocket, between three grades of pistons and two-stage supercharging body, forms 2-level hydraulic oil pocket,On three grades of pistons, have 2-level hydraulic through hole, 2-level hydraulic through hole be communicated with 2-level hydraulic oil pocket and due to level Four liveWhen plug slides with three grades of pistons between the hydraulic fluid chamber that forms, three grades of pistons as the piston bush of level Four piston andLevel Four piston is connected, and level Four piston can reciprocatingly slide in three grades of pistons, and 2-level hydraulic plunger and secondary increaseBetween depressor body, form secondary booster cavity, secondary booster cavity goes out by the hydraulic oil having on two-stage supercharging bodyMouth two is connected with hydraulic oil pipe, and hydraulic oil pipe is connected with the hydraulic cavities of hydraulic piston upper end.
The one-level hydraulic oil import having on one-level supercharging body is greater than far near the cross-sectional area of first stage piston endFrom the cross-sectional area of first stage piston end, one-level hydraulic oil import the maximum cross-section area is greater than one-level hydraulic plunger horizontal strokeSectional area, the import of one-level hydraulic oil is trapezoidal near the section shape of first stage piston end.
The 2-level hydraulic oil inlet having on two-stage supercharging body is greater than far near the cross-sectional area of three grades of piston endsFrom the cross-sectional area of three grades of piston ends, 2-level hydraulic oil inlet the maximum cross-section area is greater than 2-level hydraulic plunger horizontal strokeSectional area, 2-level hydraulic oil inlet is trapezoidal near the section shape of three grades of piston ends.
The one-level hydraulic pressure through hole having on first stage piston is greater than one-level liquid near the cross-sectional area of second piston endThe cross-sectional area of hydraulic plunger, one-level hydraulic pressure through hole the maximum cross-section area is greater than one-level hydraulic plunger cross-sectional area,One-level hydraulic pressure through hole is trapezoidal near the section shape of second piston end.
The 2-level hydraulic through hole having on three grades of pistons is greater than secondary liquid near the cross-sectional area of level Four piston endThe cross-sectional area of hydraulic plunger, 2-level hydraulic through hole the maximum cross-section area is greater than 2-level hydraulic plunger cross-sectional area,2-level hydraulic through hole is trapezoidal near the section shape of level Four piston end.
The maximum cross-section area of first stage piston is greater than the cross-sectional area of second piston, the cross-sectional area of second pistonBe greater than the cross-sectional area of one-level hydraulic plunger.
The maximum cross-section area of three grades of pistons is greater than the cross-sectional area of level Four piston, the cross-sectional area of level Four pistonBe greater than the cross-sectional area of 2-level hydraulic plunger.
Claims (5)
1. multi-stage booster valve exhaust gear, is characterized in that: comprise exhaust unit, one-level booster, twoLevel booster, hydraulic oil container, 3-position-3-way solenoid directional control valve; Exhaust unit comprise piston bush, hydraulic piston,Reseting spring sleeve, air bleeding valve, air bleeding valve shell, hydraulic piston be arranged in piston bush and with piston bush upper wallBetween form hydraulic cavities, piston bush is fixed on back-moving spring and puts, reseting spring sleeve is fixed on air bleeding valve shellUpper, back-moving spring and return spring holder are installed in reseting spring sleeve, back-moving spring be arranged on return spring holder andBetween air bleeding valve housing, the valve rod end of air bleeding valve is arranged in hydraulic piston, the valve head of air bleeding valve and exhaustDelivery valve seat on valve chest matches; One-level booster comprises booster housing, first stage piston, secondary workPlug, one-level hydraulic plunger, be hollow structure in booster housing, on booster housing, has hydraulic oilOutlet one, low-pressure hydraulic oil inlet one, the import of one-level hydraulic oil, the top of booster housing hollow structure is dividedBe not connected in hydraulic oil outlet one, low-pressure hydraulic oil inlet one, first stage piston, second piston, one-level liquidHydraulic plunger is arranged in booster housing from bottom to top successively, and first stage piston lower end and booster housing form oneLevel hydraulic fluid chamber, first stage piston lower end has one-level hydraulic pressure through hole, one-level hydraulic pressure through hole, one-level hydraulic fluid chamber,The import of one-level hydraulic oil is connected, and between one-level hydraulic plunger and the top of booster housing hollow structure, formsElementary booster cavity; Two-stage supercharger is identical with one-level supercharger structure, the hydraulic oil of one-level booster outlet one,Low-pressure hydraulic oil inlet one, the import of one-level hydraulic oil respectively with hydraulic oil outlet two, the low pressure of two-stage superchargerHydraulic oil import two, 2-level hydraulic oil inlet are corresponding, and the import of one-level hydraulic oil is communicated with 3-position-3-way electromagnetism and changesTo valve, 3-position-3-way solenoid directional control valve is communicated with hydraulic oil container by low-pressure hydraulic oil pipe and high-pressure and hydraulic oil pipe,Cleaner, hydraulic oil oil transfer pump, high-pressure and hydraulic oil pump are installed on high-pressure and hydraulic oil pipe, and low-pressure hydraulic oil pipe connectsLogical low-pressure hydraulic oil oil inlet pipe one, installs the first hydraulic pressure in line check valve on low-pressure hydraulic oil oil inlet pipe one, lowHydraulic fluid force feed oil inlet pipe one is communicated with low-pressure hydraulic oil inlet one and low-pressure hydraulic oil oil inlet pipe two, low-pressure hydraulic oilThe second hydraulic pressure in line check valve is installed on oil inlet pipe two, and low-pressure hydraulic oil oil inlet pipe two is communicated with low-pressure hydraulic oil and entersMouth two, hydraulic oil outlet one is communicated with 2-level hydraulic oil inlet, hydraulic pressure oil-out two-way by pressurization hydraulic oil pipeCross hydraulic oil pipe and be communicated with hydraulic cavities.
2. multi-stage booster valve exhaust gear according to claim 1, is characterized in that: first stage pistonThe cross-sectional area that is positioned at one-level hydraulic fluid chamber one end is greater than the cross-sectional area of its other end, the import of one-level hydraulic oilThe maximum cross-section area is greater than one-level hydraulic plunger cross-sectional area, the import of one-level hydraulic oil and one-level hydraulic fluid chamber phaseThe cut-away section being communicated with is shaped as trapezoidal.
3. multi-stage booster valve exhaust gear according to claim 1 and 2, is characterized in that: one-levelThe one-level hydraulic pressure through hole that has on piston is greater than one-level hydraulic plunger near the cross-sectional area of second piston endCross-sectional area, one-level hydraulic pressure through hole the maximum cross-section area is greater than one-level hydraulic plunger cross-sectional area, one-level liquidPressing through hole is trapezoidal near the section shape of second piston end.
4. multi-stage booster valve exhaust gear according to claim 1 and 2, is characterized in that: one-levelThe maximum cross-section area of piston is greater than the cross-sectional area of second piston, and the cross-sectional area of second piston is greater than one-levelThe cross-sectional area of hydraulic plunger.
5. multi-stage booster valve exhaust gear according to claim 3, is characterized in that: first stage pistonThe maximum cross-section area be greater than the cross-sectional area of second piston, the cross-sectional area of second piston is greater than one-level hydraulic pressureThe cross-sectional area of plunger.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410107950.4A CN103953413B (en) | 2014-03-21 | 2014-03-21 | Multi-stage booster valve exhaust gear |
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| CN201410107950.4A CN103953413B (en) | 2014-03-21 | 2014-03-21 | Multi-stage booster valve exhaust gear |
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| CN103953413A CN103953413A (en) | 2014-07-30 |
| CN103953413B true CN103953413B (en) | 2016-05-04 |
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| GB396105A (en) * | 1932-02-01 | 1933-08-03 | Werkspoor Nv | Improved starting device for an internal combustion engine |
| DE3815668A1 (en) * | 1988-05-07 | 1989-11-16 | Bosch Gmbh Robert | VALVE CONTROL DEVICE WITH SOLENOID VALVE FOR INTERNAL COMBUSTION ENGINES |
| DK176152B1 (en) * | 2000-07-10 | 2006-10-16 | Man B & W Diesel As | Method of activating an exhaust valve for an internal combustion engine and such an exhaust valve |
| JP2011058458A (en) * | 2009-09-11 | 2011-03-24 | Toyota Motor Corp | Oil supply device of internal combustion engine |
| CN103244231B (en) * | 2013-05-03 | 2015-04-29 | 深圳市特尔佳科技股份有限公司 | Variable-pressure gas release braking method and variable-pressure gas release brake for implementing same |
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