CN100371573C

CN100371573C - Valve operating device for internal combustion engine

Info

Publication number: CN100371573C
Application number: CNB200510004441XA
Authority: CN
Inventors: 井元丰; 田边和也; 堤崎高司
Original assignee: Honda Motor Co Ltd
Current assignee: Honda Motor Co Ltd
Priority date: 2004-01-20
Filing date: 2005-01-17
Publication date: 2008-02-27
Anticipated expiration: 2025-01-17
Also published as: KR20050076633A; CN1644882A; MY139856A; TWI303285B; AR047427A1; KR100582654B1; WO2005068789A1; TW200530490A; JP2005207256A; JP4274425B2

Abstract

The object of this invention is to prevent or suppress the blow back of intake air and suppress the lowering of fuel economy due to the lowering of an effective expansion ratio by starting to open an intake valve when a pressure in a combustion chamber is low. The valve characteristic variable mechanism M of a valve system 40 controls an internal EGR rate by controlling an overlapping period and a non-overlapping period. The valve characteristic variable mechanism M comprises a control mechanism M3 swinging an intake link mechanism connected to an intake cam and an exhaust link mechanism connected to an exhaust cam 54 about a camshaft 50 and a drive mechanism driving the control mechanism M3. The control mechanism M3 connects the drive mechanism to each link mechanism so that the spark-retard angle of an intake valve 22 at an opening time by an intake link mechanism is larger than the spark-advance angle of an exhaust valve 23 at a closing timing by an exhaust link mechanism relative to the same drive amount of the drive mechanism in the increasing direction of an internal EGR rate.

Description

The valve device of internal-combustion engine

Technical field

The present invention relates to have the valve device of internal-combustion engine of valve characteristic changing mechanism of the valve event characteristic of control intake valve and exhaust valve, say in detail, relate to the switch timing that valve characteristic changing mechanism changes intake valve and exhaust valve, control cover time and non-cover time, thus, the valve device of the internal-combustion engine of control internal EGR (exhaust gas recirculatioon) rate.

Background technique

As everyone knows,, carry out internal EGR by residual a part of burnt gas in the firing chamber, thus, reduce internal-combustion engine loss of suction, improve the fuel consumption performance, and reduce the NOx in the exhaust and improve exhaust purification performance.And, as the device that is used to carry out internal EGR, controls the valve event characteristic of intake valve and exhaust valve, for example, the variable stigmatic opening transmission device of the internal-combustion engine of in patent documentation 1, delivering.This variable stigmatic opening transmission device has the variable lift valve operating mechanism of air inlet reveal and exhaust valve side.Each variable lift valve operating mechanism has: be fixed on the eccentric cam on the live axle that rotates with the bent axle interlock; Can be entrenched in the connecting rod of the annular on the periphery of this eccentric cam rotationally; Rocking arm, it can be entrenched in off-centre rotationally and be fixed on substantially on the periphery of the driving cam on the Control Shaft that disposes abreast with live axle, and one end pivot is automatically connected on the annular connecting rod; Oscillating cam, it can be entrenched on the live axle rotationally, and is connected the other end of rocking arm by connecting rod.The oscillating cam of switch intake valve and exhaust valve, to rotate Control Shaft according to the operating condition of internal-combustion engine, the distance of the center of shaking of change rocking arm and the center of rotation of live axle, thus, the maximum lift amount and the operating angle that change intake valve and exhaust valve shake in this wise.And Control Shaft will reduce along with the maximum lift amount of intake valve and exhaust valve, make the maximum lift timing at intake valve to the retardation angle side shifting, rotate control in this wise to the lead angle side shifting at exhaust valve.The result, intake valve open the also big retardation angle of leading angle that forms valve timing than its timing of holding one's breath, a timing of holding one's breath of exhaust valve forms opens the also big lead angle of hysteresis angle of valve timing than it, thereby, can utilize combustion gas residual in the firing chamber to realize improving cleaning of fuel consumption and exhaust.

(patent documentation 1) spy opens the 2001-3721 communique.

, when carrying out internal EGR, when residual burnt gas causes pressure in IVO Inlet Valve Open firing chamber valve timing high in by the firing chamber, the air inlet blowback can take place, make the air that is difficult to flow into established amount in the firing chamber.Thereby, by reducing the cover time or increase the non-cover time when improving the internal EGR rate, in order to prevent or suppress the air inlet blowback, make the air quantity inflow firing chamber of needs that the pressure in IVO Inlet Valve Open firing chamber valve timing is low more to be thought with regard to unreasonable as far as possible.In addition, in present technology,, maximize so be formed for controlling the changeable mechanism of the valve event characteristic of intake valve and exhaust valve because live axle and Control Shaft be separately positioned in each variable lift valve operating mechanism of air inlet reveal and exhaust valve side.And, when the opening and close timing that makes intake valve or exhaust valve forms lead angle or retardation angle, if exhaust close to open valve timing slow excessively, will cause the exhaust loss increase of combustion gas, the thermal efficiency to reduce; In addition, if intake valve to open valve timing too early, just can not suck enough fresh airs, output power descends, combustion instability.

Summary of the invention

The present invention is a mirror with above-mentioned problem, and the purpose of a first aspect of the present invention～second aspect is to begin to open intake valve at the low state of chamber pressure, to prevent or to suppress the air inlet blowback.In addition, the purpose of first and second aspect of the present invention is the miniaturization of realization valve characteristic changing mechanism, simplifies the structure.The purpose of the third aspect is to realize simplifying the structure of valve characteristic changing mechanism.

A first aspect of the present invention is the valve device of internal-combustion engine, it has the valve characteristic changing mechanism of the valve event characteristic of controlling intake valve and exhaust valve respectively, above-mentioned valve characteristic changing mechanism changes opening and close timing, control cover time and the non-cover time of above-mentioned intake valve and above-mentioned exhaust valve, thus, control internal EGR rate.Wherein, above-mentioned valve characteristic changeable mechanism has: the camshaft that rotates with the bent axle interlock of above-mentioned internal-combustion engine; Be connected according to the air-breathing double-action mechanism on the air inlet cam of the above-mentioned intake valve of rotating switch of above-mentioned camshaft; Be connected according to the exhaust double-action mechanism on the exhaust cam of the above-mentioned exhaust valve of rotating switch of above-mentioned camshaft; Making above-mentioned each double-action mechanism is center control mechanism that shakes and the driving mechanism that drives above-mentioned control mechanism with above-mentioned camshaft.By reducing the above-mentioned cover time or increasing the above-mentioned non-cover time and when improving on the above-mentioned internal EGR rate direction, connect above-mentioned driving mechanism and above-mentioned each double-action mechanism so that the hysteresis angle of the above-mentioned IVO Inlet Valve Open timing that is formed by above-mentioned air-breathing double-action mechanism is closed the leading angle of timing greater than the above-mentioned exhaust valve that is formed by above-mentioned exhaust double-action mechanism by the above-mentioned control mechanism of above-mentioned drive mechanism.

Thus, increasing when valve characteristic changing mechanism on the direction of internal EGR rate, when reducing the cover time or increasing non-cover time, the hysteresis angle of IVO Inlet Valve Open timing increases than the leading angle that exhaust valve closes timing; Thereby, when exhaust valve close timing form lead angle, when remaining in the increased pressure of the burnt gas in the firing chamber, close the situation of the leading angle of timing with valve that hysteresis angle that the valve of intake valve is opened timing is less than or equal to exhaust valve and compare, open during the lower state of the pressure of intake valve in the firing chamber.

And above-mentioned control mechanism has: controlling component, and it is by above-mentioned drive mechanism, can move being parallel to the rotary centerline that comprises camshaft and being parallel on the direction of datum plane of cylinder-bore axis; Air-breathing control link, it is dynamically connected, is dynamically connected by above-mentioned air-breathing double-action mechanism pivot at the second air-breathing joint by above-mentioned controlling component pivot at the first air-breathing joint; The exhaust control link, it is dynamically connected, is dynamically connected by above-mentioned exhaust double-action mechanism pivot at the second exhaust joint by above-mentioned controlling component pivot at the first exhaust joint.The moving relative said reference of the center line plane of the pivot of moving center line of the pivot of the above-mentioned first air-breathing joint and the above-mentioned first exhaust joint is configured in a side with being parallel to above-mentioned rotary centerline, and the moving centreline configuration of the pivot of the above-mentioned second air-breathing joint is in an above-mentioned side; The pivot of the above-mentioned second exhaust joint moves the relative said reference of center line plane, is configured in opposite side.Thus, when above-mentioned controlling component moved, above-mentioned air-breathing double-action mechanism was that the center is shaken with the shaking quantity greater than above-mentioned exhaust double-action mechanism with above-mentioned camshaft.

Like this.When the valve event characteristic of the leading angle that closes timing for the hysteresis angle that obtains the IVO Inlet Valve Open timing greater than exhaust valve and when air-breathing double-action mechanism and the shared controlling component of exhaust double-action mechanism are moved, because the moving center line relative datum plane of pivot of the moving center line of the pivot of the first air-breathing joint and the first exhaust joint, be configured in a side, the moving center line of the pivot of the second air-breathing joint is configured in an above-mentioned side, the pivot of the second exhaust joint moves center line relative datum plane, be configured in opposite side, therefore, making air-breathing control link and exhaust control link is that the center is shaken with the camshaft by air-breathing double-action mechanism and the exhaust double-action mechanism that the moving center line pivot of pivot that divides at the moving center line of pivot of the second air-breathing joint of the both sides of datum plane configuration and the second exhaust joint is being dynamically connected respectively, so that the shaking quantity of air-breathing double-action mechanism is greater than the shaking quantity of exhaust double-action mechanism.

A second aspect of the present invention is, valve device at the described internal-combustion engine of first aspect, above-mentioned control mechanism has: controlling component, its by above-mentioned drive mechanism, can move being parallel to the rotary centerline that comprises camshaft and being parallel on the direction of datum plane of cylinder-bore axis; Air-breathing control link, it is dynamically connected by above-mentioned controlling component pivot at the first air-breathing joint, is dynamically connected by above-mentioned air-breathing double-action mechanism pivot at the second air-breathing joint; The exhaust control link, it is dynamically connected, is dynamically connected by above-mentioned exhaust double-action mechanism pivot at the second exhaust joint by above-mentioned controlling component pivot at the first exhaust joint.The moving center line of the pivot of moving center line of the pivot of the above-mentioned first air-breathing joint and above-mentioned exhaust joint is parallel to above-mentioned rotary centerline configuration; The pivot of the above-mentioned second air-breathing joint moves the relative said reference of center line plane, is configured in a side; The pivot of the above-mentioned second exhaust joint moves the relative said reference of center line plane, is configured in opposite side.The length of above-mentioned air-breathing control link is longer than the length of above-mentioned exhaust control link, and like this, when above-mentioned controlling component moved, above-mentioned air-breathing double-action mechanism should be that the center is shaken with above-mentioned camshaft with the shaking quantity greater than above-mentioned exhaust double-action mechanism.

Thus, when the valve event characteristic of the leading angle that closes timing for the hysteresis angle that obtains the IVO Inlet Valve Open timing greater than exhaust valve and when air-breathing double-action mechanism and the shared controlling component of exhaust double-action mechanism are moved, making length of connecting rod is that the center is shaken with the camshaft by air-breathing double-action mechanism and the exhaust double-action mechanism that the moving center line pivot of pivot that divides at the moving center line of pivot of the second air-breathing joint of the both sides of datum plane configuration and the second exhaust joint is dynamically connected respectively than the long air-breathing control link of exhaust control link and exhaust control link, so that the shaking quantity of air-breathing double-action mechanism is greater than the shaking quantity of exhaust double-action mechanism.

A third aspect of the present invention is the valve device of a described internal-combustion engine in first～second aspect, above-mentioned air-breathing double-action mechanism has the moving portion of air-breathing pivot, and it is held, and the rotary centerline with above-mentioned camshaft is the moving center line of pivot that the center is shaken when above-mentioned air-breathing double-action mechanism is shaken; Above-mentioned exhaust double-action mechanism has the moving portion of exhaust pivot, and it is held when above-mentioned exhaust double-action mechanism is shaken with above-mentioned rotary centerline is the moving center line of pivot that the center is shaken; The distance of moving the above-mentioned rotary centerline of the moving center line distance of pivot of center line and the moving portion of described exhaust pivot by the pivot that makes the moving portion of above-mentioned air-breathing pivot is equidistant, and the moving center line of the pivot of the moving portion of above-mentioned air-breathing pivot is than the more close vertical plane that comprises the rotary centerline while perpendicular to described datum plane of the moving center line of the pivot of the moving portion of described exhaust pivot, like this, by the above-mentioned control mechanism of above-mentioned drive mechanism the time, above-mentioned air-breathing double-action mechanism is used than being that the center is shaken the big shaking quantity of above-mentioned exhaust cam to make above-mentioned air inlet cam be that the center is shaken with above-mentioned camshaft by above-mentioned exhaust double-action mechanism with above-mentioned camshaft.

Like this, when air-breathing double-action mechanism and exhaust double-action mechanism are shaken, because having, air-breathing double-action mechanism is positioned at than the moving center line of the pivot of exhaust double-action mechanism near the moving center line of the locational pivot of camshaft center of rotation, so, it is that the center is shaken with the camshaft that control mechanism makes air inlet cam and exhaust cam by air-breathing double-action mechanism and exhaust double-action mechanism, so that air inlet cam is bigger than exhaust cam shaking quantity.

The effect of invention

According to the described invention of first aspect, produce following effect, promptly, when valve door characteristic changing mechanism, when the direction of internal EGR rate increase is controlled cover time and non-cover time, because intake valve begins out valve at the low state of chamber pressure, so can prevent and suppress the air inlet blowback.

And, except that the invention effect of having stated, also produce following effect, promptly, because controlling component at air-breathing double-action mechanism and the shared control mechanism of exhaust double-action mechanism, and because the moving center line of the pivot of the first air-breathing joint, the pivot of the first exhaust joint moves center line, the miniaturization of valve characteristic changing mechanism of valve event characteristic of leading angle of timing and the simplification of structure thereof are closed in the configuration on the moving center line relative datum plane of pivot of the moving center line of the pivot of the second air-breathing joint and the second exhaust joint, the hysteresis angle that therefore can realize being used to obtaining the IVO Inlet Valve Open timing greater than exhaust valve.

Invent according to second aspect, except that the invention effect of having stated, also produce following effect, promptly, because controlling component at air-breathing double-action mechanism and the shared control mechanism of exhaust double-action mechanism, also because the moving center line of pivot of the moving center line of the pivot of the second air-breathing joint and the second exhaust joint divides in configuration of the both sides of datum plane and air-breathing control link longer than the length of exhaust control link, therefore, the hysteresis angle that can realize being used to obtaining the IVO Inlet Valve Open timing is closed the miniaturization of valve characteristic changing mechanism of valve event characteristic of leading angle of timing and the simplification of structure thereof greater than exhaust valve.

Invent according to the third aspect, except that the invention effect of having stated, also produce following effect, promptly, because the distance of the moving center line of the pivot of the moving portion of the air-breathing pivot of air-breathing double-action mechanism and the rotary centerline of camshaft is than the moving center line of pivot of the moving portion of exhaust pivot of exhaust double-action mechanism and the distance weak point of the rotary centerline of camshaft, therefore, the hysteresis angle that can realize being used to obtaining the IVO Inlet Valve Open timing is closed the simplifying the structure of valve characteristic changing mechanism of valve event characteristic of the leading angle of timing greater than exhaust valve.

Description of drawings

Fig. 1 has installed the right part of flg of the two-wheeled vehicle of internal-combustion engine of the present invention;

Fig. 2 be in the internal-combustion engine of Fig. 1, the II-II arrow of Fig. 6 is to the sectional drawing of looking, the sectional drawing of the face of the central axis of the central axis of local expression by the valve stem of intake valve and exhaust valve, Control Shaft;

Fig. 3 is the schematic representation of throttling air door body of the internal-combustion engine of Fig. 1;

Fig. 4 is the figure of state of control procedure of the internal-combustion engine of explanatory drawing 1, (A) during the warming-up of expression throttling valve opening curve with figure, (B) use figure behind the warming-up of expression throttle opening curve, (C) being the cover time of expression during warming-up and the figure of the state of a control of non-cover time, (D) is the figure of the state of a control of cover time behind the expression warming-up and non-cover time;

Fig. 5 be in the internal-combustion engine of Fig. 1, the sectional drawing looked of the Va-Va direction of arrow of Figure 10, the part is that signal Vb-Vb arrow is to the sectional drawing of looking;

Fig. 6 is in the internal-combustion engine of Fig. 1, is plucking the state of valve mechanism cover, and the sectional drawing of looking with the VI-VI direction of arrow of Fig. 2 of valve device is with the figure of the component parts of the local expression of suitable section valve device;

Fig. 7 is the figure that sees the camshaft carriage that is installed on the cylinder head in the internal-combustion engine of Fig. 1, along cylinder-bore axis from cylinder-head-side;

Fig. 8 is in the valve device of the internal-combustion engine of Fig. 1, (A) being the figure that sees the exhaust gas drive cam of valve characteristic changing mechanism from the camshaft direction, (B) is with the exhaust linkage mechanism of the moving state representation valve characteristic changing mechanism of suitable pivot and the figure of exhaust cam.

Fig. 9 (A) be the IX A arrow of Fig. 8 to the sectional drawing of looking, (B) be the IX B arrow of Fig. 8 to view, (C) be the sectional drawing that the IX C arrow line of vision of Fig. 8 is looked, the IX D arrow that (D) is Fig. 8 is to view.

Figure 10 is in the internal-combustion engine of Fig. 1, sees the figure of valve mechanism cover along cylinder-bore axis from the place ahead, and partly cut-away represents the figure of the driving mechanism of valve characteristic changing mechanism;

Figure 11 is the figure of the valve event characteristic of the intake valve of valve device of internal-combustion engine of explanatory drawing 1 and exhaust valve;

Figure 12 be in the internal-combustion engine of Fig. 1, (A) be the explanatory drawing of the critical piece of the valve characteristic changing mechanism when intake valve obtains maximum valve event characteristic, (B) is the explanatory drawing of the critical piece of the valve characteristic changing mechanism when exhaust valve obtains maximum valve event characteristic;

Figure 13 (A) is the figure of the corresponding Figure 12 (A) when intake valve obtains minimum valve event characteristic, (B) is the figure of the corresponding Figure 12 (B) when exhaust valve obtains minimum valve event characteristic;

Figure 14 (A) is the figure of the corresponding Figure 12 (A) when intake valve obtains reducing pressure acting characteristic, (B) is the figure of the corresponding Figure 12 (B) when exhaust valve obtains reducing pressure acting characteristic;

Symbol description

1. vehicle frame; 2. the preceding person in charge; 3. front fork; 4. handle; 5. rocking arm; 6. rear shock absorber;

7. front-wheel; 8. trailing wheel; 9. car body cover; 10. crankcase; 11. cylinder; 12. cylinder head;

13. valve mechanism cover; 14. piston; 15. bent axle; 16. firing chamber; 17. suction port;

18. exhaust port; 19. spark plug; 20i, 20e. valve guiding element; 21. valve spring;

22. intake valve; 23. exhaust valve; 24. valve seat; 25. valve retainer; 26. air filter;

27. throttling air door body; 28. outlet pipe; 29. cam pedestal; 30. throttling valve;

32. throttle opening detector; 33. motor; 34,35. gears; 40. valve device;

41,42. master rockers; 43. rocker; 44. bearing; 50. camshaft;

51,52. driving cams; 53. air inlet cam; 54. exhaust cam; 55. press pressing spring;

56. bearing; 57. cam sprocket wheel; 59. Transmission Room; 60e, 60i. anchor clamps;

61e, 61i, 62e, 62i. plate; 63e, 63i. sleeve pipe; 64. rivet;

66i, 66e. secondary-rocker; 67e, 67i. connecting rod; 68. control spring; 69. bearing;

70. Control Shaft; 71i, 71e. control link; 72,73. connecting pins;

76,77,78,79. spring holding parts;

76a, 77a, 78a, 79a. spring guide;

80. motor; 80b. output shaft; 81. reduction gear; 82. output gear; 83. lid;

84. supporting axle; 88. keep tube; 89. bearing; 90. the axis of guide; 91. through hole;

92.ECU; 94. shake position detector; 95. output required amount detector;

96. engine temperature detector; E. internal-combustion engine; V. two-wheeled; U. power unit;

L1. cylinder-bore axis; L2. rotary centerline; L3i, L3e. shake center line;

L4i, L4e, L5i, the moving center line of L5e pivot; L6. central axis;

A1. cylinder-bore axis direction; A2. camshaft direction; T. throttling control mechanism;

D. operation amount; Da. given load; Db. maximum load; Fa, Fb. load area;

E. side-play amount; M. valve characteristic changing mechanism; M1i, M1e. linkage mechanism;

M2. driving mechanism; M3. control mechanism; M4. conveyer; HO. datum plane;

H1, H2. vertical plane; R1. sense of rotation; R2. reverse directions;

The maximum valve event characteristic of Kimax, Kemax.; The minimum valve event characteristic of Kimin, Kemin.;

β. aperture; θ iomax, θ icmin, θ eomax, the most large and small lead angle of θ ecmin. position;

θ iomax, θ icmin, θ eomax, θ ecmin. maximum, mini lag angle position;

Pa. cover time; Pb. the non-cover time; Pae. effective cover time;

Pbe. effective non-cover time; N. internal EGR rate; Nn. minimum internal EGR rate;

Nx. maximum internal EGR leads.

Embodiment

Below, with reference to Fig. 1～Figure 14 embodiments of the present invention are described.

Referring to Fig. 1, used internal-combustion engine E of the present invention and be installed on a kind of vehicle two-wheeled vehicle V.Two-wheeled vehicle V has: the vehicle frame 1 that comprises side arm 1a and after-frame 1b; Be fixed on the handle 4 of the upper end portion of front fork 3, this front fork 3 can be bearing on the preceding person in charge 2 who is connected in side arm 1a rotationally; Can be bearing in the front-wheel 7 of front fork 3 underparts rotationally; Be supported in the power unit U of vehicle frame 1; Can be bearing in the trailing wheel 8 of the rearward end of Rocker arm 5 rotationally, this Rocker arm 5 can joltily be bearing on the vehicle frame 1; The rear shock absorber 6 that connects the rear portion of after-frame 1b and Rocker arm 5; Surround the car body cover 9 of vehicle frame 1.

Power unit U comprises: the horizontal internal-combustion engine E with the bent axle 15 that extends at the left and right directions of two-wheeled vehicle V; Have speed changer, transmit the transmission device of the power of internal-combustion engine E to trailing wheel 8.Internal-combustion engine E comprises: form and accommodate the crankshaft room of bent axle 15 and the crankcase 10 of double as speed changer case; The cylinder 11 that is connected on the crankcase 10, forwards extends; Be connected the cylinder head 12 on the front end of cylinder 11; Be connected the valve mechanism cover 13 on the front end of cylinder head 12.The cylinder body axis L1 of cylinder 11 forward, relatively substantially horizontal prolongations (with reference to Fig. 1) that be inclined upwardly a little, the perhaps parallel in the horizontal direction prolongation of cardinal principle.And, driving bent axle 15 by piston 14 (with reference to Fig. 2) and rotate, the rotation of bent axle 15 drives trailing wheel 8 by transmitting to trailing wheel 8 behind the described speed changer.

With reference to Fig. 2, internal-combustion engine E is a SOHC type air cooling single-cylinder four-stroke internal-combustion engine in the lump.In cylinder 11, form the 11a of cylinder chamber, can the chimeric piston 14 in to-and-fro motion ground in it.In cylinder head 12 on cylinder-bore axis direction A1 relatively the face of the 11a of cylinder chamber form firing chamber 16, also in firing chamber 16 respectively opening form suction port 17 with intakeport 17a and exhaust port 18 with relief opening 18a.Spark plug 19 faces firing chamber 16 and is inserted in the mounting hole 12c that forms on the cylinder head 12, is installed on the cylinder head 12.At this, the described 11a of cylinder chamber between firing chamber 16 and piston 14 and the cylinder head 12 constitutes the combustion space jointly.

In addition, engine valve also is set in cylinder head 12, i.e. an intake valve 22 and an exhaust valve 23, it is moved back and forth by

valve guiding element

20i, 20e supporting, pressured by valve spring 21 at ordinary times to closing direction, open and close by the valve device 40 that is installed in the internal-combustion engine E, open and close the intakeport 17a and the relief opening 18a that form by valve seat 24 respectively.Valve device 40 except that motor 80 (with reference to Fig. 5), is configured in the valve Transmission Room 25 that is made of cylinder head 12 and housing 13.

Suction means is installed on the 12a in a side of the cylinder head 12 of the inlet 17b that offers suction port 17 promptly, it has air filter 26 (with reference to Fig. 1) and throttling air door body 27 (with reference to Fig. 1), is used in the air introducing suction port 17 of outside absorption.Venting gas appliance is installed on the 12b in the another side of the cylinder head 12 of the outlet 18b that offers exhaust port 18 below promptly, it has 16 exhausts by exhaust port 18 outflows are directed to the outlet pipe 28 (with reference to Fig. 1) of internal-combustion engine E outside from the firing chamber.In addition, in above-mentioned suction means, also has the fuel supplying device of feed fluid fuel in sucking air, i.e. Fuelinjection nozzle.

And, by air filter 26 and throttling air door body 27 inhaled airs, through the intake valve of opening in the suction stroke that descends at piston 14 22, suck in the firing chamber 16 from suction port 17, in the compression stroke that piston 14 rises, be compressed with state with fuel mix.Mixed gas latter stage of compression stroke by spark plug 19 ignition, in the expansion stroke that piston 14 descends, the pressure-actuated piston 14 of burned gas drives bent axles 15 and rotates.The exhaust valve 23 of burnt gas through opening in the exhaust stroke that rises at piston 14, as exhaust, 16 in exhaust port 18 discharges from the firing chamber.

With reference to Fig. 3, be communicated with air filter 26, be provided with in the throttling air door body 27 of downstream 27b side by sucking pipe connection suction port 17 in upstream extremity 27a side: the spring that is reset is to the pressured throttling valve 30 of a direction of holding one's breath, and envoy's gas door 30 opens and closes, controls the throttling control mechanism T of its aperture; Detect the throttle opening detection device 32 of the aperture of throttling valve 30.Throttling control mechanism T comprises: be the motor 33 of the final controlling element of ECU (Electrical Control Unit) (hereinafter referred to as " ECU ") 92 (with reference to Fig. 5) control by control gear; The driving mechanism that the driving force of motor 33 transmits to throttling valve 30, the train of reduction gears that it is made up of series of

gears

34,35.

With reference to Fig. 5, import the various testing signals of the operating condition detection device of the operating condition that detects internal-combustion engine E among the ECU 92 in the lump.The operating condition detection device comprises: output required amount detection device 95, its detect runner's operation the output function parts, be the operation amount D of throttling valve operation handle; Engine temperature detection device 96, it is as the detection device (for example lubricating oil temperature detection device) of the warm-up mode that detects internal-combustion engine E; Throttle valve opening detection device 32.Here, operation amount D is the output quantity of the internal-combustion engine that requires of runner, and above-mentioned throttling valve operation handle is an output setting device of setting this required amount.

Storing with operation amount D in the storage of ECU 92 is parameter, sets the throttle valve opening figure of the aperture β of throttling valve 30.Shown in Fig. 4 (A), (B), this throttle valve opening figure is made of with figure after with figure and the warming-up that finishes to use the back at internal-combustion engine E warming-up the warming-up that uses when the internal-combustion engine E warming-up.And, control motor 33 is according to the aperture of the reality of the throttling valve 30 of operation amount D that exports 95 detections of required amount detection device and 32 detections of throttle opening detection device, open and close throttling valve 30 by ECU 92 controls, the aperture of envoy's gas door 30 reaches the aperture β that above-mentioned throttle opening figure sets.

ECU 92, detect engine temperature when not reaching the warming-up of state of set point of temperature at engine temperature detection device 96, select warming-up with figure; After engine temperature detection device 96 detects the warming-up of engine temperature more than or equal to the state of afore mentioned rules temperature, select to use figure behind the warming-up.According to warming-up figure, the aperture characteristic that the aperture of setting throttling valve 30 is directly proportional with operation amount D will be at whole load areas of internal-combustion engine E, and the aperture of envoy's gas door 30 increases along with the increase of operation amount D.Therefore, motor 33 is at the load Zone Full, and the operation amount D that detect along with output required amount detection device 95 (also being the load detection device that detects engine load) be the increase of engine load and increase the aperture that aperture is controlled throttling valve 30 in this wise.

In addition, according to using figure, the aperture characteristic that is set as follows: behind the warming-up at the first load area Fa of the given load Da from zero load to low-load region, along with the increase of operation amount D (engine load), throttling valve 30 will increase from the idling aperture, and Da reaches standard-sized sheet at load; At the second load area Fb that surpasses given load Da, the aperture of throttling valve 30 and operation amount D are irrelevant to be full-gear.Therefore, motor 33 at the first load area Fa, along with the increase of operation amount D reaches the aperture that standard-sized sheet is controlled throttling valve 30 in this wise from the idling aperture at given load Da, at the second load area Fb, keep standard-sized sheet ground control throttling valve 30.At this, whole load areas of internal-combustion engine E between zero load and maximum load Db, should roughly third-classly be divided into low-load region F1, intermediate load region F2 and high-load region F3.

With reference to Fig. 2, Fig. 5～Fig. 7, Figure 12, valve device 40 has: air-breathing master rocker 41, and it touches the valve stem 22a of intake valve 22 as the air inlet cam follower, and intake valve 22 is opened and closed; Exhaust master rocker 42, it touches the valve stem 23a of exhaust valve 23 as the exhaust cam follower, and valve 23 is opened and closed; The M of valve characteristic changing mechanism, its control comprises the opening and close timing of intake valve 22 and exhaust valve 23 and the valve event characteristic of maximum lift amount.

Air-breathing master rocker 41 and exhaust master rocker 42, fulcrum 41a, 42a with central part can joltily be bearing on a pair of rocker 43 that is fixed on the cam pedestal 29 respectively,

adjustment screw

41b, 42b with the service portion that constitutes an end touches

valve stem

22a, 23a respectively, respectively with roller 41c, the 42c contact air inlet cam 53 and the exhaust cam 54 of the contacting part that constitutes the other end.

The M of valve characteristic changing mechanism comprises: be housed in the internal mechanism in the valve Transmission Room 25; The electric actuator that drives above-mentioned internal mechanism is a motor 80, and it is configured in outside the valve Transmission Room 25 as external agency.Above-mentioned internal mechanism comprises: a camshaft 50, and it can be bearing on the cylinder head 12 rotationally, and is driven rotation with bent axle 15 interlocks; Air-breathing driving cam 51 and exhaust gas drive cam 52, it is the driving cam that is set on the camshaft 50, rotates integratedly with camshaft 50; Linkage mechanism M1i, M1e, it is that axle props up on camshaft 50, can be the double-action mechanism that the center is shaken with camshaft 50; Air inlet cam 53 and exhaust cam 54, it is to connect linkage mechanism M1i, M1e, the axle that air-breathing master rocker 41 and exhaust master rocker 42 are moved props up the valve driving cam on camshaft 50; Driving mechanism M2 (with reference to Fig. 5), it makes linkage mechanism M1i, m1e with motor 80 as driving source is that the center is shaken with camshaft 50; Control mechanism M3, it is installed between driving mechanism M2 and linkage mechanism M1i, the M1e, shakes round camshaft 50 according to the driving force control link M1i of mechanism, the M1e of motor 80; Press pressing spring 55, it is as pushing actuator, the torque that makes camshaft 50 on linkage mechanism M1i, M1e, thereby linkage mechanism M1i, M1e by being pressed on the control mechanism M3.

With reference to Fig. 2, Fig. 5, Fig. 6, camshaft 50, by pair of bearings 56 in its two end part configuration, can be bearing in cylinder head 12 rotationally and be connected on the cam pedestal 29 on the cylinder head 12, by the power (with reference to Fig. 1) and bent axle 15 interlocks of the bent axle 15 that transmits with driving mechanism via the valve transmission, be driven rotation with half rotating speed of bent axle 15.Above-mentioned valve transmission has with driving mechanism: the cam sprocket wheel 57 that is integral connection near the front end as the left part of an end of camshaft 50; Be connected the driving sprocket wheel on the bent axle 15 with being integral; Cover hangs over the timing chain 58 on cam chain wheel 57 and the above-mentioned driving sprocket wheel.Above-mentioned valve transmission is the Transmission Room in left side with the side that driving mechanism is housed in the first vertical plane H1 that is positioned at cylinder 11 and cylinder head 12 that is formed by cylinder 11 and cylinder head 12.And, the Transmission Room 59 that is formed by cylinder head 12 in the above-mentioned Transmission Room is to be the footpath direction (hereinafter referred to as " footpath direction ") at center with cylinder-bore axis L1, and adjoins valve Transmission Room 25 at the direction A2 (to call " camshaft direction A2 " in the following text) of the rotary centerline L2 of camshaft 50.At this, the first vertical plane H1 comprises cylinder-bore axis L1, and the while is perpendicular to the plane of datum plane H0 described later.

In addition, in valve characteristic changeable mechanism M, because the parts relevant with intake valve 22 and with exhaust valve 23 relevant parts comprise in correspondence with each other parts, in addition because air-breathing driving cam 51, exhaust gas drive cam 52, linkage mechanism M1i, M1e, air inlet cam 53 has identical basic structure with exhaust cam 54, so in the following description, with the parts that relate to exhaust valve 23 is that the center describes, and the parts that relate to intake valve 22 wait with relevant explanation to be charged in the parantheses on demand.

With reference to Fig. 2, Fig. 5, Fig. 8, Fig. 9, Figure 12, be pressed into the exhaust gas drive cam 52 (air-breathing driving cam 51) that is fixed on the camshaft 50 and have the camming surface that spreads all over the full week formation of outer circumferential face.This camming surface constitutes by the 52a of basic circle portion (51a) that does not shake exhaust cam 54 (air inlet cam 53) by linkage mechanism M1e (M1i) with by the nose of cam 52b (51b) that linkage mechanism M1e (M1i) shakes exhaust cam 54 (air inlet cam 53).Basic circle portion 52a (51a) has the section shape that forms by from the certain circular arc of the radius of rotary centerline L2, and nose of cam 52b (51b) has by the radius from rotary centerline L2 increases the section shape that reduce the back at the sense of rotation R1 of camshaft 50.And, basic circle portion 52a (51a) will make basic circle portion 54a (53a) of exhaust master rocker 42 (air-breathing master rocker 41) contact exhaust cam 54 (air inlet cam 53) set the position of shaking of exhaust cam 54 (air inlet cam 53) like that, and nose of cam 52b (51b) will make the 54a of basic circle portion (53a) of exhaust master rocker 42 (air-breathing master rocker 41) contact exhaust cam 54 (air inlet cam 53) and the position of shaking that nose of cam 54b (53b) sets exhaust cam 54 (air inlet cam 53) like that.

Linkage mechanism M1i, M1e are made of with the exhaust linkage mechanism M1e that is connected exhaust cam 54 the air-breathing linkage mechanism M1i that connects air inlet cam 53.With reference to Fig. 5, Fig. 6, exhaust linkage mechanism M1e (air-breathing linkage mechanism M1i) has in the lump: axle props up on camshaft 50, can be the carriage 60e (60i) that the center is shaken with camshaft 50; Axle is bearing on the carriage 60e (60i), is driven the exhaust secondary-rocker 66e (air-breathing secondary-rocker 66i) that shakes by exhaust gas drive cam 52 (air-breathing driving cam 51); Prop up on exhaust auxiliary 66e (air-breathing secondary-rocker 66i) with an end axis, simultaneously prop up connecting rod 67e (67i) on exhaust cam 54 (air inlet cam 53) with the other end axle; Exhaust secondary-rocker 66e (air-breathing secondary-rocker 66i) by the control spring 68 that is pressed on the exhaust gas drive cam 52 (air-breathing driving cam 51).

The carriage 60e (60i) that is bearing on the camshaft 50 by the bearing 69 that is enclosed within on the camshaft 50 has: at camshaft direction A ₂On leave a pair of first, second plate 61e (61i), the 62e (62i) that is provided with at interval; At camshaft direction A ₂Leave predetermined distance and connect the first plate 61e (61i) and the second plate 62e (62i), simultaneously the connected element of axle supporting exhaust secondary-rocker 66e (air-breathing secondary-rocker 66i).This connected element comprises: determining to isolate the described predetermined distance of two plate 61e (61i), 62e (62i), is again simultaneously the sleeve pipe 63e (63i) of the supporting axle of an axle exhaust secondary-rocker 66e (air-breathing secondary-rocker 66i); Pass the rivet 64 that sleeve pipe 63e (63i) links into an integrated entity two plate 61e (61i), 62e (62i).As Fig. 6, shown in Figure 8, go up formation mounting hole 61e3 (61i3), 62e3 (62i3) at each plate 61e (61i), 62e (62i), it is used for installing the bearing 69 that can joltily be bearing in each plate 61e (61i), 62e (62i) on the camshaft 50.

In the lump with reference to Fig. 5, at the exhaust control link 71e (air-breathing control link 71i) of the last control mechanism M3 that ins succession of the first plate 61e (61i), exhaust control link 71e (air-breathing control link 71i) can be connected to relative movement at both joint 71e2 (71i2), 61e1 (61i1) with the first plate 61e (61i).Specifically, can insert in the hole of joint 71e2 (71i2) of the exhaust control link 71e (air-breathing control link 71i) as control mechanism side joint being pressed into to be fixed on as the connecting pin 61e1a (61i1a) in the hole of the joint 61e1 (61i1) of the first plate 61e (61i) of bracket side joint with relatively rotating.

In addition, go up formation relief cam 62e1 (62i1) at the second plate 62e (62i), it is used for when cranking internal combustion engine E, by opening intake valve 22 and exhaust valve 23 a little, reduces compression pressure in compression stroke, thus starting (with reference to Fig. 8, Figure 12) easily.In addition, on the second plate 62e detected portion 62e2 is set also, it is used for being shaken the detection unit 94a detection of position detecting device 94 (with reference to Figure 14).Detected portion 62e2 is by shaking direction at the second plate 62e, and the tooth portion that is connected with a joggle with the tooth portion that constitutes detection unit 94a constitutes.In addition, do not have use, the part 62i2 suitable with detected portion 62e2 also is set on the second plate 61i in present embodiment.

On sleeve pipe 63e (63i), the movable side spring holding part 78 that the first spring holding part 76 of the integrally formed end that the control spring 68 that maintenance forms by compression helical spring is set and keeping is formed by compression helical spring by an end of pressing spring 55.Two

spring holding parts

76,78 are at camshaft direction A ₂Fulcrum 66ea (66ia) last and exhaust secondary-rocker 66e (air-breathing secondary-rocker 66i) adjoins configuration, and arranged spaced (with reference to Fig. 6) is spaced on the Zhou Fangxiang of sleeve pipe 63e (63i) simultaneously.

In addition, on sleeve pipe 63e (63i), on the position of shaking centre line L 3e (L3i) of leaving exhaust secondary-rocker 66e (air-breathing secondary-rocker 66i), form the protuberance 63e1 (63i1) that is entrenched in the hole 62e4 (62i4) that is formed on the second plate 62e (62i).Protuberance 63e1 (63i1) and hole 62e4 (62i4) constitute joint, and it is used to stop between the second plate 62e (62i) and the sleeve pipe 63e (63i) round shaking relatively rotating of centre line L 3e (L3i).Stop by a pair of

spring holding part

76,78 is set by this joint, and by control spring 68 with press sleeve pipe 63e (63i) the rotating relative to first, second plate 61e (61i), 62e (62i) of unidirectional torque of the elastic force generation of pressing spring 55.Thereby, can positively carry out by paying round the torque of camshaft 50 with by the push effect of control spring 68 to linkage mechanism M1i, M1e to exhaust gas drive cam 52 (air-breathing driving cam 51) by pressing spring 55.

With reference to Fig. 2, Fig. 5, Fig. 6, Fig. 8, Fig. 9, Figure 12, at camshaft direction A2, be configured in exhaust secondary-rocker 66e (air-breathing secondary-rocker 66i) between first, second plate 61e (61i), the 62e (62i) with exhaust cam 54 (air inlet cam 53) and exhaust gas drive cam 52 (air-breathing driving cam 51), roller 66eb (66ib) as the contacting part that contacts with exhaust gas drive cam 52 (air-breathing driving cam 51) contacts with exhaust gas drive cam 52 (air-breathing driving cam 51); At one end the fulcrum 66ea of portion (66ia) can joltily be bearing on the sleeve pipe 63e (63i); At the joint 66ec of the other end (66ic), axle props up on the connecting pin 72 on the end of being fixed in connecting rod 67e (67i).Therefore, exhaust secondary-rocker 66e (air-breathing secondary-rocker 66i) is rotated with camshaft 50 and is shaken for shaking the center with sleeve pipe 63e (63i) by exhaust gas drive cam 52 (air-breathing driving cam 51).

The quilt axle props up the exhaust cam 54 (air inlet cam 53) on the connecting pin on the other end of being fixed in connecting rod 67e (67i) 73, being supported on the camshaft 50 by bearing 44 to be that the oscillating cam that the center is shaken constitutes with camshaft 50, forms camming surface on the part of the outer circumferential face of this cam.This camming surface is by keeping exhaust valve 23 (intake valve 22) for the 54a of basic circle portion (53a) of a state of holding one's breath with push nose of cam 54b (53b) formation of opening exhaust valve 23 (intake valve 22) downwards.The section shape of the 54a of basic circle portion (53a) is from rotary centerline L ₂The certain circular arc of radius, the section of nose of cam 54b (53b) forms from rotary centerline L ₂The shape that increases at the reverse directions R2 of camshaft 50 (sense of rotation R1) of radius.Therefore, the nose of cam 54b (53b) of exhaust cam 54 (air inlet cam 53) has the shape that little by little increases the lifting capacity of exhaust valve 23 (intake valve 22) at reverse turn direction R2 (sense of rotation R1).

Exhaust cam 54 (air inlet cam 53) by the driving force of the driving mechanism M2 that transmits by control mechanism M3, is that the center is shaken with identical shaking quantity with camshaft 50 with exhaust linkage mechanism M1e (air-breathing linkage mechanism M1i) on the one hand together; The exhaust secondary-rocker 66e (air-breathing secondary-rocker 66i) that is shaken by exhaust gas drive cam 52 (air-breathing driving cam 51) is that the center is shaken with camshaft 50 on the other hand.And the exhaust cam 54 (air inlet cam 53) that relative camshaft 50 shakes shakes exhaust master rocker 42 (air-breathing master rocker 41), thus switch pair valve 23 (intake valve 22).Therefore, exhaust cam 54 (air inlet cam 53), driving force by the driving mechanism M2 that transmits by carriage 60e (60i), exhaust secondary-rocker 66e (air-breathing secondary-rocker 66i) and connecting rod 67e (67i) is successively shaken, and, shake by the driving force of the exhaust gas drive cam 52 (air-breathing driving cam 51) that transmits by exhaust secondary-rocker 66e (air-breathing secondary-rocker 66i) and connecting rod 67e (67i) successively.

Control spring 68 is configured between sleeve pipe 63e (63i) and the exhaust cam 54, corresponding exhaust secondary-rocker 66e (air-breathing secondary-rocker 66i) shakes, can be flexible at the Zhou Fangxiang of camshaft 50, produce the elastic force of on exhaust gas drive cam 52 (air-breathing driving cam 51), pushing the roller 66eb (66ib) of exhaust secondary-rocker 66e (air-breathing secondary-rocker 66i).One end of control spring 68 is maintained in the first spring holding part 76, and the other end is maintained to be arranged on exhaust cam 54 (air inlet cam 53) and forms in the second spring holding part 77 on the tabular bump of the pavilion of one.

In exhaust linkage mechanism M1e (air-breathing linkage mechanism M1i), often act on its end by pressing spring 55 of shaking the elastic force that produces torque on the direction in the same direction as and be maintained in the movable side spring holding part 78 of carriage 60e (60i), the other end is maintained in the fixed side spring holding part 79 that is arranged on the cam pedestal 29 (it is the fixed component that is fixed in the cylinder head 12).

The elastic force that exhaust linkage mechanism M1e (air-breathing linkage mechanism M1i) is pushed to cylinder 11 sides by pressing spring 55, act directly on the carriage 60e (60i), this carriage 60e (60i) is pushed to the direction of cylinder 11, act on torque on the carriage 60e (60i) towards an above-mentioned side's direction by this elastic force.And, set an above-mentioned side's direction and to act on the torque direction that acts on the exhaust cam 54 (air inlet cam 53) that the reaction force on the exhaust cam 54 (air inlet cam 53) produces by exhaust valve 23 (intake valve 22) when exhaust cam 54 (air inlet cam 53) is opened exhaust valve 23 (intake valve 22) identical.Therefore, by the elastic force of pressing spring 55 joint 61e1 (61i1) joint 71e2 (71i2) to often shake direction that direction pushes with based on acting on the above-mentioned reaction force of torque on the carriage 60e (60i) at joint 71e2 (71i2) by connecting rod 67e (67i) and exhaust secondary-rocker 66e (air-breathing secondary-rocker 66i) from exhaust cam 54 (air inlet cam 53), identical joint 61e1 (61i1) to shaking the direction that direction pushes.

And, by pressing pressing spring 55, propping up each the joint 71e2 (71i2) that produces micro-gap by axle, 61e1 (61i1), one side's joint 61e1 (61i1) is pushed to shaking direction often at the opposing party's joint 71e2 (71i2), thereby, when shaking the first plate 61e (61i) by exhaust control link 71e (air-breathing control link 71i), the influence in the gap (play) between joint 71e2 (71i2) and the joint 61e1 (61i1) is disengaged, and the movement high-precision ground of exhaust control link 71e (air-breathing control link 71i) transmits to carriage 60e (60i).

With reference to Fig. 2, Fig. 5, Figure 12, control mechanism M3 has: as the columnar Control Shaft 70 of the controlling component that is driven by driving mechanism M2; The motion that transmits Control Shaft 70 to linkage mechanism M1i, M1e is control link 71i, the 71e of the M1i of center walking bar rod mechanism, M1e with camshaft 50.

Control Shaft 70 can move in the direction that is parallel to cylinder-bore axis L1, thereby, can move in the parallel direction of datum plane H0 that is parallel to cylinder-bore axis L1 relative to the rotary centerline L2 that comprises camshaft 50 simultaneously.

Control link 71i, 71e are made of air-breathing control link 71i and exhaust control link 71e.Air-breathing control link 71i at the first air-breathing joint, be 70 on the controlled axle of joint 71i1, at the second air-breathing joint, be that joint 71i2 is dynamically connected by the joint 61i1 pivot of the first plate 61i of air-breathing linkage mechanism M1i.Exhaust control link 71e at the first exhaust joint, be that the controlled axle of joint 7,1e1 70 pivots are dynamically connected, at the second exhaust joint, be that the joint 61e1 pivot that joint 71e2 is deflated the first plate 61e of linkage mechanism M1e is dynamically connected.The joint 71i1 of air-breathing control link 71i and the joint 70a of Control Shaft 70 have respectively can insert a hole that is pressed into the connecting pin 71e3 in the joint 71e1 hole that is fixed on exhaust control link 71e with relatively rotating, is connected pin 71e3 axle and props up.Two forked joint 71i2,71e2 have respectively can insert the connecting pin 61i1a of joint 71i2,71e2, the hole of 61e1a with relatively rotating, is connected pin 61i1a, 61e1a pivot suspension.And, press the elastic force of pressing spring, exist by pivot be dynamically connected each joint 71e1 (71i1), the 70a in the small gap that produces, often joint 71e1 (71i1) by being pressed on the joint 70a, thereby, the influence in the gap (play) between joint 71e1 (71i1) and the joint 70a is eliminated, and the motion of Control Shaft 70 is sent to exhaust control link 71e (air-breathing control link 71i) accurately.

And, the pivot of joint 71i1 moves the moving centre line L 4e (with reference to Fig. 2, Figure 12) of pivot of centre line L 4i (with reference to Fig. 2, Figure 12) and joint 71e1, constitute the moving center line of common pivot at the joint 70a of Control Shaft 70, and, to a side, i.e. the state (with reference to Fig. 2, Fig. 7) of exhaust side skew predetermined distance side-play amount e is parallel to the configuration of rotary centerline L2 ground with relative datum plane H0.The pivot of joint 71i2 moves centre line L 5i (with reference to Fig. 2, Figure 12) and is configured in above-mentioned exhaust side with being parallel to rotary centerline L2.The pivot of joint 71e2 moves the opposite side that centre line L 5e (with reference to Fig. 2, Figure 12) is configured in relative datum plane H0 with being parallel to rotary centerline L2, i.e. suction side.Therefore, as shown in Figure 7, the axis L 6 of Control Shaft 70 is parallel to cylinder-bore axis L1, and relative datum plane H0 is only to exhaust side skew side-play amount e simultaneously.Here, suction side is relative datum plane H0, is configured into a side of valve 22, and exhaust side is a side of relative datum plane H0 configuration exhaust valve 23.

In addition, set distance between two pivots moving centre line L 4i, the L5i, be the length of connecting rod of air-breathing control link 71i than the distance between two pivots moving centre line L 4e, the L5e, be that the length of exhaust control link 71e is long.Two pivots moving centre line L 5i, L5e be configured in camshaft 50 around, with rotary centerline L2 is on the same cylndrical surface of axle, L2 is equidistant with center of rotation, and, be positioned at the relative second vertical plane H2 (it comprises that rotary centerline L2 is simultaneously perpendicular to datum plane H0) configuration Control Shaft 70 and the moving centre line L 4i of pivot, L4e one side.In addition, the moving centre line L 5i of pivot is in the position than the moving more close second vertical plane H2 of centre line L 5e of pivot.

Therefore, owing to common pivot moves center line, is pivot moving centre line L 4i, the L4e relative datum plane H0 side-play amount e to exhaust side skew regulation, also because the length of connecting rod of the air-breathing control link 71i of setting is longer than the length of connecting rod of exhaust control link 71e, like this, for the amount of movement of the Control Shaft 70 that drives by driving mechanism M2, be that the shaking quantity shaking quantity of air-breathing linkage mechanism M1i and air inlet cam 53 (thereby also make) of the moving centre line L 5i of pivot at center is bigger than the shaking quantity of exhaust connecting rod M1e and exhaust cam 54 with camshaft 50.

With reference to Fig. 6, Figure 10, the driving mechanism M2 of drive controlling axle 70 comprises: but be installed in reverse motors 80 on the valve mechanism cover 13; The rotation of motor 80 is sent to the conveyer M4 of Control Shaft 70.And the relative second vertical plane H2 with driving mechanism M2 of control mechanism M3 is configured in the opposition side of cylinder 11 and firing chamber 16.

Motor 80 has: accommodate generating heat department such as coil portion and have the cylinder-bore axis of being parallel to L ₁The cylinder body 80a of central axis; Be parallel to cylinder-bore axis L ₁The output shaft 80b that extends.Motor 80 relative cylinder head 12 and valve mechanism cover 13 are in the foreign side that is arranged radially in of valve Transmission Room 25.And the relative first vertical plane H1 is right side configuration body 80a and spark plug 19 at left side configuration Transmission Room 59 at opposite side.In body 80a, on valve mechanism cover 13 to the assembly department 13a that radially protrude to form hat, with the 80a1 of the portion that is mounted that above-mentioned assembly department 13a engages on form through hole 80a2, output shaft 80b runs through the outside that this through hole 80a2 protrudes into body 80a and extends in the valve Transmission Room 25.Body 80a, along cylinder-bore axis direction A1, in addition, from the place ahead of valve mechanism cover 13, it all is configured on the position that is covered by assembly department (with reference to Figure 10) from valve mechanism cover 13 sides.

With reference to Fig. 2, Fig. 5, Figure 10, in valve Transmission Room 25, the conveyer M4 that is configured between cam pedestal 29 and the valve mechanism cover 13 at cylinder-bore axis direction A1 comprises: reduction gear 81, its with mesh running through valve mechanism cover 13 and extend to the actuation gear 80b1 that forms on output shaft 80b valve Transmission Room 25 in; Output gear 82, itself and reduction gear 81 mesh, and can be supported in rotationally on the cylinder head 12 by cam pedestal 29 simultaneously.Reduction gear 81, it can be bearing on the supporting axle 84 of valve mechanism cover 13 and lid 83 supportings that cover the opening 13c that forms on the valve mechanism cover 13 rotationally, have: with the gearwheel 81a of actuation gear 80b1 engagement, with the small gear 81b of output gear 82 engagements.Output gear 82 has columnar hub portion 82a, and it can be held tube 88 supportings rotationally by bearing 89, this keep tube 88 by bolted joints on cam pedestal 29.

Output gear 82 drives by feed screw mechanism with Control Shaft 70 and is connected, and this feed screw mechanism is transformed into the rotational motion of output gear 82 straight reciprocating motion that is parallel to cylinder-bore axis L1 of Control Shaft 70.Above-mentioned feed screw mechanism has the 82b of female thread portion that trapezoidal thread that the inner peripheral surface at hub portion 82a forms constitutes and form the outer screw section 70b that is made of the trapezoidal thread that is threaded with outer screw section 70b on the outer circumferential face of Control Shaft 70.Control Shaft 70 can be entrenched on the periphery of the axis of guide 90 that is fixed on the hub portion 82a slidably, under by these axis of guide 90 guiding movement direction states, by the through hole 91 (also with reference to Fig. 7) that on cam pedestal 29, forms, along cylinder-bore axis direction A1 camshaft 50 turnover relatively.

With reference to Fig. 5, motor 80 is by ECU (Electrical Control Unit) (to call ECU in the following text) 92 controls.For this reason, for ECU92 input from output required amount detection device 95, internal-combustion engine temperature detection device 96 and constitute the testing signals such as internal-combustion engine rotational speed detection device that play motion detection device and detection internal-combustion engine rotational speed of starting time of the detection internal-combustion engine E of above-mentioned running state detecting device, also import shaking the angle, promptly shake the testing signal that shakes position detecting device 94 (for example, constituting) of position from the relative camshaft 50 of carriage 60e that detects the exhaust linkage mechanism M1e that shakes by motor 80 and exhaust cam 54 by potentiometer.

The store memory storage of ECU 92 is that parameter has been set the valve control diagram that shakes the position with operation amount D.And, the operation amount D that ECU 92 correspondences are detected by output required amount detection device 95 and by the actual position of shaking of the carriage 60e that shakes the exhaust linkage mechanism M1i that position detecting device 94 detects, be exhaust cam 54 reality shake position control motor 80, make it to reach the position of shaking that above-mentioned valve control graph sets.Therefore, when the change in location of the Control Shaft 70 that drives by motor 80, exhaust linkage mechanism M1e (air-breathing linkage mechanism M1i) with the pivotal position of the relative camshaft 50 of exhaust cam 54 (air inlet cam 53), promptly shaking the position will respective operations amount D and change, the valve event characteristic of exhaust valve 23 (intake valve 22) is controlled with regard to the operating condition of corresponding internal-combustion engine E.

Detailed process is as follows:

As shown in figure 11, as the valve event characteristic Ki that controls respectively by the M of valve characteristic changing mechanism that changes opening and close timing and maximum lift amount, the elemental motion characteristic of Ke, with maximum valve event characteristic Kimax, Kemax and minimum valve event characteristic Kimin, Kemin is limiting value, opens and closes intake valve and exhaust valve with any middle valve acting characteristic in the middle of maximum valve event characteristic Kimax, Kemax and minimum valve event characteristic Kimin, the Kemin.For this reason, for intake valve 22, along with it is opened timing and forms retardation angle continuously, closing timing forms lead angle continuously and opens even shortening valve timing with contracting, and then, the corner (perhaps the pivotal position of bent axle 15, be crank shaft angle) that obtains the camshaft 50 of maximum lift amount forms retardation angle continuously, and meanwhile, maximum lift amount reduces continuously.And, with the valve event characteristic changing of intake valve 22 in, at exhaust valve 23, along with it opens the continuous retardation angle that forms valve timing, close timing and form lead angle continuously, shorten continuously valve timing and open, and then, the corner that obtains the camshaft 50 of maximum lift amount forms lead angle continuously, and maximum lift amount reduces continuously.

In the lump with reference to Figure 12, when the Control Shaft 70 and the air-breathing control link 71i that are driven by driving mechanism M2 are in Figure 12 (A), during primary importance (B), the timing of opening that can obtain intake valve 22 is maximum lead angle position θ iomax, it closes timing is maximum retardation angle position θ icmax, and it opens valve timing and maximum lift amount all is maximum valve event dynamic response Kimax, and the timing of opening that can access exhaust valve 23 simultaneously is maximum lead angle position θ eomax, it closes timing is maximum retardation angle position θ ecmax, and it opens during the valve and maximum lift amount all is maximum valve event characteristic Kemax.

In addition, in Figure 12, Figure 13, represent the row linkage mechanism M1e (air-breathing linkage mechanism M1i) of exhaust valve 23 (intake valve 22) when closing and the state of exhaust master rocker 42 (air-breathing master rocker 41) with solid line and dotted line; Represent the exhaust linkage mechanism M1e (air-breathing linkage mechanism M1i) of exhaust valve 23 (intake valve 22) when opening and the state roughly of exhaust master rocker 42 (air-breathing master rocker 41) with double dot dash line with maximum lift amount.

In operating condition according to internal-combustion engine E, by the M of valve characteristic changing mechanism from the state that obtains maximum valve event characteristic Kimax, Kemax when the state that obtains minimum valve event characteristic Kimin, Kemin moves, motor 80 drives output gears 72 and rotates, Control Shaft 70 by above-mentioned feed screw mechanism towards camshaft 50 turnover.At this moment, driven quantity based on motor 80, Control Shaft 70 is by air-breathing control link 71i, air-breathing linkage mechanism M1i and air inlet cam 53 are shaken for middle mind-set sense of rotation R1 with camshaft 50, simultaneously by exhaust control link 71e, exhaust linkage mechanism M1e and exhaust cam 54 are shaken for middle mind-set reverse directions R2 with camshaft 50.

And, when Control Shaft 70 and exhaust control link 71e are in Figure 13 (A), during the second place (B), the timing of opening that can access intake valve 22 is position, minimum lag angle θ iomin, it closes timing is position, minimum advance angle θ icmin, and it opens during the valve and maximum lift amount all is minimum minimum valve event dynamic response Kimax, and the timing of opening that can access exhaust valve 23 simultaneously is position, minimum lag angle θ eomin, it closes timing is position, minimum advance angle θ ecmin, and it opens during the valve and maximum lift amount all is minimum minimum valve event characteristic Kemin.

And, when Control Shaft 70 when said second position moves to above-mentioned primary importance, it is moving to counter rotation that motor 80 drives output gears 82, Control Shaft 70 retreats by feed screw mechanism and leaves camshaft 50.At this moment, Control Shaft 70 is by air-breathing control link 71i, air-breathing linkage mechanism M1i and air inlet cam 53 are shaken for middle mind-set reverse directions R2 with camshaft 50, simultaneously by exhaust control link 71e, exhaust linkage mechanism M1e and exhaust cam 54 are shaken for middle mind-set sense of rotation R1 with camshaft 50.

In addition, when Control Shaft 70 is in position between above-mentioned primary importance and the said second position, exhaust valve 23 (intake valve 22) can access in maximum valve event characteristic Kemax (Kimax) and minimum valve event characteristic Kemin (Kimin), set become out timing, close timing, open be worth between valve timing and the maximum lift amount open timing, close timing open valve during and the numerous above-mentioned middle valve acting characteristic of maximum lift amount.

And, except that above-mentioned elemental motion characteristic,, carry out air-breathing closing and the exhaust valve on-off action respectively by the M of valve characteristic changing mechanism also with the auxiliary movement characteristic.Describe the actual process that obtains as the decompression acting characteristic of above-mentioned auxiliary movement characteristic in detail with reference to Figure 14 (A), (B).In the compression stroke that internal-combustion engine E begins to start, it is moving to counter rotation that motor 80 drives output gears 82, and Control Shaft 70 surpasses above-mentioned primary importance, is in the position that will leave camshaft 50 and retreat, is decompression position.At this moment, exhaust linkage mechanism M1e (air-breathing linkage mechanism Mi1) and exhaust cam 54 (air inlet cam 53) shake to sense of rotation R1 (reverse directions R2), relief cam 62e1 (62i1) contact of the second plate 62e (62i) is near the relief portion 42d (41d) the roller 42c (41c) that is arranged at exhaust master rocker 42 (air-breathing master rocker 41), roller 42c (41c) leaves exhaust cam 54 (air inlet cam 53), and exhaust valve 23 (intake valve 24) is opened little aperture, the i.e. aperture that reduces pressure.

With reference to Figure 11 as can be known, the valve event characteristic of corresponding intake valve 22 and exhaust valve 23, near the intake valve 22 air-breathing top dead center and the cover time Pa of exhaust valve 23 and non-cover time Pb change.Promptly, can obtain maximum cover time Pax at maximum valve event characteristic Kimax, Kemax, can obtain maximum non-cover time Pbx at minimum valve event characteristic Kimin, Kemin, middle valve acting characteristic between two valve event characteristics, along with moving to minimum valve event characteristic Kimin, Kemin from maximum valve event characteristic Kimax, Kemax, cover time Pa is reduced to 0 (zero), and non-cover time Pb increases from 0 (zero).At this, cover time Pa is near air-breathing top dead center, and exhaust valve 23 and intake valve 22 all are in out valve state, is the scope of opening the crank shaft angle (perhaps camshaft rotational angle) between the timing of closing timing and intake valve 22 of exhaust valve 23.Non-cover time Pb is near air-breathing top dead center, and exhaust valve 23 and intake valve 22 all are in a state of holding one's breath, and is the scope of the crank shaft angle of opening timing of closing timing and intake valve 22 (perhaps camshaft rotational angle) of exhaust valve 23.

And, when detecting to warming-up by engine temperature detection device 96, just shown in Fig. 4 (C), for obtain the full load scope of internal-combustion engine E and operation amount D irrelevant control the valve event characteristic of intake valve 22 and exhaust valve 23 with the fixing cover time Pa of established amount (serve as maximum cover time Pax at this), ECU 92 controls motor 80 based on above-mentioned valve control graph.At this, when warming-up, the M of valve characteristic changing mechanism will open and close intake valve 22 and exhaust valve 23 at maximum valve event characteristic Kimax, Kemax, and control valve event characteristic does not form non-cover time Pb in load is region-wide.

In addition, ECU 92, in the time of after being warming-up by 96 detections of engine temperature detection device, shown in Fig. 4 (D), make the M of valve characteristic changing mechanism control valve event characteristic, with above-mentioned whole load areas by with 30 concerted actions of throttling valve, obtain the internal-combustion engine output of corresponding required amount, controlling combustion engine output according to operation amount D control cover time Pa or non-cover time Pb.

With reference to Fig. 4, Figure 11, the M of valve characteristic changing mechanism, control valve event characteristic makes at the first load area Fa and reduces cover time Pa along with required amount increases, and reaching 0 (zero) increases non-cover time Pb afterwards, obtains maximum non-cover time Pbx before reaching given load Da; Make at the second load area Fb, reduce non-cover time Pb along with required amount increases from the non-cover time Pbx of maximum, reaching 0 (zero) increases cover time Pa afterwards, at maximum load (maximum operation amount) Db, obtains maximum cover time Pax.And at this valve device 40, the M of valve characteristic changing mechanism changes the opening and close timing of intake valve 22 and the opening and close timing of exhaust valve 23, control cover time Pa and non-cover time Pb, thus, control internal EGR rate N.

Internal EGR rate N represents the ratio of burnt gas amount residual in the amount of new gas of firing chamber 16 and the firing chamber 16, defines with following formula.

N＝Vce/(Vc-Vca)

In the formula, Vc: at the volume of cylinder of air-breathing lower dead center;

Vca: the volume of cylinder of intake valve when effective hoisting load;

Vce: the volume of cylinder of exhaust valve when effective hoisting load;

The effective hoisting load of intake valve: the lifting capacity of the intake valve of new gas when suction port begins to flow in the firing chamber by the intake valve of opening is actual;

The effective hoisting load of exhaust valve: burnt gas flows out exhaust port, the lifting capacity of the exhaust valve when finishing practically from the firing chamber by the exhaust valve of opening.

Therefore, internal EGR rate N, at minimum internal EGR rate Nn that the maximum cover time Pax that is used in maximum valve event characteristic Kimax, Kemax obtains with in the maximum internal EGR that the maximum non-cover time Pbx of minimum valve event characteristic Kimin, Kemin obtains leads the control range of Nx regulation, along with the valve event characteristic moves to minimum valve event characteristic Kimin, Kemin from maximum valve event characteristic Kimax, Kemax, leading Nx from minimum internal EGR rate Nn to maximum internal EGR increases continuously.

And when warming-up, the valve event characteristic of the M of valve characteristic changing mechanism control intake valve 22 and exhaust valve 23 makes that irrespectively to keep internal EGR rate N at load gamut and operation amount D be minimum internal EGR rate Nn.In addition, behind warming-up, change the M of mechanism according to operation amount D control cover time Pa or non-cover time Pb, by internal EGR rate N or by internal EGR amount controlling combustion engine output with internal EGR rate N regulation at load gamut valve event.More particularly, behind warming-up, the M of valve characteristic changing mechanism, the valve event characteristic of control intake valve 22 and exhaust valve 23, making at the first load area Fa increases internal EGR rate N from uncharge minimum internal EGR rate Nn along with the increase of operation amount D, obtains maximum internal EGR and lead Nx before reaching given load Da; Make at the second load area Fb and lead Nx, reduce internal EGR rate N, obtain minimum internal EGR rate Nn at maximum load Db along with the increase of operation amount D from maximum internal EGR at given load Da.

In addition, if for intake valve 22 leave valve seat 24 actual open open timing, use intake valve 22 to open the timing of valve, promptly effectively drive timing and exhaust valve 23 and open the timing of valve, promptly effectively close timing with effective hoisting load with effective hoisting load, just can enough effective cover time Pae and effective non-cover time Pbe represent cover time Pa and non-cover time Pb.In addition, in present embodiment, the above-mentioned effective hoisting load of intake valve 22 and exhaust valve 23 is identical value.

Below, use the control that the valve event characteristic of being undertaken by the M of valve characteristic changing mechanism is described by the effective non-cover time Pbe that effectively opens timing and effectively close the timing regulation.The valve event characteristic of valve characteristic changing mechanism controls intake valve 22 and exhaust valve 23 makes when hot machine in that load is region-wide effective cover time Pae and effective non-cover time Pbe is fixed as 0 (zero); Behind hot machine, in the increase of the first load area Fa along with operation amount D, effective non-cover time Pbe is from being increased to the maximum value at given load Da at uncharge 0 (zero); In the increase of the second load area Fb along with operation amount D, it is 0 (zero) of peaked busy hour that effective non-cover time Pbe reduces at operation amount D from maximum value.In addition, in present embodiment, the corner (crank shaft angle) of the camshaft 50 that effective cover time Pae and effective non-cover time Pbe are 0 (zero) is air-breathing top dead centers.

And, be minimum value at the effective cover time Pae that obtains by intake valve 22 that opens and closes with maximum valve event characteristic Kimax, Kemax and exhaust valve 23 and effective non-cover time Pbe, when being 0 (zero), inner GER leads N becomes minimum internal EGR rate Nn; When the effective non-cover time Pbe that is obtained by intake valve 22 that opens and closes with minimum valve event characteristic Kimin, Kemin and exhaust valve 23 was maximum value Pbex, internal EGR rate N became maximum internal EGR and leads Nx.

Below, effect and effect as the mode of execution of above-mentioned structure are described.

When the warming-up of internal-combustion engine E, throttling control mechanism T is region-wide at the load of internal-combustion engine E, to increase the aperture that the aperture mode is controlled throttling valve 30 along with the increase of operation amount D, the M of valve characteristic changing mechanism is not to form the valve event characteristic that non-cover time Pb mode is controlled intake valve 22 and exhaust valve 23 in that load is region-wide, and state of a control is carried out the control of internal-combustion engine E when the control range internal EGR rate N of internal EGR rate N becomes minimum hot machine.Thus, region-wide at load when warming-up, new gas is supplied with firing chamber 16 by throttling valve 30 according to operation amount D control flow rate.In addition, owing to do not form non-cover time Pb by the M of valve characteristic changing mechanism, compare with the occasion that forms non-cover time Pb, control internal EGR rate N reduces, and makes the control range at internal EGR rate N become minimum.Thereby, can improve combustion efficiency, combustion temperature also increases, so region-wide at load, combustion efficiency improves, combustion stability improves, combustion temperature increases, and has promoted the warming-up of internal-combustion engine.In addition,, also promoted to be arranged on Exhaust gas purifying device on the above-mentioned venting gas appliance, be the warming-up of catalysis device because combustion temperature increases, thereby, accelerated the activate of catalysis device, improve the exhaust gas purification ability.

Behind the warming-up of internal-combustion engine E, the aperture of throttling control mechanism T control throttling valve 30 makes at the first load area Fa to reach the standard-sized sheet at given load Da along with the increase of operation amount D from the idling aperture, and, be standard-sized sheet at the second load area Fb envoy gas door 30.The M of valve characteristic changing mechanism is region-wide according to operation amount D control cover time Pa or non-cover time Pb at load, export by internal EGR rate N controlling combustion engine, and, control valve event characteristic, make to obtain maximum internal EGR at given load Da by the non-cover time Pbx of maximum and lead Nx,, make at load region-wide especially at low-load region F1 by the State Control internal-combustion engine E behind the above-mentioned warming-up, loss of suction more reduces, and improves the fuel consumption performance.On the other hand, in the region-wide internal EGR rate N controlling combustion engine output of using the control by cover time Pa and non-cover time Pb to form of load, export with the internal-combustion engine that obtains respective operations amount D.Thereby the suction and discharge loss reduces, and the generating capacity of NOx reduces simultaneously.And then, lead N because form maximum internal EGR at given load Da, thus the generating capacity of the loss of suction of the low-load region F1 given load Da near and NOx reduce significantly, thereby, improve the fuel consumption performance, improve exhaust purification performance.

In addition, state of a control behind above-mentioned warming-up, the valve event characteristic of the M of valve characteristic changing mechanism control intake valve 22 and exhaust valve 23, making at the first load area Fa makes internal EGR rate N from uncharge minimum internal EGR rate Nn, along with operation amount D increases and increases, reach maximum internal EGR at given load Da to lead Nx; Make and make internal EGR rate N lead Nx at the second load area Fb to increase with operation amount D and reduce, reach minimum internal EGR rate Nn at maximum load Db from maximum internal EGR at given load Da.Thus, at the first load area Fa, flow in the firing chamber 16 owing to control new gas, thereby the suction and discharge loss reduces the generating capacity of NOx minimizing simultaneously by the aperture increase internal EGR rate N that increases throttling valve 30.In addition, at the second load area Fb, non-cover time Pb reduces along with the increase of operation amount D, thereby internal EGR rate N reduces, and the new gas flow of supplying with firing chamber 16 increases.Thereby along with near given load Da, internal EGR rate N increases, loss of suction reduces thus, and the generating capacity of NOx reduces simultaneously, improves the fuel consumption performance, improve exhaust purification performance, obtain big internal-combustion engine output, guarantee the internal-combustion engine output of the needs of amount as requested at high-load region F3.

The M of valve characteristic changing mechanism control valve event characteristic, at the first load area Fa, at the load area littler than given load Da, maximum internal EGR be can obtain and Nx and maximum non-cover time Pbx and maximum effective non-cover time Pbex led, thus, just further reduce the air-breathing loss of the first load area Fa, thereby improve the fuel consumption performance, and then, improve exhaust purification performance.

The M of valve characteristic changing mechanism control valve event characteristic makes the maximum lift amount of intake valve 22 along with the increase of the minimizing of cover time Pa, non-cover time Pb, effective non-cover time Pbe reduce from effective cover time Pae and effective non-cover time Pbe state increase that all is 0 (zero) and the increase of internal EGR rate N.Thus, when cover time Pa increases, when the non-cover time, Pb reduced, effective when the non-cover time, Pbe reduced and internal EGR rate N when reducing, the maximum lift amount of intake valve 22 increases, thereby air-breathing exhaust loss reduces.In addition, near given load Da, when the cover time, Pa reduced, when non-cover time Pb increases, effective when the non-cover time, Pbe was big and internal EGR rate N when big, because internal EGR rate N increases, air-breathing loss is reduced, thereby near the suction and discharge loss the first load area Fa and given load Da reduces, the fuel consumption performance improvement.

Simultaneously, the M of valve characteristic changing mechanism control valve event characteristic makes the maximum lift amount of exhaust valve 23 along with the increase of the minimizing of cover time Pa, non-cover time Pb, effective non-cover time Pbe reduce from effective cover time Pae and effective non-cover time Pbe state increase that all is 0 (zero) and the increase of internal EGR rate N.Thus, when cover time Pa increases, when the non-cover time, Pb reduced, effective when the non-cover time, Pbe reduced and internal EGR rate N when reducing, the maximum lift amount of exhaust valve 23 increases, thereby air-breathing exhaust loss reduces.In addition, near given load Da, when the cover time, Pa reduced, when non-cover time Pb increases, effective when the non-cover time, Pbe was big and internal EGR rate N when big, because internal EGR rate N increases, air-breathing loss is reduced, thereby near the suction and discharge loss the first load area Fa and given load Da reduce, at this point, the fuel consumption performance also improves.

The M of valve characteristic changing mechanism control valve event characteristic, at maximum cover time Pax or minimum internal EGR rate Nn, making effective cover time Pae and effective non-cover time Pbe is zero.Thus, in the control range of internal EGR rate N, with the gas that has fired actually stop from the firing chamber 16 flowing out, the actual time that begins to flow into firing chamber 16 of new gas is benchmark, the control of beginning internal EGR rate N, so, the control accuracy of raising internal EGR rate N, and, can also enlarge the control range of internal EGR rate N, thereby, can improve by internal EGR rate N control with by the output control accuracy of the internal-combustion engine of effective non-cover time Pbe control.

At the M of valve characteristic changing mechanism, be connected with each linkage mechanism M1i, M1e at control mechanism M3 driving mechanism M2, making is being increased on the direction that forms internal EGR rate N increase by cover time Pa minimizing, non-cover time Pb or effective non-cover time Pbe, when being driven by driving mechanism M2, it is bigger than the leading angle that closes timing of the exhaust valve 23 that is formed by exhaust linkage mechanism M1e to make the intake valve 22 that is formed by air-breathing linkage mechanism M1i open the hysteresis angle of timing.Thus, the M of valve characteristic changing mechanism, when the direction that increases at internal EGR rate N reduces cover time Pa, increase non-covering Pb, and when increasing effective non-cover time Pbe, the hysteresis angle of opening timing of intake valve 22 is increased than the leading angle that exhaust valve 23 closes timing, thereby, the closing that timing forms lead angle of exhaust valve 23 and when remaining in burnt gas increased pressure in the firing chamber 16, hysteresis angle during with the opening of intake valve 22 is compared smaller or equal to the occasion of the leading angle that closes timing of exhaust valve 23, begin to open during intake valve 22 state that 16 pressure is lower in the firing chamber, thereby, can prevent or suppress the air inlet blowback.

Moving centre line L 4i of pivot and the moving centre line L 4e of pivot are offset to exhaust side, are parallel to rotary centerline L2 configuration for datum plane H0, the moving centre line L 5i of pivot is configured in exhaust side, the moving centre line L 5e of pivot is configured in suction side, thus, when Control Shaft 70 moves, air-breathing linkage mechanism M1i is that the center is shaken with the shaking quantity bigger than exhaust linkage mechanism M1e with camshaft 50, obtains the valve event characteristic of the hysteresis angle of opening timing of intake valve 22 than the leading angle increase of closing timing of exhaust valve 23.Like this, because the Control Shaft 70 of air-breathing linkage mechanism M1i and the shared control mechanism M3 of exhaust linkage mechanism M1e, also because the configuration of the moving centre line L 4i of pivot, the moving centre line L 4e of pivot, the moving centre line L 5i of pivot and the moving centre line L 5e relative datum plane H0 of pivot, realize the valve characteristic changing M of mechanism miniaturization and simplify the structure.

Moving centre line L 4i of pivot and the moving centre line L 4e of pivot are parallel to rotary centerline L2 configuration, the moving centre line L 5i of pivot is configured in exhaust side, the moving centre line L 5e of pivot is configured in suction side, the length of connecting rod of air-breathing control link 71i is longer than the length of connecting rod of exhaust control link 71e, like this, when Control Shaft 70 moves, air-breathing linkage mechanism M1i is that the center is shaken with the shaking quantity bigger than exhaust linkage mechanism M1e with camshaft 50, obtain the hysteresis angle of the opening timing valve event characteristic bigger of intake valve 22 than the leading angle that closes timing of exhaust valve 23, thereby, because the Control Shaft 70 of air-breathing linkage mechanism M1i and the shared control mechanism M3 of exhaust linkage mechanism M1e, also because moving centre line L 5i of pivot and L5e are in the length of connecting rod of the connecting rod of configuration of datum plane H0 both sides and air-breathing control link 71i than exhaust control link 71e, therefore, valve characteristic changing mechanism realizes miniaturization, and its structure realizes oversimplifying.

In addition, because moving centre line L 4i of pivot and L4e constitute the moving center line of common pivot, therefore, and the M of valve characteristic changing mechanism miniaturization more, its structure is more oversimplified.

Below, a part that relates to the above-mentioned mode of execution of change is described, the structure of the change of the mode of execution of structure.

With reference to Fig. 6, Figure 12, exhaust linkage mechanism M1e (air-breathing linkage mechanism M1i) has: when 70 motions of driving mechanism M2 drive controlling axle, when shaking exhaust linkage mechanism M1e (air-breathing linkage mechanism M1i), hold rotary centerline L2 with camshaft 50 and be the moving portion's (air-breathing pivot moves portion) of exhaust pivot of the moving center line of pivot that shakes at the center by exhaust control link 71e (air-breathing control link 71i).Therefore, the distance of moving center line of the pivot of the moving portion of above-mentioned air-breathing pivot and rotary centerline L2 is shorter than the distance of moving center line of the pivot of the moving portion of above-mentioned exhaust pivot and rotary centerline L2, like this, when Control Shaft 70 and exhaust control link 71e (air-breathing control link 71i) driven-mechanism M2 driving, air-breathing linkage mechanism M1i can be that air inlet cam 53 is shaken at the center with camshaft 50 with being the shaking quantity that exhaust cam 54 is shaken at the center greater than exhaust linkage mechanism M1e with camshaft 50 also.

Here, the moving portion of above-mentioned air-breathing pivot is made of the joint 61i1 of each first plate 61i and the fulcrum 66ia of air-breathing secondary-rocker 66i and the support 63i2 (with reference to Fig. 6) of sleeve pipe 63i respectively.In addition, the moving center line of the pivot of the moving portion of above-mentioned each air-breathing pivot is the moving centre line L 5i of pivot, shakes centre line L 3i.

Similarly, the moving portion of exhaust pivot is made of the joint 61e1 of each first plate 61e and the fulcrum 66ea of air-breathing secondary-rocker 66e and the support 63e2 (with reference to Fig. 6) of sleeve pipe 63e respectively.In addition, the moving center line of the pivot of the moving portion of above-mentioned each exhaust pivot is the moving centre line L 5e of pivot, shakes centre line L 3e.

And, the distance of setting moving centre line L 5i of pivot and rotary centerline L2 is shorter than the distance of moving centre line L 5e of pivot and rotary centerline L2, perhaps, setting the distance of shaking centre line L 3i and rotary centerline L2 lacks than the distance of shaking centre line L 3e and rotary centerline L2.

Like this, when air-breathing linkage mechanism M1i and the controlled M3 of mechanism of exhaust linkage mechanism M1e shake, because the moving portion of the above-mentioned air-breathing pivot of air-breathing linkage mechanism M1i has the moving centre line L 5e of pivot that is positioned at than the moving portion of above-mentioned exhaust pivot of exhaust linkage mechanism M1e, the pivot of the position that L3e is near apart from the rotary centerline L2 of camshaft 50 moves centre line L 5i, L3i, so, control mechanism M3 is that air inlet cam 53 and exhaust cam 54 are shaken in the center by air-breathing linkage mechanism M1i and exhaust linkage mechanism M1e with camshaft 50, makes the shaking quantity of air inlet cam 53 bigger than the shaking quantity of exhaust cam 54.The M of valve characteristic changing mechanism of the valve event characteristic of the leading angle of the hysteresis angle when as a result, realizing being used to obtaining the opening of intake valve 22 during greater than the closing of exhaust valve 23 simplifies the structure.

Given load Da also can be the load among the intermediate load region F2.Above-mentioned fuel supplying device also can be the fuel injection valve to firing chamber inner direct fuel.

Internal-combustion engine also can be a multi-cylinder internal-combustion engine.In addition, also can be the internal-combustion engine of in a cylinder, establishing a plurality of intake valves and one or more exhaust valves, perhaps, in a cylinder, establish the internal-combustion engine of a plurality of exhaust valves and one or more intake valves.

At the given load Da and the second load area Fb, throttling valve 30 is standard-sized sheet substantially also, and in addition, at maximum cover time Pax and minimum internal EGR rate Nn, effectively cover time Pae and effective non-cover time Pbe can be 0 substantially also; In addition, when warming-up, minimum is also passable substantially at the region-wide internal EGR rate N of load.When " substantially " is meant respectively with throttling valve 30 standard-sized sheets here, effectively cover time Pae and effective non-cover time Pbe are that 0 o'clock, internal EGR rate N are hour to compare, action effect not have the scope of difference intentionally.

Claims

1. the valve device of an internal-combustion engine, it has the valve characteristic changing mechanism of the valve event characteristic of controlling intake valve and exhaust valve respectively, change the opening and close timing of described intake valve and described exhaust valve and control the cover time and control of non-cover time internal EGR rate by described valve characteristic changing mechanism, it is characterized in that described valve characteristic changeable mechanism has: the camshaft that rotates with the bent axle interlock of described internal-combustion engine; Be connected according to the air-breathing double-action mechanism on the air inlet cam of the described intake valve of rotating switch of described camshaft; Be connected according to the exhaust double-action mechanism on the exhaust cam of the described exhaust valve of rotating switch of described camshaft; Making described each double-action mechanism is center control mechanism that shakes and the driving mechanism that drives described control mechanism with described camshaft, by reducing the described cover time or increasing the described non-cover time and when improving on the described internal EGR rate direction by the described control mechanism of described drive mechanism, connect described driving mechanism and described each double-action mechanism so that the retardation angle of the described IVO Inlet Valve Open timing that described air-breathing double-action mechanism forms is closed the lead angle of timing greater than the described exhaust valve that is formed by described exhaust double-action mechanism, described control mechanism has: controlling component, it is by described drive mechanism, can move being parallel to the rotary centerline that comprises camshaft and being parallel on the direction of datum plane of cylinder-bore axis; Air-breathing control link, it is dynamically connected by described controlling component pivot at the first air-breathing joint, is dynamically connected by described air-breathing double-action mechanism pivot at the second air-breathing joint; The exhaust control link, it is dynamically connected by described controlling component pivot at the first exhaust joint, be dynamically connected by described exhaust double-action mechanism pivot at the second exhaust joint, by the moving center line of pivot of the described first air-breathing joint and the pivot of the described first exhaust joint are moved the relative described datum plane of center line, be configured in a side with being parallel to described rotary centerline, the pivot of the described second air-breathing joint is moved centreline configuration in a described side, the moving described relatively datum plane of center line of the pivot of the described second exhaust joint is configured in opposite side, makes that described air-breathing double-action mechanism is that the center is shaken with the shaking quantity greater than described exhaust double-action mechanism with described camshaft when described controlling component moves.

2. the valve device of internal-combustion engine as claimed in claim 1, it is characterized in that, the length of described air-breathing control link is longer than the length of described exhaust control link, and described air-breathing double-action mechanism was that the center is shaken with the shaking quantity greater than described exhaust double-action mechanism with described camshaft when described controlling component was moved.

3. the valve device of internal-combustion engine as claimed in claim 1 or 2, it is characterized in that, described air-breathing double-action mechanism has the moving portion of air-breathing pivot, and it has, and the rotary centerline with described camshaft is the moving center line of pivot that the center is shaken when described air-breathing double-action mechanism is shaken; Described exhaust double-action mechanism has the moving portion of exhaust pivot, and it has when described exhaust double-action mechanism is shaken with described rotary centerline is the moving center line of pivot that the center is shaken; The distance of moving the described rotary centerline of the moving center line distance of pivot of center line and the moving portion of described exhaust pivot by the pivot that makes the moving portion of described air-breathing pivot is equidistant, and the moving center line of the pivot of the moving portion of described air-breathing pivot is than the more close vertical plane that comprises the rotary centerline while perpendicular to described datum plane of the moving center line of the pivot of the moving portion of described exhaust pivot, and described air-breathing double-action mechanism is used than being that the center is shaken the big shaking quantity of described exhaust cam to make described air inlet cam be that the center is shaken with described camshaft by described exhaust double-action mechanism with described camshaft.