CN103306774B - Valve lift adjusting device - Google Patents

Valve lift adjusting device Download PDF

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Publication number
CN103306774B
CN103306774B CN201310070745.0A CN201310070745A CN103306774B CN 103306774 B CN103306774 B CN 103306774B CN 201310070745 A CN201310070745 A CN 201310070745A CN 103306774 B CN103306774 B CN 103306774B
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CN
China
Prior art keywords
sliding device
external gear
camshaft
cam
plane cam
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
CN201310070745.0A
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Chinese (zh)
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CN103306774A (en
Inventor
天野均
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Denso Corp
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Denso Corp
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Filing date
Publication date
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Publication of CN103306774A publication Critical patent/CN103306774A/en
Application granted granted Critical
Publication of CN103306774B publication Critical patent/CN103306774B/en
Expired - Fee Related legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/185—Overhead end-pivot rocking arms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F01L2013/0052—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction with cams provided on an axially slidable sleeve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2305/00—Valve arrangements comprising rollers

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

The invention relates to a valve lift adjusting device (10, 90, 100), comprising a first plate cam (25), a second plate cam (30), a cylindrical sliding apparatus (50, 91, 101), a limiting component (71), a drive unit (73), and a reduction gear (80, 92, 102). The sliding apparatus can integrally conduct axial movement between a first running position and a second running position on the first and second plate cams. When a cam shaft (21) is rotated, the limiting component is inserted in a joint groove (51) so as to be jointed to a first oblique surface (55), the sliding apparatus is moved to the second running position by the limiting component. When the cam shaft (21) is rotated, the limiting component is inserted in the joint groove so as to be jointed to a second oblique surface (59), the sliding apparatus is moved to the first running position by the limiting component. The limiting component is operated by the drive unit to be inserted in the joint groove. The rotation of the cam shaft is reduced by the reduction gear, so that the cam shaft can be transmitted to the sliding apparatus.

Description

Valve stroke controlling device
Technical field
The disclosure relates to a kind of valve stroke controlling device.
Background technique
Known valve stroke controlling device comprise can be by the convert rotational motion of the camshaft of internal-combustion engine the linear reciprocating motion of engine valve two kinds of plane cams and by switching to regulate the valve stroke of engine valve between plane cam.In the valve stroke controlling device that US Patent No. 2011/0247577A1 describes, two kinds of plane cams are coupled to camshaft can transmit and rotate and can axial relative displacement.Plane cam in the axial direction neighboringly location and integrally formed with each other.The switching of plane cam is performed by sliding device.
Sliding device be in the axial direction with the Cylinder shape constructional element of plane cam integrally displacement.Sliding device comprises the groove of winding in radial outer wall, and the axial position of sliding device is by inserting the banking pin restriction of this groove.In US Patent No. 2011/0247577A1, the first half semi-perimeter parts of groove are used for mobile sliding device to be switched to a plane cam, and the second half semi-perimeter parts of groove are used for mobile sliding device to be switched to another plane cam.Sliding device is displaced to two axial positions by a banking pin by valve stroke controlling device.
In the valve stroke controlling device that US Patent No. 2011/0247577A1 describes, it is required that banking pin is inserted in groove while sliding device rotates about 1/4th weeks.For this reason, the driver element of banking pin needs to activate banking pin rapidly.Especially, when the rotating speed of motor becomes higher, the service speed of driver element needs faster.If banking pin postpones to be inserted in groove, so likely insufficient between banking pin and groove joint or disengagement.
As the measure for above problem, the operation elapsed time of banking pin can shift to an earlier date.But, if the operation elapsed time of banking pin in advance, so when banking pin is inserted in the first half semi-perimeter parts of groove, such as, banking pin may engage with the second half semi-perimeter parts of groove, and excessive load thus may banking pin be applied to.
Summary of the invention
The disclosure solves at least one in above problem.Therefore, object of the present disclosure is to provide a kind of valve stroke controlling device, and sliding device can be displaced to two axial positions by a limiting member and banking pin reliably can be inserted in groove by it.
For realizing object of the present disclosure, provide a kind of for regulating the valve stroke controlling device of the valve stroke of the engine valve of internal-combustion engine.Valve stroke controlling device comprises the first plane cam, the second plane cam, tubular sliding device, limiting member, driver element and speed reducer.First plane cam is coupled to the camshaft integrally rotated with the output shaft of motor, the rotation of camshaft can be transmitted and can relative to camshaft displacement on the axial direction of camshaft, and can be the linear reciprocating motion of engine valve by the convert rotational motion of camshaft.Second plane cam is coupled to camshaft can transmit the rotation of camshaft and can in the axial direction relative to camshaft displacement, and can be the linear reciprocating motion of engine valve by the convert rotational motion of camshaft.Second plane cam has the cam profile different from the first plane cam.Tubular sliding device is attached to the first plane cam and the second plane cam rotation can be delivered to the first plane cam and the second plane cam, and comprises the engaging groove that the circumferential direction along sliding device extends in the radial outer wall of sliding device.Sliding device can integrally move axially with the first plane cam and the second plane cam between the first and second operating position, engine valve is synchronous with the first plane cam at the first running position, and engine valve is synchronous with the second plane cam at the second running position.Limiting member can be inserted in engaging groove and can to remove from engaging groove.When limiting member to be inserted in engaging groove to engage with the first inclined surface of engaging groove when camshaft rotates, sliding device is displaced to the second running position by limiting member.When limiting member to be inserted in engaging groove to engage with the second inclined surface of engaging groove when camshaft rotates, sliding device is displaced to the first running position by limiting member.Driver element is configured to performance constraint component and is inserted in engaging groove.Speed reducer is used for the rotation of camshaft to slow down to be delivered to sliding device.
Accompanying drawing explanation
By following detailed description by reference to the accompanying drawings, above and other objects, features and advantages of the present disclosure will become more apparent.In the drawings:
Fig. 1 is the schematic diagram showing valve system, and the valve stroke controlling device according to the first embodiment uses in this valve system;
Fig. 2 is the sectional view obtained along the II-II line in Fig. 1;
Fig. 3 is the sectional view obtained along the III-III line in Fig. 1;
Fig. 4 is the sectional view obtained along the IV-IV line in Fig. 1;
Fig. 5 is the schematic diagram showing the valve system observed along the arrow V direction in Fig. 3;
Fig. 6 is the stereogram of the first raised sides of sliding device in exploded view 1;
Fig. 7 is the stereogram of the second raised sides of sliding device in exploded view 1;
According to the first embodiment, Fig. 8 shows that the state towards the banking pin of sliding device projection from Fig. 2 inserts the schematic diagram of the state of engaging groove;
Fig. 9 shows the schematic diagram of sliding device from the state displacement of Fig. 8 to the state of the second running position according to the first embodiment;
According to the first embodiment, Figure 10 shows that the banking pin raised to sliding device inserts the schematic diagram of the state of engaging groove from the state of Fig. 9;
Figure 11 is the schematic diagram showing valve system, and the valve stroke controlling device according to the second embodiment uses in this valve system; And
Figure 12 is the schematic diagram showing valve system, and the valve stroke controlling device according to the 3rd embodiment uses in this valve system.
Embodiment
Embodiment will be described with reference to the drawings below.In order to indicate the structure identical in fact between embodiment, use identical reference character so that the descriptions thereof are omitted.
(the first embodiment)
According to the variable valve mechanism that the valve stroke controlling device of the first embodiment is cam-switching type, and use in valve system as shown in Figure 1.Valve system 20 is the systems of the suction valve 44 being used to open or close internal-combustion engine.
As shown in Fig. 1 to 5, valve system 20 comprises camshaft 21, low rotating cam 25, high rotating cam 30, roller locking device 40, slack adjuster 43, suction valve 44, sliding device 50, actuator 70 and speed reducer 80.
Low rotating cam 25, high rotating cam 30, sliding device 50, actuator 70 and speed reducer 80 form valve stroke controlling device 10.Low rotating cam 25 can be equivalent to " the first plane cam ", and high rotating cam 30 can be equivalent to " the second plane cam ".
Camshaft 21 is rotatably supported in unshowned position by cylinder head 12.As shown in Figures 2 to 4, the spline external tooth extended in the axial direction is formed on the periphery wall of camshaft 21.The output shaft (not shown) of motor is connected to camshaft 21 by timing chain etc.Camshaft 21 and this output shaft integrally rotate.
First external gear 81 of low rotating cam 25, high rotating cam 30, speed reducer 80 is made up of identical components and integrally formed with each other.Low rotating cam 25 is the disk cams being coupled to camshaft 21.Be formed in the periphery wall of low rotating cam 25 with the nose of cam 27 of prearranging quatity from basic circle 26 radially outward projection.
The spline internal tooth extended in the axial direction is formed in the inner radial wall of low rotating cam 25.Spline internal tooth engages with the spline external tooth of camshaft 21.Low rotating cam 25 be connected to camshaft 21 in case can transmit rotate and can relative displacement in the axial direction.
Low rotating cam 25 forms low rotary cam structure together with roller locking device 40, and the convert rotational motion of camshaft 21 is the linear reciprocating motion of suction valve 44 by it.In this low rotary cam structure, low rotating cam 25 is used as drive unit, and roller locking device 40 is used as driven device.
High rotating cam 30 is the disk cams being coupled to camshaft 21 and being close to low rotating cam 25 location in the axial direction.Be formed in high rotating cam 30 periphery wall from the nose of cam 32 of basic circle 31 radially outward projection with prearranging quatity.Basic circle 26 and basic circle 31 are formed as identical surface configuration and do not have height difference.
The cam profile of high rotating cam 30 is different from the cam profile of low rotating cam 25.Such as, the maximum cam lift of high rotating cam 30 is greater than the maximum cam lift of low rotating cam 25.In addition, the cam of high rotating cam 30 runs the cam operation angle that angle is greater than low rotating cam 25.
The spline internal tooth extended in the axial direction is formed on the inwall of high rotating cam 30.Spline internal tooth engages with the spline external tooth of camshaft 21.High rotating cam 30 be connected to camshaft 21 in case can transmit rotate and can relative displacement in the axial direction.
High rotating cam 30 forms high rotary cam structure together with roller locking device 40, and the convert rotational motion of camshaft 21 is the linear reciprocating motion of suction valve 44 by it.In this high rotary cam structure, high rotating cam 30 is used as drive unit, and roller locking device 40 is used as driven device.
Roller locking device 40 comprises Rocker arm 41 and roller 42.An end of Rocker arm 41 contacts with slack adjuster 43, and another end of Rocker arm 41 contacts with the end of the handle 45 of suction valve 44.Rocker arm 41 can shake using one end thereof as the strong point that its another end is separated close to camshaft 21 or with camshaft 21.
Roller 42 is configured between an end of Rocker arm 41 and another end.As shown in Figure 1, when cam and sliding device 50 are positioned on side in the axial direction, roller 42 contacts with the periphery wall of low rotating cam 25.The axial position of cam and sliding device 50 is called as " the first running position " in this case.
Shown in Fig. 9 as described below, when cam and sliding device 50 are located on another side in the axial direction, roller 42 contacts with the periphery wall of high rotating cam 30.The axial position of cam and sliding device 50 is called as " the second running position " in this case.
Referring back to Fig. 1 to 5, suction valve 44 is poppet valves, and can open or close the suction port of the cylinder of motor.Suction valve 44 is ordered about on valve closing direction by spring (not shown), and opens this suction port when being pressed by the nose of cam 32 of the nose of cam 27 or high rotating cam 30 of low rotating cam 25 by Rocker arm 41.
Sliding device 50 forms tubular, and contiguous low rotating cam 25 is located on the side contrary with high rotating cam 30 in the axial direction of low rotating cam 25.Sliding device 50 can rotate around the axial centre (axle center) relative to camshaft 21 bias, and can relative to camshaft 21 displacement in the axial direction.Camshaft 21 is through the inner side of sliding device 50.Speed reducer 80 is configured in the inner radial of sliding device 50.Sliding device 50 is connected to camshaft 21 rotation can be delivered to camshaft 21 by speed reducer 80.Speed reducer 80 will describe hereinafter comprehensively.
Sliding device 50 can integrally move with cam in the axial direction between the first and second operating position.First running position is by suction valve 44 position synchronous with low rotating cam 25.Second running position is by suction valve 44 position synchronous with high rotating cam 30.When sliding device 50 in the axial direction displacement time, cam and sliding device 50 integrally move.
The periphery wall of sliding device 50 is included in the engaging groove 51 that its circumferential direction extends.In the present embodiment, the axial width of engaging groove 51 is identical along the whole circumference of sliding device 50.In addition, engaging groove 51 extends on the direction of the axial direction perpendicular to sliding device 50.
In the inwall of engaging groove 51, a wall is in the axial direction called as first wall 52, and another wall in the inwall of engaging groove 51 is called as the second wall 53, towards the first projection 54 of the second wall 53 projection further on the rear side that first wall 52 is included in the sense of rotation of sliding device 50.When cam and sliding device 50 are positioned at the first running position place, and when sliding device 50 rotates, when first inclined surface 55 of the first projection 54 on the front side of sense of rotation engages with banking pin 71, sliding device 50 is displaced to the second running position by the first inclined surface 55.
Second wall 53 comprises the second projection 58 towards first wall 52 projection further on rear side that positions different from the first projection 54 is in circumferential direction in sense of rotation.When cam and sliding device 50 are positioned at the second running position place, and when sliding device 50 rotates, when second inclined surface 59 of the second projection 58 on the front side of sense of rotation engages with banking pin 71, sliding device 50 is displaced to the first running position by the second inclined surface 59.
The diapire of engaging groove 51 comprises the first rise surface 64 and the second rise surface 66.First rise surface 64 is inclined surfaces, and its degree of depth apart from the radially-outer surface 68 of sliding device 50 diminishes towards the first projection 54 rear end 57 in a rotational direction.Second rise surface 66 is inclined surfaces, and its degree of depth apart from the radially-outer surface 68 of sliding device 50 diminishes towards the second projection 58 rear end 61 in a rotational direction.
Actuator 70 is Linear-moving type electromagnetic actuating devices, and is fixed to cylinder head 12.Actuator 70 comprises banking pin 71 and driver element 73.Banking pin 71 can be equivalent to " limiting member ".Banking pin 71 is configured to make the axial direction of banking pin 71 consistent with the radial direction of sliding device 50.Banking pin 71 can in a direction, that is, at the axial direction top offset of banking pin 71 to be separated close to sliding device 50 or with sliding device 50.
When close to sliding device 50, engaging groove 51 is inserted in the end of banking pin 71, and when being separated from sliding device 50, the end of banking pin 71 removes from engaging groove 51.Therefore, banking pin 71 can insert engaging groove 51 and remove from engaging groove 51.When inserting engaging groove 51, banking pin 71 engages with the inwall of engaging groove 51 with the axial position of limit slippage device 50.
Driver element 73 comprises the axle sleeve 74 reciprocally keeping banking pin 71, the fixed core 75 be fixed on the inwall of axle sleeve 74, the mobile core 77 being fixed to the end of banking pin 71 in axle sleeve 74 and coil 79, and this coil 79 is made up of the winding wire around fixed core 75 and produces magnetic field when being energized.
Mobile core 77 comprises permanent magnet, and it repels the fixed core 75 by the magnetic field magnetisation of coil 79.Banking pin 71 is inserted into engaging groove 51 to be separated from fixed core 75 by mobile core 77 by the energising of coil 79 by driver element 73.Similarly, driver element 73 makes banking pin 71 remove from engaging groove 51 by stopping the energising of coil 79 to eliminate the magnetization of fixed core 75.
When sliding device 50 is displaced to the second running position in Fig. 9 from the first running position Fig. 1, when banking pin 71 is consistent with the first projection 54 relative to the position of sliding device 50 in circumferential direction, driver element 73 starts the operation be inserted into by banking pin 71 in engaging groove 51.When sliding device 50 moves to the second running position from the first running position, when banking pin 71 is consistent with the first rise surface 64 relative to the position of sliding device 50 in circumferential direction, driver element 73 stops energising.
When sliding device 50 is displaced to the first running position in Fig. 1 from the second running position Fig. 9, when banking pin 71 is consistent with the second projection 58 relative to the position of sliding device 50 in circumferential direction, driver element 73 starts the operation be inserted into by banking pin 71 in engaging groove 51.When sliding device 50 moves to the first running position from the second running position, when banking pin 71 is consistent with the second rise surface 66 relative to the position of sliding device 50 in circumferential direction, driver element 73 stops energising.
The rotation of camshaft 21 is slowed down so that rotation is delivered to sliding device 50 by speed reducer 80, and comprises the first external gear 81 and internal gear 83.First external gear 81 is contiguous low rotating cam 25 on the side contrary with high rotating cam 30 in the axial direction of low rotating cam 25, and integrally rotates with low rotating cam 25 and high rotating cam 30.First external gear 81 has cylindrical shape, and be coupled to camshaft 21 in case can transmit rotate and can relative displacement in the axial direction.
First external gear 81 is included in the flange portion 82 from its end radially outward projection on the side contrary with low rotating cam 25.Flange portion 82 keeps sliding device 50 together with low rotating cam 25.Axial force towards the sliding device 50 of low rotating cam 25 movement is delivered to each cam by low rotating cam 25.Axial force towards the sliding device 50 of flange portion 82 movement is delivered to each cam by the first external gear 81.
Internal gear 83 and sliding device 50 are formed by identical components and integrally formed with each other.Internal gear 83 and sliding device 50 integrally rotate.Internal gear 83 is positioned at the inner radial of sliding device 50 and coaxially arranges with sliding device 50.Internal gear 83 engages with the first external gear 81.
The rotation of camshaft 21 is slowed down by speed reducer 80, and rotation is delivered to sliding device 50.Assuming that sliding device 50 is slave ends, the reduction speed ratio of speed reducer 80 is 2.More specifically, the number of teeth of internal gear 83 is 2 times of the number of teeth of the first external gear 81.The rotating speed of sliding device 50 is 1/2 of the rotating speed of camshaft 21.
The operation of valve system 20 will be described with reference to Fig. 1 and 8 to 10.When sliding device 50 is positioned at the first running position place as shown in Figure 1, when camshaft 21 rotates, the rotary motion of low rotating cam 25 is delivered to Rocker arm 41 by roller 42, and is converted into the linear reciprocating motion of suction valve 44 subsequently.
In the state of Fig. 1, when engine speed has arrived high rotary area, such as, when banking pin 71 is consistent with the first projection 54 relative to the position of sliding device 50 in circumferential direction, driver element 73 starts the operation be inserted into by banking pin 71 in engaging groove 51.Banking pin 71 is after it is consistent with the first projection 54 relative to the position of sliding device 50 in circumferential direction and inserted engaging groove 51 once arrive the first projection 54 on it before.Therefore, banking pin 71 inserted engaging groove 51 after its relative position is in circumferential direction consistent with the first projection 54 before camshaft 21 rotates twice.
When sliding device 50 rotates together with camshaft 21 and banking pin 71 inserts engaging groove 51 as shown in Figure 8, first inclined surface 55 of the first projection 54 of sliding device 50 engages with banking pin 71, to make the axial position of sliding device 50 be limited, and sliding device 50 thus as in Fig. 8 arrow A 1 indicate towards second running position slide.When sliding device 50 slides towards the second running position, driver element 73 stops energising.At this moment, banking pin 71 is engaged the first rise surface 64 radially outward pressing of groove 51, and banking pin 71 removes to return in a radial outward direction from engaging groove 51.
When sliding device 50 is positioned at the second running position place as shown in Figure 9, when camshaft 21 rotates, the rotary motion of high rotating cam 30 is delivered to Rocker arm 41 by roller 42, and is converted into the linear reciprocating motion of suction valve 44 subsequently.Valve stroke when the convert rotational motion of high rotating cam 30 is the linear reciprocating motion of suction valve 44 is greater than the valve stroke when low rotating cam 25 convert rotational motion is suction valve 44 linear reciprocating motion.
In the state of Fig. 9, when engine speed arrives low rotary area, such as, when banking pin 71 is consistent with the second projection 58 relative to the position of sliding device 50 in circumferential direction, driver element 73 starts the operation be inserted into by banking pin 71 in engaging groove 51.Banking pin 71 is after it is consistent with the second projection 58 relative to the position of sliding device 50 in circumferential direction and inserted engaging groove 51 once arrive the second projection 58 on it before.Therefore, banking pin 71 inserted engaging groove 51 after its relative position is in circumferential direction consistent with the second projection 58 before camshaft 21 rotates twice.
When sliding device 50 rotates together with camshaft 21 and banking pin 71 inserts engaging groove 51 as shown in Figure 10, second inclined surface 59 of the second projection 58 of sliding device 50 engages with banking pin 71, to make the axial position of sliding device 50 be limited, and sliding device 50 thus as in Figure 10 arrow A 2 indicate towards first running position slide.When sliding device 50 slides towards the first running position, driver element 73 stops energising.At this moment, banking pin 71 is engaged the second rise surface 66 radially outward pressing of groove 51, and banking pin 71 removes to return in a radial outward direction from engaging groove 51.
As mentioned above, in the valve stroke controlling device 10 of the present embodiment, the first wall 52 of the engaging groove 51 of sliding device 50 comprises the first projection 54, towards the second wall 53 projection and when engaging with banking pin 71, sliding device 50 is displaced to the second running position from the first running position when sliding device 50 rotates further on its rear side in a rotational direction.When banking pin 71 inserts engaging groove 51 to engage with the first inclined surface 55 of the first projection 54 when camshaft 21 rotates, sliding device 50 is displaced to the second running position by banking pin 71.
Second wall 53 comprises the second projection 58, towards first wall 52 projection and when engaging with banking pin 71, sliding device 50 is displaced to the first running position from the second running position when sliding device 50 rotates further on the rear side that its position different from the first projection 54 is in circumferential direction in sense of rotation.When banking pin 71 inserts engaging groove 51 to engage with the second inclined surface 59 of the second projection 58 when camshaft 21 rotates, sliding device 50 is displaced to the first running position by banking pin 71.Therefore, according to valve stroke controlling device 10, sliding device 50 can by the displacement between the first and second operating position of single banking pin 71.
Valve stroke controlling device 10 comprises speed reducer 80 for slowing down the rotation of camshaft 21 so that rotation is delivered to sliding device 50.Therefore, according to valve stroke controlling device 10, because the rotation of the speed ratio camshaft 21 of sliding device 50 is slow, even if so the service speed of driver element 73 is relatively slow, banking pin 71 also can reliably be inserted in engaging groove 51.In addition, the load being applied to banking pin 71 from the inwall of the engaging groove 51 of sliding device 50 can reduce.
In the present embodiment, in speed reducer 80, assuming that sliding device 50 is slave ends, the reduction speed ratio of speed reducer 80 is 2.Consequently, banking pin 71 can be inserted in engaging groove 51 after banking pin 71 is consistent with the first projection 54 relative to the position of sliding device 50 in circumferential direction by driver element 73 before camshaft 21 rotates twice.Therefore, even if the service speed of driver element 73 is relatively slow, banking pin 71 also can reliably be inserted in engaging groove 51.
In the present embodiment, speed reducer 80 comprises the first external gear 81 of integrally rotating with low rotating cam 25 and high rotating cam 30 and engages with the first external gear 81 and the internal gear 83 integrally rotated with sliding device 50.Therefore, the structure of speed reducer 80 is simplified.
(the second embodiment)
Valve stroke controlling device according to the second embodiment will describe with reference to Figure 11.Valve stroke controlling device 90 comprises sliding device 91 and speed reducer 92.Sliding device 91 can rotate around the axial centre (axle center) being parallel to camshaft 21, and can move relative to camshaft 21 in the axial direction.Sliding device 91 can in the axial direction between the first and second operating position with the integrally displacement of each cam.
Sliding device 91 is connected to camshaft 21 can be rotated by speed reducer 92 transmission.Speed reducer 92 comprises the second external gear 93 and the 3rd external gear 95.Second external gear 93 is contiguous low rotating cam 25 on the side contrary with high rotating cam 30 in the axial direction of low rotating cam 25.Second external gear 93, low rotating cam 25 and high rotating cam 30 are made up of identical component and integrally formed with each other.Second external gear 93 can transmit and rotate to camshaft 21 and can in the axial direction relative to camshaft 21 displacement.
3rd external gear 95 is contiguous sliding device 91 in the axial direction, and coaxially arranges with sliding device 91.3rd external gear 95 engages with the second external gear 93.3rd external gear 95 and sliding device 91 are made up of identical components and integrally formed with each other.
Second external gear 93 is included in the flange portion 94 from its end radially outward projection on the side contrary with low rotating cam 25.Flange portion 94 keeps the 3rd external gear 95 together with low rotating cam 25.Axial force towards the 3rd external gear 95 of low rotating cam 25 movement is directly delivered to each cam.Axial force towards the 3rd external gear 95 of flange portion 94 movement is delivered to each cam by the flange portion 94 of the second external gear 93.When sliding device 91 axial displacement, each cam and sliding device 91 integrally move.
The rotation of camshaft 21 is slowed down by speed reducer 92, and rotation is delivered to sliding device 91.Assuming that sliding device 91 is slave ends, the reduction speed ratio of speed reducer 92 is 2.More specifically, the number of teeth of the 3rd external gear 95 is 2 times of the number of teeth of the second external gear 93.The rotating speed of sliding device 91 is 1/2 of the rotating speed of camshaft 21.In a second embodiment, the effect similar to the effect of the first embodiment is produced.
(the 3rd embodiment)
Valve stroke controlling device according to the 3rd embodiment will describe with reference to Figure 12.Valve stroke controlling device 100 comprises sliding device 101 and speed reducer 102.Sliding device 101 is contiguous low rotating cam 25 on the side contrary with high rotating cam 30 of low rotating cam 25.Sliding device 101 and camshaft 21 are coaxially arranged.Sliding device 101 can rotate relative to camshaft 21 and can relative movement in the axial direction.Sliding device 101 can in the axial direction between the first and second operating position with the integrally displacement of each cam.
Sliding device 101 is connected to camshaft 21 can be rotated by speed reducer 102 transmission.Speed reducer 102 comprises the 4th external gear 103, the 5th external gear 105, the 6th external gear 106 and the 7th external gear 107.
4th external gear 103 is positioned on the side contrary with low rotating cam 25 in the axial direction of sliding device 101.The joint 104 that the inner radial that 4th external gear 103 is included in sliding device 101 extends towards low rotating cam 25.4th external gear 103, low rotating cam 25 and high rotating cam 30 are made up of identical component and integrally formed with each other.Rotation can be delivered to camshaft 21 and can relative displacement in the axial direction by the 4th external gear 103.
5th external gear 105 can rotate around the axial centre (axle center) being parallel to camshaft 21, and engages with the 4th external gear 103.6th external gear 106 is contiguous 5th external gear 105 on sliding device 101 side, and coaxially arranges with the 5th external gear 105.5th external gear 105 and the 6th external gear 106 are made up of identical components and integrally formed with each other.
7th external gear 107 is positioned between sliding device 101 and the 4th external gear 103, and coaxially arranges with camshaft 21.7th external gear 107 engages with the 6th external gear 106.7th external gear 107 and sliding device 101 are made up of identical component and integrally formed with each other.
Sliding device 101 remains between low rotating cam 25 and the 4th external gear 103 in the axial direction.Axial force towards the sliding device 101 of low rotating cam 25 movement is directly delivered to each cam.Axial force towards the sliding device 101 of the 4th external gear 103 movement is delivered to each cam by the 4th external gear 103.When sliding device 101 axial displacement, each cam and sliding device 101 integrally move.
The rotation of camshaft 21 is slowed down by speed reducer 102, and rotation is delivered to sliding device 101.Assuming that sliding device 101 is slave ends, the reduction speed ratio of speed reducer 102 is 2.The rotating speed of sliding device 101 is 1/2 of the rotating speed of camshaft 21.In the third embodiment, the effect similar to the effect of the first embodiment is produced.
The amendment of above embodiment will be described.
In amendment, speed reducer can be realized by another kind of mechanical realization.Such as, speed reducer can by the such as epicyclic reduction gear unit configuration of another kind of gear reducer.Or speed reducer such as can comprise the banding pattern speed reducer configuration of pulley and band by the speed reducer of another kind of type.
In amendment, the reduction speed ratio of speed reducer can be the integer of 3 or larger.Alternatively, the value of reduction speed ratio can be its integral multiple be integer, such as 1.5.In amendment, the axial width of engaging groove can be different in circumferential direction.In amendment, engaging groove can form to have predetermined angle relative to axial direction.
In amendment, valve stroke controlling device can use in the valve system of outlet valve.In amendment, valve stroke controlling device not only can use in the valve system being configured with the roller locking device with rocking arm, and can use in the valve system of another kind of type.
In amendment, two or more valve stroke controlling device can be configured for an engine valve.Such as, three cams can be configured, and sliding device can be displaced to three axial positions by two banking pins.
In amendment, cam and sliding device can be connected to camshaft by the fit system beyond spline fitted.In amendment, the spline internal tooth engaged with camshaft can be formed at the place at least partially of cam and sliding device.
In amendment, the cam profile of high rotating cam and the cam profile of low rotating cam can have any difference.Such as, they can have identical maximum cam lift and can have different cam operation angles.Alternatively, they can have identical cam operation angle and have different maximum cam lifts.In addition, they can have identical maximum cam lift and cam and run angle and have different valves and open and close the time.
The disclosure is not limited in above-described embodiment, and can embody in the various modes and not deviate from the scope of the present disclosure.
In sum, the valve stroke controlling device 10,90 of above embodiment, 100 can describe as follows.
The disclosure relates to the valve stroke controlling device 10,90,100 of the valve stroke of the engine valve 44 for regulating motor.Valve stroke controlling device 10,90,100 comprise the first plane cam 25 of being coupled to camshaft 21 and the second plane cam 30, be connected to camshaft 21 can transmit and rotate and can the tubular sliding device 50 of relative displacement in the axial direction, 91,101, sliding device 50 can be inserted, the engaging groove 51 of the periphery wall of 91,101 and the limiting member 71 that can remove from engaging groove 51 and performance constraint component 71 are to insert the driver element 73 of engaging groove 51.
Sliding device 50,91,101 can in the axial direction between engine valve 44 first running position synchronous with the first plane cam 25 and engine valve 44 and synchronous the second running position of the second plane cam 30 with the first plane cam 25 and the second plane cam 30 integrally displacement.
Limiting member 71 inserts engaging groove 51 to engage with the first inclined surface 55 of engaging groove 51 when camshaft 21 rotates.Therefore, limiting member 71 is by sliding device 50, and 91,101 are displaced to the second running position.Limiting member 71 inserts engaging groove 51 to engage with the second inclined surface 59 of engaging groove 51 when camshaft 21 rotates.Therefore, limiting member 71 is by sliding device 50, and 91,101 are displaced to the first running position.Therefore, sliding device 50,91,101 can be displaced to two axial positions by single limiting member 71.
In addition, valve stroke controlling device 10,90,100 comprise for slowing down the rotation of camshaft 21 rotation is delivered to sliding device 50,91, the speed reducer 80,92,102 of 101.Therefore, due to sliding device 50, the rotation of the speed ratio camshaft 21 of 91,101 is slow, even if so the service speed of driver element 73 is relatively slow, limiting member 71 also can reliably be inserted in engaging groove 51.In addition, from sliding device 50, the load that the inwall of the engaging groove 51 of 91,101 is applied to limiting member 71 can reduce.
Although the disclosure describes with reference to embodiment, it will be appreciated that the disclosure is unlimited in embodiment and structure.The disclosure is intended to cover various amendment and equivalent arrangements.In addition, except above-mentioned various combination and structure, other combination and the structure of more, less or single element is comprised, also in spirit and scope of the present disclosure.

Claims (5)

1. one kind for regulating the valve stroke controlling device (10,90,100) of the valve stroke of the engine valve (44) of internal-combustion engine, and described valve stroke controlling device (10,90,100) comprising:
First plane cam (25), described first plane cam (25) is coupled to the camshaft (21) integrally rotated with the output shaft of described internal-combustion engine, so as can to transmit described camshaft (21) rotation and can relative to (21) displacement of described camshaft and can be the linear reciprocating motion of described engine valve (44) by the convert rotational motion of described camshaft (21) on the axial direction of described camshaft (21);
Second plane cam (30), described second plane cam (30) be coupled to described camshaft (21) in case can transmit described camshaft (21) described rotation and can in the axial direction relative to (21) displacement of described camshaft and can be the described linear reciprocating motion of described engine valve (44) by the described convert rotational motion of described camshaft (21), wherein said second plane cam (30) has the cam profile different from described first plane cam (25);
The sliding device (50 of tubular, 91, 101), described sliding device (50, 91, 101) being attached to described first plane cam (25) and described second plane cam (30) can transmit to it rotates, and be included in along described sliding device (50, 91, 101) circumferential direction is at described sliding device (50, 91, 101) engaging groove (51) that radial outer wall extends, wherein said sliding device (50, 91, 101) integrally can move axially with the first plane cam (25) and the second plane cam (30) between the first running position and the second running position, described engine valve (44) is synchronous with described first plane cam (25) at described first running position place, described engine valve (44) is synchronous with described second plane cam (30) at described second running position place,
Limiting member (71), described limiting member (71) can insert described engaging groove (51) and remove from described engaging groove (51), wherein:
When described limiting member (71) inserts described engaging groove (51) to engage with first inclined surface (55) of described engaging groove (51) when described camshaft (21) rotates, described limiting member (71) is by described sliding device (50,91,101) described second running position is displaced to; And
When limiting member (71) inserts described engaging groove (51) to engage with second inclined surface (59) of described engaging groove (51) when described camshaft (21) rotates, described limiting member (71) is by described sliding device (50,91,101) described first running position is displaced to;
Driver element (73), described driver element (73) is configured to performance constraint component (71) to insert described engaging groove (51); And
Speed reducer (80,92,102), described speed reducer (80,92,102) is for slowing down the rotation of described camshaft (21) described rotation to be delivered to described sliding device (50,91,101).
2. valve stroke controlling device according to claim 1 (10,90,100), wherein suppose that sliding device (50,91,101) is slave end, the reduction speed ratio of described speed reducer (80,92,102) is 2 or 3.
3. valve stroke controlling device (10) according to claim 1 and 2, wherein:
Described sliding device (50) to be arranged and eccentric relative to described camshaft (21) at the radially outward of described camshaft (21); And
Described speed reducer (80) comprising:
First external gear (81), described first external gear (81) integrally rotates with described first plane cam (25) and described second plane cam (30); And
Internal gear (83), described internal gear (83) engages with described first external gear (81) and integrally rotates with described sliding device (50).
4. valve stroke controlling device (90) according to claim 1 and 2, wherein:
Described sliding device (91) is configured to rotate around the axle center being parallel to described camshaft (21); And
Described speed reducer (92) comprising:
Second external gear (93), described second external gear (93) integrally rotates with described first plane cam (25) and described second plane cam (30); And
3rd external gear (95), described 3rd external gear (95) engages with described second external gear (93) and integrally rotates with described sliding device (91).
5. valve stroke controlling device (100) according to claim 1 and 2, wherein:
Described sliding device (101) and described camshaft (21) are coaxially arranged; And
Described speed reducer (102) comprising:
4th external gear (103), described 4th external gear (103) integrally rotates with described first plane cam (25) and described second plane cam (30);
5th external gear (105), described 5th external gear (105) is eccentric relative to described 4th external gear (103) and engage with described 4th external gear (103);
6th external gear (106), described 6th external gear (106) and described 5th external gear (105) coaxially arrange and integrally rotate with described 5th external gear (105); And
7th external gear (107), described 7th external gear (107) coaxially arranges with described 4th external gear (103) and engages with described 6th external gear (106), and described 7th external gear (107) and sliding device (101) integrally rotate.
CN201310070745.0A 2012-03-06 2013-03-06 Valve lift adjusting device Expired - Fee Related CN103306774B (en)

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