阅读说明：本技术 可变气门升程系统 (Variable valve lift system ) 是由 I·梅思利 T·M·兰斯菲尔德 凯尔·韦布 于 2020-04-15 设计创作，主要内容包括：公开了一种总和摇杆系统,其根据由同心凸轮轴(46)的不同凸轮凸角(14、22)限定的第一和第二凸轮轮廓的组合升程来作用在提升气门(16)的杆的端部上。所述系统包括安装在枢转轴(18)上并具有与第一凸轮轮廓接触的第一从动件(44)和作用在气门(16)上的端部以根据第一凸轮轮廓的升程来使气门(16)移动一定量的第一摇杆(12),将固定地安装在发动机上的摇杆轴(24),以及可绕摇杆轴(24)枢转的第二摇杆(20),第二摇杆(20)具有接触第二凸轮轮廓的第二从动件(48)并用于根据第二凸轮轮廓的升程来移动第一摇杆(12)的枢转轴(18)。摇杆轴(24)与一平面相交,该平面包含枢转轴(18)的轴线和第一摇杆(12)的作用在气门杆上的端部,并且第一摇杆(12)包括用于容纳摇杆轴(24)的切口(26),切口(26)构造和尺寸设计成可防止摇杆轴(24)干扰第一摇杆(12)的运动。(A summation rocker system is disclosed that acts on the end of the stem of a poppet valve (16) according to the combined lift of first and second cam profiles defined by different cam lobes (14, 22) of a concentric camshaft (46). The system includes a first rocker (12) mounted on the pivot shaft (18) and having a first follower (44) in contact with the first cam profile and an end acting on the valve (16) to move the valve (16) an amount according to the lift of the first cam profile, a rocker shaft (24) to be fixedly mounted on the engine, and a second rocker (20) pivotable about the rocker shaft (24), the second rocker (20) having a pivot shaft (18) contacting a second follower (48) of the second cam profile and for moving the first rocker (12) according to the lift of the second cam profile. The rocker shaft (24) intersects a plane containing the axis of the pivot shaft (18) and the end of the first rocker (12) acting on the valve stem, and the first rocker (12) comprises a cutout (26) for receiving the rocker shaft (24), the cutout (26) being configured and dimensioned to prevent the rocker shaft (24) from interfering with the movement of the first rocker (12).)

1. A summation rocker system for acting on an end of a stem of a poppet valve (16) according to a combined lift of first and second cam profiles defined by different cam lobes (14, 22) of a concentric camshaft (46), the system comprising:

a first rocker (12) mounted on a pivot shaft (18) and having a first follower (44) in contact with the first cam profile and an end acting on the valve (16) to move the valve (16) by an amount according to the lift of the first cam profile,

a rocker shaft (24) to be fixedly mounted on the engine, an

A second rocker (20) pivotable about the rocker shaft (24), the second rocker (20) having a second follower (48) contacting the second cam profile and being for moving the pivot shaft (18) of the first rocker (12) according to a lift of the second cam profile,

it is characterized in that

The rocker shaft (24) intersects a plane which contains the axis of the pivot shaft (18) and the end of the first rocker (12) which acts on the valve stem, and

the first rocker (12) includes a cutout (26) for receiving the rocker shaft (24), the cutout (26) being configured and dimensioned to prevent the rocker shaft (24) from interfering with the motion of the first rocker (12).

2. The summation rocker system according to claim 1, wherein the cutout (26) in the first rocker (12) is a hole for receiving the fixed rocker shaft (24), the hole (26) being sized to allow the rocker shaft (24) to pass through the hole (26) with a sweeping clearance.

3. The summation rocker system according to claim 1 or 2, wherein the rocker shaft (124) has a reduced cross-sectional area in a region (121, 123), in which region (121, 123) the rocker shaft (124) is accommodated within the cutout (126) in the first rocker (112).

4. The summation rocker system according to any preceding claim, wherein the first rocker (212) comprises two surfaces (213, 215) axially spanning the second rocker (20), the two surfaces (213, 215) defining a pocket (217) therebetween, the second rocker (20) being housed with clearance within the pocket (217).

5. The summation rocker system of claim 1, wherein the first rocker (212) comprises at least two components (712a, 712b) fixed to each other.

6. A summation rocker system according to any preceding claim, wherein the first rocker (212) is formed from sheet metal.

7. Valvetrain comprising a summation rocker system according to any preceding claim for operating two different types of valves of an engine cylinder, wherein the summation rocker system is for opening and closing one of the two types of valves (16) according to the combined lift of the two cam profiles of the camshaft, and wherein the valvetrain further comprises a third rocker (332), the third rocker (334) being for operating the other of the two types of valves according to a single profile of a third cam (334) of the camshaft.

8. A valve train according to claim 7, wherein the third rocker (332) is pivotally mounted about the rocker shaft (324) axis of the second rocker (320).

9. A valve train as claimed in claim 7, wherein the third rocker (432) is mounted to the rocker shaft (424) by an eccentric element (436) to pivot about an axis different from that of the rocker shaft (424).

10. A valve train according to claim 7, wherein a control spring (28) acting between a fixed point in the engine and the first rocker (12) is provided to urge the follower (44) towards the first cam profile (14).

11. A valve train according to claim 7, wherein the first rocker (512) has a bore with an axis in a plane perpendicular to the axes of the pivot shaft (518) and the rocker shaft (524), the bore allowing a control spring (528) connected to the second rocker (520) to pass through the first rocker (512) with clearance.

Technical Field

The present invention relates to a valvetrain system for an internal combustion engine, and more particularly to a system that provides variable valve lift.

Background

Traditionally, internal combustion engines have used a single cam profile to enable gas to enter or exit the combustion chamber. More modern engines are able to vary the valve lift profile based on a variety of factors (e.g., engine speed and load) to achieve higher efficiency. Variable valve lift systems utilizing a summation rocker system may be used to combine two different cam profiles to produce a desired valve lift profile. The valve lift profile may be modified to accommodate current engine operating conditions by changing the timing of the two cam profiles relative to each other.

Summation rocker systems are known from the prior art, and a rocker system which is considered closest to the invention is described in EP 1426569. They function using two rockers, each of which is acted upon by one of two cam profiles. The two rockers are connected using a pivot shaft that allows the rockers to rotate relative to each other.

A first of the two rockers pivots about a pivot axis and acts between a first cam profile and the stem of the poppet valve to open and close the valve. The second of the two rockers is mounted in the engine on a fixed rocker shaft and acts between the second cam profile and the pivot shaft of the first rocker. This raises and lowers the pivot shaft supporting the first rocker according to the profile of the second cam profile. Movement of the pivot shaft changes the position of the first rocker, thereby changing the valve lift. It follows that the valve lift at any one point is determined by a combination of both the first and second cam profiles. In each case, the cam profile may be defined by a single cam lobe or, to avoid unbalanced forces, by two identical but axially spaced lobes.

For optimum performance, both rockers should have the same mechanical advantage, and the force exerted on the rocker should exert only a torque to rotate the rocker about the pivot axis or rocker axis (as the case may be). A further consideration in designing the geometry of the valve train is that the space available in the engine to accommodate the valve train may be limited. Since these different considerations create conflicting requirements, it has heretofore been necessary to compromise and address a configuration that is not optimal in terms of motion geometry and valve train packaging.

Disclosure of Invention

OBJECT OF THE INVENTION

The present invention therefore seeks to provide a valve train which employs a sum of cams but which provides greater freedom in the relative positioning of the different elements of the valve train.

According to the present invention, there is provided a variable valve lift system as set forth in claim 1 of the following appended claims.

Preferred features of the invention are set out in the appended dependent claims.

Drawings

The invention will now be further described, by way of example, with reference to the accompanying drawings, in which:

fig. 1a is a front view of a first embodiment of a variable valve lift system, in which a cutout in the form of a bore for a rocker shaft is provided in a first rocker,

Fig. 1b shows a detail of a further embodiment of the rocker in fig. 1a, wherein the cutout is in the form of a groove extending to the boundary of the first rocker,

FIG. 2 is an isometric view of a second embodiment of a variable valve lift system in which a hole in a first rocker and a rocker shaft passing through the hole with clearance, each having more than one diameter,

fig. 3a and 3b are different views of the first rocker of the third embodiment of the variable valve lift system, wherein the first rocker is made from a single formed sheet metal part,

figure 4 is an isometric view of another first rocker made from two sheet metal parts and assembled using a pivot shaft and a cam follower shaft,

fig. 5 is an isometric view of a valve train in which one of the intake and exhaust valves is operated using a cam summation system, while the other valve is operated by a conventional rocker and a single cam profile,

fig. 6 is an isometric view of a valve train similar to that of fig. 5, but wherein an eccentric bushing is used to optimize the location of the pivot axis of the conventional rocker,

FIG. 7 is an isometric view of a valve train similar to that of FIG. 6, showing another way of securing the eccentric bushing, an

FIG. 8 is a view of another valvetrain similar to the valvetrain of FIG. 7, but with the control spring mounted on the second rocker rather than the first rocker.

DETAILED DESCRIPTION OF EMBODIMENT (S) OF INVENTION

In the following description of embodiments of the invention, to avoid unnecessary repetition, like parts of different embodiments have been assigned reference numerals with the same last two digits. Accordingly, the numbers XX, 1XX, 2XX, 3XX, etc. will denote the same elements or modified elements that may fulfill the same function.

FIG. 1a shows a summation rocker system 10 for acting on two poppet valves 16 according to the combined lift of first and second cam profiles defined by different cam lobes 14, 22 of a concentric camshaft 46. The first rocker 12 of the system 10 is mounted about the pivot axis 18 and has a first cam follower 44 in the form of a roller in contact with the profile of the first cam lobe 14. The other end of the first rocker 12 acts on the valve stem via a bridge 27 to move the valve 16 according to the lift of the profile of the first cam 14. The second rocker 20 is pivotable about a rocker shaft 24 fixedly mounted on the engine, the second rocker 20 having a second follower 48 (more clearly visible in fig. 2), also in the form of a roller, in contact with the profile of the second cam 22. The second rocker 20 is used to move the pivot shaft 18 of the first rocker 12 according to the lift of the profile of the second cam 22.

As can be seen in FIG. 1a, the rocker shaft 24 intersects a plane that passes through the axis of the pivot shaft 18 and the end of the first rocker 12 that applies a downward force (as shown) to the valve 16. This placement of the rocker shaft 24, while optimizing the valve train geometry and packaging, is traditionally not possible because the robust first rocker 12 and rocker shaft 24 would compete to occupy the same space.

To accommodate the rocker shaft 24 in such a position, the first rocker 12 of the embodiment of the invention shown in fig. 1a and 1b is provided with a cutout 26, which cutout 26 is configured and dimensioned to prevent the rocker shaft 24 from interfering with the movement of the first rocker 12. In the case of fig. 1a, the cutout 26 is in the form of a bore in which the rocker shaft 24 is accommodated with clearance, whereas in fig. 1b the cutout 26a is a slot which extends to the boundary of the first rocker 12.

While a circular bore of sufficiently large diameter may be used, it is preferred to minimize the amount of material removed from the first rocker by providing a bore that is elongated in the direction of relative motion. The direction of relative motion may be curved or relatively straight, depending on the geometry of the valve train.

The first rocker 212 of the embodiment shown in fig. 3a and 3b comprises two inner surfaces 213, 215 axially straddling the second rocker 20, the two surfaces 213, 215 defining between them a pocket 217, the second rocker 20 being housed with clearance in the pocket 217. The pivot shaft 18, which is received in aligned holes 219 in the surfaces 213 and 215 of the first rocker 12, is pivotally connected to the second rocker 20 within the pocket 217.

The control spring 28 shown in fig. 1a is used to maintain contact between the first follower 44 and its corresponding cam lobe 14 throughout its rotation. The control spring 28 acts on the first rocker 12 and is mounted to a fixed point on the engine.

The optimal position of the control spring 28 generates a force vector through the pivot shaft 18 perpendicular to the line formed between the pivot shaft 18 and the fixed rocker shaft 24. However, it is often more important to minimize the height of the valve train, in which case the spring 28 may move from this optimal position.

In the second embodiment of the invention shown in fig. 2, the rocker shaft 124 has reduced diameters 121 and 123 in the region where it passes through the first rocker 112. The reduced diameter regions 121, 123 of the rocker shaft 124 allow at least a portion of the cutout 126 in the first rocker 112 to have a reduced diameter, such that the first rocker 112 benefits from increased stiffness characteristics due to less material being removed.

It is also possible to form the reduced area of the rocker shaft 124 with one or more slots, rather than a reduced diameter, in order to reduce the size of the cutout 126 in the first rocker 112.

If formed as a hole, a portion of the cutout 126 should remain diametric to provide a clearance fit for the larger diameter region of the rocker shaft 124. The diameter of the rocker shaft 124 is typically specified for the journal bearing of the second rocker 120 and therefore cannot be changed directly in the region through the second rocker 120. The location of this larger diameter portion of the bore may be placed anywhere along its swept extent to maximize stiffness.

The first rocking lever 212 of fig. 3a and 3b may be formed from sheet metal. While the material is still in its expanded sheet state, any holes required, such as those for the rocker shaft, pivot shaft and cam follower shaft, may be punched or cut, then the outer profile of the rocker is punched or cut, then finally folded to form rocker 212. The use of sheet metal parts automatically creates a pocket in which the second rocker can be placed, avoiding the need for machining.

Alternatively, as shown in fig. 4, the first rocker 712 may be assembled from two formed sheet metal part 712a and 712 b. These two components may be held together by pivot shaft 718 and cam follower shaft 730. The production of the cutout 726 for the rocker shaft 724 and the pocket for the second rocker can again be done before any shaping. It should be noted that the first rocker may be assembled from more than two parts, and it is not necessary that all parts are formed from sheet metal parts.

It is common to use a summation rocker system on only one of the intake or exhaust valves, which is operated using a conventional system having a single cam profile. Such a valve mechanism is shown in each of fig. 5 to 7. In the embodiment of FIG. 5, a conventional third rocker 332 is used to operate a valve not shown, the rocker 332 acting between another valve and a third cam lobe 334 mounted to the camshaft 346. The valve is opened and closed by the third rocker 332 according to a single third cam profile. As shown in fig. 5, rocker 332 pivots about rocker shaft 324. While such a configuration minimizes the impact of the summation rocker system on the cylinder head design, the rocker shaft 324 may not provide an optimal location for the pivoting of the third rocker 332.

The embodiments of the invention shown in fig. 6 and 7 provide a solution to alleviate this problem. In these embodiments, the position of the pivot axis of the rocker shaft 424 is changed by fitting an eccentric element such as a bushing 436 onto the rocker shaft 424, and the third rocker 432 is mounted onto the eccentric bushing 436. The bushing 436 must be prevented from rotating on the rocker shaft 424. Fig. 6 shows a bushing secured to the rocker shaft 424 by a machine screw 438. Other securing means may be used.

Another method of preventing rotation of the bushing 436 is employed in the embodiment shown in fig. 7. Rotational and axial movement in a first direction is constrained by the rocker shaft bearing 440 having a shaft mounting bolt 450 that secures the rocker shaft 424 to the bearing 440. Axial movement in the second direction is constrained by the bushing retaining washer 442 and ultimately by the first rocker 412 of the summation rocker system. This solution eliminates the need for any additional fixturing and requires only minimal design changes to the rocker shaft support 440 to accommodate the bushing 436.

As previously disclosed, the control spring 28 may sometimes be mounted in a less than optimally oriented manner to minimize the overall height of the valve train. Moving the control spring 28 from its optimal position requires a greater force to be generated by the spring 28. Designing a control spring that applies sufficient force, but still fits into the packaging space of the cylinder head, can be difficult or costly.

Fig. 8 shows an alternative arrangement of the control spring 528. Using the two-piece rocker described in the embodiment of fig. 4, the control spring 528 may be mounted directly to the second rocker 520 instead of the first rocker 512. Since the second rockers 520 are mounted lower than the first rockers, mounting the control spring 528 to the second rockers 520 reduces the valve train height while maintaining an optimal or near optimal angle of the control spring 528. In this position, the force vector generated by the control spring 528 acts through the pivot shaft 518 perpendicular to the line formed between the pivot shaft 518 and the fixed rocker shaft 24. Thus, the spring 528 needs to generate less force and is easier to package.

It should be understood that the above described embodiments may be combined where technically possible. For example, the control spring may act on the second rocker independently of the design of the first rocker. If the first rocker is to be constructed in any other way than that shown in fig. 8, the first rocker may require a through hole for the passage of the control spring. Alternatively, the control spring may be located in a recess or hole in the first rocker.

Additionally, or possibly, the control spring may be arranged to act between the two rockers to maintain a desired contact with one of the cam profiles, rather than between one of the rockers and a fixed point on the engine.

Although in the above described embodiments, the summation rocker system is concerned with varying the lift of the valves, the duration of valve opening and the timing of the valves may vary depending on the phase of the cam lobes relative to each other, relative to either or both of the engine crankshaft.

The present invention may be used with any number of intake or exhaust valves in an engine, or indeed with any engine configuration or number of cylinders. If each rocker arm acts on more than one valve, the valves may be synchronized by a valve bridge connecting the valves to the valves.