JPS60116809A - Valve non-operating device of engine - Google Patents

Abstract

PURPOSE:To reduce the driving force required for a changing-over member for the operation/ non-operation of a valve by a method wherein a spring member is provided in pressured manner between a supporting member forming the supporting point of a rocker arm and an engine fixing part, and the spring member is provided with a strong spring force cancelling an inertia force acted under a valve non-operation condition. CONSTITUTION:Supporting point members 13 transfer the movement of a cam surface 8a of a cam shaft 8 to an intake and an exhaust valves 5, 6, a valve moving mechanism 7 is provided with the rocker arms 11 which are freely swingable arround the supporting point members 13. In the above structure, the supporting point members 13 are respectively inserted in freely slidable manner into inserting holes 12a, 12b of a supporting member 12 fixed on a cylinder head 1. The inserting hole 12b at the exhaust valve 5 side is provided to be penetrated through from the upper side to the lowe side of the supporting member 12, then a slidable intermediate member and the first spring energizing the supporting member 12 toward the separating direction from the supporting point member 13 are provided at the inserting hole 12b side. Further, the second spring and a cam member 17 are provided, that is, the second spring having a larger spring force than the first spring is provided in pressured manner between the member 12 and the member 13, also a cam member 17 for changing-over the operation/non- operation is releasably supported in rotatable manner on the supporting member 12 and is flush with the intermediate member.

Description

Detailed Description of the Invention (Field of Industrial Application) The present invention is a valve train that controls the opening and closing of intake and exhaust valves. This invention relates to a valve actuator.

(Prior art) In general, in the case of a multi-cylinder engine, when the engine has surplus power such as when idling, decelerating, or stepping down, the intake and exhaust valves of specific cylinders are adjusted to stop operation of some of the cylinders. It is preferable to stop the operation in order to improve fuel efficiency.

In addition, in the case of a so-called dual-induction intake system engine that has two intake boats 1 to 1 for low-load and high-load applications, when the engine is operating at low load, the intake boat is designed to supply intake air only from the low-load intake boat. From the low-load intake bows 1 to 1, it is possible to open and close only the low-load intake valves that open and close the low-load intake boats, and to stop the operation of the high-load intake valves that open and close the high-load intake boats. The intake air effectively creates a powerful intake swirl inside the combustion chamber,
It is known that this is preferable for improving combustion stability and fuel efficiency.

As a device to make the intake and exhaust valves inactive in this way,
Conventionally, there is a device disclosed in Japanese Patent Application Laid-Open No. 54-57009, in which an oil chamber is formed inside a hydraulic lifter that constitutes the fulcrum of a rocker arm that controls the opening and closing of the intake and exhaust valves, and To activate the oil chamber, pressurized oil is filled in the oil chamber to maintain the fulcrum position. To deactivate the intake/exhaust valve, the pressure oil in the oil chamber is flowed out, and the movement of the hydraulic lifter is controlled by the movement of the rocker arm. However, when the hydraulic lifter follows the movement, air may be sucked into the oil chamber from the oil discharge passage side, and when this air is sucked, the intake and exhaust valves are deactivated. When pressure oil is filled in the oil chamber to activate the IIC air valve, when the oil chamber is compressed, the above-mentioned air is also compressed, so the fulcrum position is lowered, and as a result, the intake and exhaust valve The problem is that the opening period and the number of lift groups are reduced.

Therefore, in order to solve such problems, the applicant first attempted to prevent air from being sucked into the oil chamber when the intake and exhaust valves were not in operation, and also to prevent air from being sucked into the oil chamber when the intake and exhaust valves were not operating. An application has been filed for an engine valve operating device that can smooth the movement of the engine (see Japanese Patent Application No. 58-171,618).

A spring member with a strong spring force is interposed between the fulcrum member that constitutes the fulcrum of the rocker arm and the intermediate member, so that when the valve is in operation, the fulcrum member remains deviated upward due to inertia and uneven wear occurs. Therefore, when the valve operating state changes to the valve operating state, the suppressing member (for example, a cam) that controls switching between the valve operating state and the valve operating state overcomes the spring force of the spring and is driven. However, there remained the problem that a large driving torque was required.

(Object of the Invention) An object of the present invention is to reduce the driving force of the suppressing member that controls switching between the valve operating state and the valve operating state in the above-mentioned engine valve actuating device.

(Structure of the Invention) In order to achieve two objects, the present invention provides a strong force that cancels the inertial force that acts in the valve operating state between the fulcrum member that constitutes the fulcrum of the rocker arm and the engine fixing part. It is characterized in that a spring member (second spring member) having spring force is compressed.

(Example) An embodiment of the present invention will be described in detail below with reference to the drawings.

The drawing shows a dual induction intake system in which two intake boats for low load and high load and one exhaust boat are provided for one cylinder.
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3 is a cylinder head, in which a cylinder 2 forming a combustion chamber is formed, and a pair of intake bows h3a and 3b for low load and high load are opened in parallel in this cylinder 2, and , inspiratory bow h , 3 a.

An exhaust boat 4 is provided so as to open opposite to the exhaust boat 3b. The low-load intake boat 3a is formed with a relatively small passage area to increase the intake flow rate, and is curved so as to form an intake swirl within the cylinder 2. On the other hand, the high-load intake boat 3b is formed to have a relatively large passage area in order to increase intake air filling efficiency. In addition, low load and high load intake boats 3a, 3
An intake valve 5 for low load and high load (only the intake valve for high load is shown) that opens and closes each intake bow 1'' 3a, 3b at a predetermined timing is provided at the opening to cylinder 2 in b. On the other hand, at the opening of the exhaust boat 4 to the cylinder 2, there is an exhaust valve 6 that opens and closes the exhaust boat 4 at a predetermined timing.
are arranged, and each intake valve 5 and discharge bale valve 6 are arranged in a V shape.

At the top of the cylinder spatula F1, there is a rocker arm 2 that controls the opening and closing of the low-load intake valve, the high-load intake valve 5, and the exhaust valve 6. A valve train 4 is provided with an overhead cam 1M4iW.
ii7 is installed. This valve train (37) has a single camshaft 1 to 8 which extends in the direction of the centerline of the cylinder head 1 and is rotationally driven by the engine crankshaft (not shown); is formed with a cam surface 8a corresponding to each intake valve 5 and exhaust valve 6. Also, for each valve 5, 6, each valve 5, 6 is slidably supported on a valve guard 9. Valve closing direction V
In other words, the valve spring lO exerts an upward force, one end abuts against the cam surface 8a of the corresponding cam shirt 1-8, and the other end abuts against the valve stems 5s and 6s of each valve 5 and 6, and a force of 11 is generated. 8a for each valve 5. (The rocker arm 11, which can be rocked to transmit data to A fulcrum portion 13 is provided in which the tip portion 13a formed at the bottom fits into and contacts the spherical recess 11a formed at the intermediate portion of the rocker arm 11, and the fulcrum portion 13 constitutes the fulcrum of the rocker arm 11. 8, the rocker arm 11 moves to the fulcrum member 1.
The valves 5 and 6 are opened and closed by swinging around the tip 13a of the valve 3 as a fulcrum. The insertion hole 12a of the support member 12 is on the exhaust valve 6 side and the low-load intake valve side, and has a bottom at the top, while the insertion hole 12b is on the high-load intake valve 5 side and penetrates vertically. ing. Further, the support member 12 is formed integrally with each cam cap 12C that constitutes a bearing of the camshaft 8, and is fixed to the cylinder head l with a bolt (not shown).

Furthermore, the low-load intake valve side of the valve mechanism 7 and the exhaust valve 6
On the side, a hydraulic tappet (not shown) is slidably disposed within the fulcrum member 13, so that the fulcrum member I3 is pressed against the rocker arm 11 side with good followability to prevent the occurrence of valve clearance. It has become.

On the other hand, on the high-load intake valve 5 side of the valve mechanism 7, the fulcrum member I3 is slid in the sliding direction with respect to the fulcrum member 13 that is slidably inserted into the fitting hole 12b that penetrates vertically. An intermediate member 14 is fitted and inserted to be slidable in the same direction as the intermediate member 1 , and the intermediate member 1 is compressed between the intermediate member 14 and the support member 12 .
a first spring member 15 that urges the support member 12 and the support member 13 in a direction to separate the support member 12 from the fulcrum member 13; A spring member 16 and a cam member (suppressing member) 17 rotatably supported on the support member 12 and abutting the intermediate member 14 are provided.

The cam member 17 presses the intermediate member 14 toward the rocker arm 11, that is, downwardly, against the biasing force of the first spring member 15 in the first position where the intake valve 5 is activated, thereby turning the intermediate member 14 into a fulcrum member. The intermediate member 14 is separated from the fulcrum member 13 by the biasing force of the first spring member 15 in the second position where the first cam surface 18a is brought into contact with the upper end of the rod portion 13b of the rod portion 13b and the intake valve 5 is inactive. It has two cam surfaces 18b, and the groove bottom is deepest on the first cam surface 18a on the intermediate circumferential surface, becomes shallower as it goes to the second cam surface 18b, and on the second cam surface 18b there is a groove bottom that coincides with the circumferential surface. A cam 18 with an operating groove 18c carved therein;
This cam 18 is fixed to the shirt 1 by 19 and iL.

The cam member 17 rotates the shaft 19 by a drive mechanism (not shown) during high-load operation of the engine.
When positioned, the first cam surface 18a of the cam 18
The fulcrum member 13 that is pressed through the intermediate member 14 is pressed by the rocker arm 11, and the rocker arm 11 swings around the fulcrum member 13 as a fulcrum, and the camshaft 8
The movement of the cam surface 8a is transmitted to the high-load intake valve 5, and the high-load intake valve 5 is activated (see Fig. 2).On the other hand, when the engine is operating at low load, the cam 18 rotates. at the second position, at which time the second cam surface 18b of the cam 18
The intermediate member 14 and the fulcrum member 13, which are regulated by
The cam surface 8 of the camshaft 8
The rocker arm 11 and the fulcrum member 13 move according to the movement of a.
floats, and the movement of the cam surface 8a is not transmitted to the high-load intake valve 5, so that the high-load intake valve 5 is rendered inoperative (see Fig. 3), and the valve deactivation device according to the present invention A is configured.

Next, the structure of the intermediate member 14 is shown in FIGS. 2 and 3.
This will be explained in detail along the drawings.

The intermediate member I4 has a hydraulic tappet structure, with a pressure receiving plate 20 at the top that receives the pressing force from the cam part $417, a cylindrical sliding part 21a that slides within the fulcrum member 13 at the side, and an opening 1 at the bottom. The outer cylinder member 21 has a bottomed cylindrical shape and has a portion 21b.

A reservoir tJi22 is fitted into the bottom of the outer cylindrical member 21, and a cylindrical first plunger 23 is fitted into the inside so as to be slidable in an oil-tight manner. A lower oil chamber 24 is formed between the lower surface of the oil sump 22 and the oil sump 22. A second plunger 25 is fitted into the upper end of the first plunger 23 so as to be movable relative to each other in an oil-tight manner.

The second plunger 25 forms an upper oil chamber 26 between the lower surface of its bottom and the inner surface of the bottom of the first plunger 23, and a spring 227 is interposed in this oil chamber 2G.

An orifice 28 is formed in the center of the bottom of the second plunger 25, and a check valve 34 is provided in this orifice 28 from the upper oil chamber 26 side.
4 is formed by a ball 34a and is biased 1 in the closing direction by a spring 34b.

Also, a relief plate 3 is provided inside the upper part of the second plunger 25.
A pin 37 is connected to the bottom surface of the relief plate 36, and the pin 37 is connected to the check valve 34.
A spring 38 is interposed between the relief plate 36 and the bottom of the second plunger 25, and urges the tip of the pin 37 to move beyond the check valve 34 by #L4. An operating pin 39 that penetrates the pressure receiving plate 20 and extends upward is connected to the upper surface side of the relief plate 36, and the upper end of this operating pin 39 operates the valve of the cam 18 of the cam portion 4', J' 17. When the second cam surface 18 faces the groove 18 and faces, the upper end of the operating pin 39 is pushed down, and this pushing down causes the pin 37 to open the check valve 34. - Pressure receiving plate 20 through which the operation pin 39 is penetrated
A local part of the operating pin 39 is a discharge passage [40] for discharging the hydraulic oil to the outside.

A pressure oil supply passage 41 is formed in the support member 12.

Pressurized hydraulic oil (pressure oil) is supplied to this pressure oil supply passage 41 from an oil pump (not shown). A pressure oil passage 42 is provided in the body of the fulcrum member 13 facing the pressure oil supply passage 41.
Also, a first pressure oil passage 43 and a second pressure oil passage 44 are formed above and below the body of the outer cylinder member 21, and the first pressure oil passage 43 is formed in the circumferential gap of the first plunger 23. 45, the pressure oil passage 4G formed at the upper end of the second plunger 25 communicates with the orifice 28 at the bottom of the second plunger 25 to supply pressure oil to the upper oil chamber 26, and the second pressure oil passage・14
communicates with the lower oil chamber 24 to supply pressurized oil to the pump 4.

Above 1. When the first plunger 23 and the fulcrum member 13 are sliding relative to each other and the first pressure oil passage 43 is in communication with the pressure oil supply passage 41, the second pressure oil passage 43, 44 is connected to the second pressure oil passage 43,44. The oil passage 44 faces the relief gap 47 in the fulcrum member 13, and when the second pressure oil passage is in communication with the pressure oil O (supply passage 41), the first pressure oil passage 43 faces the relief gap 47 in the fulcrum member 13. Each passage 43, 44 is switched so that it is closed at the inner wall surface of the spring. It communicates with 4B.

Next, the valve deactivation device M of the engine configured as described above is
(Explain Ij operation.

FIG. 2 shows the intake valve 5 in the operating state, and the tip 13a at the lower end of the fulcrum member 13 supports the spherical recess 11a of the rocker arm 11 at a predetermined fulcrum position, and the fulcrum position is fixed. There is.

At this time, the first cam surface 18a of the cam 18
The pressure oil from the pressure oil supply passage 2341 is in contact with the pressure receiving plate 20 of the upper part of the first pressure oil passage! ! 343, the circumferential gap 45, the pressure oil passage 4G, and the upper oil chamber 2 via the check valve 34.
6, this oil chamber 26 increases its volume and pushes down the first plunger 23, so that the bottom of the oil chamber 26 comes into contact with the temporary oil sump 22, and the rod of the fulcrum member 13 is placed on the lower surface of the oil sump plate 22. The upper ends of the portions 13b abut, and the fulcrum position of the fulcrum member 13 is secured by the pressure of the upper oil chamber 24.

Next, in order to put the intake valve 5 into the valve operating state, the cam 18 is controlled to rotate 180 degrees from the position shown in FIG. Board 20
to face.

Since the second cam surface 18b has a small amount of eccentricity, it allows the outer cylinder member 21 to move upward, and the first spring member 15 pushes up the intermediate member 14.

At this time, the fulcrum part ()i13 is the second spring part +)
At U6, the tip 13a is the four spherical parts 1 of the rocker arm 11.
It is biased so as to be in constant contact with 1a.

Further, the second cam surface 18b pushes down the operating pin 39 of the relief plate 36 with its peripheral surface, so that the relief plate 36
The pin 37 pushes down the check valve 34 and opens the strainer. By opening the check valve 34, the pressure oil in the upper oil chamber 2G flows out through the discharge passage 40, and the pressure oil in the oil chamber 26 is relieved.

When the outer cylinder member 21 is pushed up, the first pressure oil passage j"' of the outer cylinder item 21 is connected to the pressure oil passage 42 of the fulcrum member 13.
143 to the second pressure oil passage 44, and the pressure oil is 0 (the pressure oil from the supply passage 41 is introduced into the lower oil chamber 24).

As a result, since the upper oil chamber 26 is in the relief state 2 as described above, pressure oil flows into the lower oil chamber 24, and the volume of this oil chamber 24 is increased. The volume of the chamber 26 is constant, and air is prevented from being sucked into the oil chamber 2G.

When the outer cylinder member 21 is pushed up as shown in the upper part, the contact between the upper end of the rod part 13b of the fulcrum member work 3 and the lower surface of the oil sump plate 22 is released. The action force of the spring member 15 of No. 1 enables the rocker arm 11 to float relative to the outer cylinder member 21, and the fulcrum portion 4'' 13 follows the movement of the cam surface 8a, and the rocker arm 11 moves with the intake valve 5 side as the fulcrum. As a result, the intake valve 5 becomes movable and the valve element is activated.

Furthermore, in order to change from the above-mentioned valve operating state to the valve operating state, the state shown in FIG. 3 returns to the state shown in FIG. 18a presses the pressure receiving plate 20 of the outer cylindrical portion I, 1'21 against the spring force of the first spring member 15, thereby causing one stroke.

In this case, since the spring force of the first spring member 15 is relatively small, the driving torque of the cam 18 may be small.
The pressure oil passage 42 is the second pressure oil passage 4 in the lower part of the outer cylinder member 21.
4 to the upper first pressure oil passage 43, and the second
The pressure passage 44 communicates with the relief gap 47, and the pressure oil in the lower oil chamber 2/I is relieved. and up+i
/E oil is introduced into the 1+ oil chamber 2G and its volume is increased, and the volume of the lower oil chamber 211 is decreased, and finally the 2nd
As shown in the figure, the temporary oil sump and the bottom of the first plunger 23 are in contact with each other, causing a bubble? Get working status.

” IJJ is changed from the double valve operating state to the valve operating state.
When the rocker arm 11 touches the cam surface 8, the fulcrum member 13
The upper end of the rod part 13b pushes up the lower surface of the oil sump plate 22, but at the time of this pushing up, the lower oil chamber 24 is filled with hydraulic oil. Oil chamber 24 is 81
mf, the noise generated by the above-mentioned thrusting can be reduced, and the load on the cam 18 can also be reduced.

It should be noted that the present invention is not limited to the above embodiments, but includes various other modifications. For example, in the above embodiment, the valve actuation) 'Ji if
An example is shown in which i A is applied to the high-load intake valve 5 in a dual induction intake system, but the present invention puts the intake and exhaust valves in an inactive state in order to stop the operation of a specific cylinder of a multi-cylinder engine. It is also applicable to cases where

Further, in the above embodiment, the first spring portion (,1■
5 is compressed between the flange of the outer cylinder opening 21 constituting the intermediate member 14 and the support member ■2, but between the intermediate part 4'' (outer cylinder member) and the fulcrum member The same effect can be obtained even if 4111 units are installed.

Further, in the above embodiment, the rocker 1111 has one end connected to the camshaft 8 and the other end connected to the valve stem 5s.

6s, respectively, and swings using the middle part as a fulcrum, but in the present invention, one end is used as a fulcrum, the other end is brought into contact with the valve stem, and the middle part is connected to the camshaft. There is also a method C that can be applied to a rocker arm method in which the rocker arm is brought into contact with the rocker arm.

Furthermore, in the above embodiment, the middle part month 1.1 is I)u
Although the hydraulic tappet J-type body is used as described above, a block body may also be used for the lit part. However, the four-piece hydraulic tappet assembly described in "--" maintains one contact of the intermediate member 14 with the fulcrum part 4413 during the valve operating state 84, has better followability, and has a smaller valve clearance. It can suppress the noise during valve operation to 0! It is advantageous for reduction.

In addition, as the suppressing member, in addition to the cam member such as σ mentioned above, various means such as a hydraulic cylinder that can take the first position and the second position as described above can be adopted. The rear member is advantageous because it is easy to operate and is simple in construction when moving between the first and second positions.

(Effects of the Invention) Since the present invention is configured as described above, it is possible to reduce the driving force of the suppressing portion H that controls switching between the valve operating state and the valve operating state.

[Brief explanation of drawings]

The drawings illustrate the embodiment of the present invention, and FIG. 1 is a longitudinal cross-sectional side view of a dual-inductor intake system engine, and FIGS. 2 and 3 show the Jr operation state and valve operation, respectively. FIG. 3 is a cross-sectional view of main parts showing the state.

Claims (1)

[Claims] (1) A camshaft with a cam surface and a spring in the closing direction? An intake or exhaust valve which is energized at the time of operation, a rocker arm that transmits the movement of the cam surface of the force shaft 1 to the valve, and a fulcrum of the rocker arm that is slidably supported on the engine fixing part. a fulcrum member, an intermediate member disposed to be slidable in the same direction as the sliding direction of the fulcrum member, and a first member that urges the intermediate member in a direction to separate it from the fulcrum member. a spring member;
-j-, a second spring member compressed between the engine fixing part and the fulcrum member and having a larger spring force than the first spring part 18; By pressing the intermediate member toward the rocker arm against the spring force and bringing it into contact with the fulcrum member, the valve is moved to the first position where it is activated and in the direction in which it is separated from the rocker arm in the sliding direction of the fulcrum member. In the middle of the day
l! and a suppressing member that assumes a second position in which the valve is rendered inoperative by separating the first member from the fulcrum member by the spring force of the first spring member. Child actuator.